Patent Publication Number: US-2020285257-A1

Title: Cartridge for a mixing valve

Description:
PRIORITY AND CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is the U.S. National Phase Application under 35 U.S.C. § 371 of International Application No. PCT/EP2018/075190, filed Sep. 18, 2018, designating the U.S. and published in English as WO 2019/057706 A1 on Mar. 28, 2019, which claims the benefit of French Application No. FR 1758673, filed Sep. 19, 2017. Any and all applications for which a foreign or a domestic priority is claimed is/are identified in the Application Data Sheet filed herewith and is/are hereby incorporated by reference in their entireties under 37 C.F.R. § 1.57. 
    
    
     FIELD 
     The invention relates to the field of taps, in particular for sanitary purposes. 
     SUMMARY 
     The present invention relates to a cartridge for a mixing valve, a mixing valve comprising such a cartridge and a method of operating such a cartridge. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention and its advantages will be better understood in the light of the examples described below, given by way of nonlimiting example, with reference to the appended drawings, wherein: 
         FIG. 1  shows a perspective view of a cartridge according to the invention; 
         FIG. 2  shows a view from below of the cartridge of  FIG. 1 ; 
         FIG. 3  shows a perspective view of a part of the cartridge of the preceding figures; 
         FIG. 4  shows a view from below of a part of the cartridge of the preceding figures; 
         FIGS. 5 to 10  show longitudinal sections of the cartridge of the preceding figures, according to the section line V-V of  FIG. 4 , showing the cartridge in several different operating configurations; 
         FIG. 11  shows a perspective view of a part of the cartridge of the preceding figures; and 
         FIGS. 12 and 13  show perspective views from two different angles, of a part of the cartridge of the preceding figures. 
     
    
    
     DETAILED DESCRIPTION 
     In this field, a cartridge is a device that makes it possible, by actuating a controller, or several controllers, to regulate the flow rate of a flow of cold fluid and the flow rate of a flow of hot fluid, in particular flows of water, in order to mix these two flows and thus form an outgoing flow, whose temperature and flow rate are the result of this regulation. A cartridge is referred to as “single control cartridge” when a single controller, for example a single lever or a single button, is used to adjust both the flow rate and the temperature of the outgoing flow. A cartridge is referred to as “double control cartridge” when the operation of one controller changes the temperature, while the operation of another controller changes the flow rate. A cartridge is referred to as a “thermostatic cartridge” when it incorporates a thermo-actuator participating in this regulation of the flow rate and temperature. 
     FR 3 047 534 A1 discloses an example of a particular type of cartridge referred to as a “sequential thermostatic cartridge”, in which, apart from the above-mentioned thermostatic regulation, the controller follows an angular stroke, during which the controller first causes an increase in the flow rate of the outgoing flow at a constant temperature, and then an increase in the temperature of the outgoing flow at a constant flow rate. 
     In known manner for this type of sequential cartridge, the controller actuates a disc that is rotatable relative to a fixed disc, so as to face a system of channels formed by the two discs as a function of the angular position of the rotary disc. For this type of specific cartridge, it is necessary in practice for the rotary disc to effect a relatively large angular stroke with respect to the fixed disc, for example about 150°, to allow the successive functions of the sequential cartridge to be implemented: firstly, increasing the flow rate of the outgoing flow at constant temperature, then the gradual increase of the temperature without variation of the flow rate. 
     To ensure the thermostatic regulation, the cartridge also comprises a slide that is axially movable in translation between two stops corresponding to extreme positions of the slide, referred to as “full cold” and “full hot”, in order to inversely vary the flow rates of the flow of water having passed through the discs. The position of the rotary disc and the slide are mechanically linked via a coaxial screw-nut system and a thermostatic actuator, wherein an over-travel spring is axially interposed between them. Therefore, the position of this slide depends both on the expansion of the thermostatic element and the position of the rotary disc. 
     At the beginning of the angular stroke of the rotary disc, corresponding to the case where the two incoming flows are closed by the discs, the screw of the screw-nut system is in its lowest position along the axis. The screw-nut system transmits the rotation of the rotary disc to the screw, so that the screw translates axially to a high position reached at the end of angular stroke of the rotary disc, which corresponds to the case where the flow rate and the temperature of the outgoing flows are at a maximum. Insofar as, for this type of cartridge, the angular stroke is particularly important, it occurs that a first angular sector of the rotary disc includes the start of the stroke, wherein the position of the screw is so low that the slide is blocked at full cold. As a result, the over-travel spring interposed between the screw and the slide is compressed for this first angular sector. In particular, the over-travel spring is compressed very significantly at the start of the stroke, which corresponds to the case where the incoming flow is closed: this closure configuration is the one most used during the life of the cartridge. Because of this excessive and prolonged compression, the over-travel spring may lose its stiffness, or be damaged, so that it no longer provides its over-travel function. When the spring deteriorates, it is possible that the slide may no longer reach the full cold position, which may be detrimental not only for the regulation of the temperature of the outgoing flow, but also in terms of safety of the user in the event of the slide closing badly, or no longer closing the passage of hot water. 
     The invention aims to remedy the drawbacks of the prior art by proposing a new cartridge reliably guaranteeing the state of the over-travel spring over time. 
     The invention relates to a cartridge for a mixing valve, wherein the cartridge comprises: two inlets of incoming flows of liquid; a chamber, designed to form an outgoing flow by mixing the incoming flows; a controller, which is movable relative to the chamber between an initial position and a terminal position, passing through an intermediate position between the initial position and the terminal position; an adjuster, which comprises: a positioner, which is movable relative to the chamber upon being actuated by the controller so as to be displaced relative to the chamber from a retracted position to an extended position when the controller is moved from the intermediate position to the terminal position; a shutter, which is movable with respect to the chamber for differentially modifying the respective flow rate of the incoming flows; a thermo-actuator, which comprises a primary part fixedly attached to the shutter and a secondary part moving relative to the primary part as a function of an outlet temperature of the outgoing flow; and an over-travel spring, which is interposed between the positioner and the secondary part of the thermo-actuator. According to the invention, the positioner is held in the retracted position, when the controller is moved from the initial position to the intermediate position. 
     Thanks to the invention, the positioner is only moved for a continuous range of the stroke of the controller, namely the intermediate position and the terminal position. Over this range of the stroke of the controller, thermostatic regulation of the flow rate of the incoming flows is carried out at least as well as in the prior art, since the position of the positioner varies according to the position of the controller, so that the position of the positioner depends on both the thermo-actuator and the controller. For another continuous range of the stroke of the controller, namely between the initial position and the intermediate position, the positioner is maintained in the same position, which avoids unnecessary stressing of the over-travel spring and so ensure its good condition in a sustainable way. 
     Advantageous and optional features of the invention to be considered in any technically feasible combination are defined in the following:
         the cartridge defines a fixed main axis with respect to the chamber; the controller is pivotally movable about the main axis from the initial position to the terminal position relative to the chamber; the positioner is movable in translation parallel to the main axis from the retracted position to the extended position relative to the chamber; and the adjuster comprises a mechanical connection through which the controller actuates the positioner, wherein the mechanical connection comprises: at least one radial tooth which protrudes radially with respect to the main axis from a first member among the controller and the positioner; at least one meshing path of the radial tooth which is recessed in a second member of the controller and the positioner.   each meshing path comprises: a helical thread, which is coaxial with the main axis, so that when the controller is moved from the intermediate position to the terminal position, the positioner is moved relative to the chamber from the retracted position to the extended position by the meshing of the radial tooth with the helical thread; and a radial notch, beginning at the end of the helical thread and extending in a plane orthogonal to the main axis, so that when the controller is moved from the initial position to the intermediate position, the positioner is held in the retracted position by the axial capture of the radial tooth in the radial notch.   the shutter is movable relative to the chamber, between: a safety position in which the shutter closes the first incoming flow and allows the second incoming flow; and an opposite position in which the shutter closes the second incoming flow and allows the first incoming flow.   the secondary part of the thermo-actuator is movable, relative to the positioner between a normal stroke position and an over-travel position; and the over-travel spring exerts a return force on the secondary part that tends to return the secondary part to the normal stroke position when the secondary part is brought into the over-travel position.   the secondary part of the thermo-actuator moves with respect to the primary part, from at least one retracted position to at least one extended position as a function of the outlet temperature; and the controller passes through a non-forcing position when moved between the initial position and the terminal position, so that: when the controller is between the initial position and the non-forcing position, the secondary part of the thermo-actuator is held in the over-travel position against the return force of the over-travel spring, while the shutter is held in the safety position, regardless of the secondary part being in the retracted position or in the extended position, and when the controller is between the non-forcing position and the terminal position, the secondary part of the thermo-actuator is in the normal stroke position at least when the secondary part is in the retracted position.   the controller passes through a single-opening position, when it is moved between the initial position and the intermediate position, and by a double-opening position, when it is moved between the intermediate position and the terminal position; and the cartridge further comprises a regulator that is designed to differentially vary the respective flow rate of the incoming flows as a function of the position of the controller, so that when the controller is between the initial position and the single-opening position the two incoming flows are closed by the regulator; when it is between the single-opening position and the double-opening position, one of the incoming flows is closed by the regulator and the other incoming flow is allowed by the regulator; and when it is between the double-opening position and the terminal position, the two incoming flows are allowed by the regulator.   the adjuster further comprises a return spring which is interposed between: on the one hand, the shutter or the primary part, and, on the other hand, the chamber.       

     The invention also relates to a mixing valve comprising a cartridge according to the above. 
     The invention also relates to a method of operating a cartridge according to the above, wherein: when the controller is moved from the initial position to the intermediate position, the positioner is held in the retracted position; and when the controller is positioned between the intermediate position and the terminal position, the positioner is moved from the retracted position to an extended position. 
       FIG. 1  shows a complete cartridge  1  that is intended to be integrated within a mixing valve for sanitary use (not shown). In the case of the example, the cartridge  1  is a sequential thermostatic cartridge. However, one could provide a cartridge  1  according to the invention, operating otherwise than sequential. 
     As may be seen in  FIG. 1 , the cartridge  1  comprises a housing  2  having a generally cylindrical shape with a circular base and geometrically defining a main axis X 1 . The housing  2  is intended to be fixed relative to the valve housing in which the cartridge  1  is integrated. 
     Unless otherwise stated, expressions such as “radial”, “axial” and “coaxial” refer to this axis X 1 . In addition, a main direction U 1  is defined by the axis X 1 . Unless otherwise stated, expressions such as “upper”, “high” and “above” refer to the U 1  direction, while expressions such as “lower”, “low” and “below” refer to a direction that is the reverse of the U 1  direction. 
     The cartridge  1  comprises a controller  3 , i.e. a control member. In the present example, the controller  3  is an assembly of several parts fixed relative to each other and which may be pivoted about the axis X 1  relative to the housing  2 . The pivoting is effected from an initial position, shown in  FIG. 5  to a terminal position shown in  FIG. 10 . Preferably, it is the only degree of freedom of the controller  3 . 
     Alternatively, the controller  3  may be in the form of a single integral part. 
     In addition, the cartridge  1  and its controller  3  are represented in the following configurations:
         in  FIG. 6 , the controller  3  is positioned at 35° (degrees) with respect to the initial position;   in  FIG. 7 , the controller  3  is positioned at 70° with respect to the initial position;   in  FIGS. 8 and 9 , the controller  3  is positioned at 97° with respect to the initial position;   in  FIG. 10 , the controller  3  is positioned at 145° with respect to the initial position.       

     Unless otherwise stated, all angular degree values mentioned in this document are understood to be in rotation of the controller  3  about the axis X 1  relative to the housing  2 , and in the same direction of rotation as represented by the rotation arrow R 3  visible in  FIGS. 2 and 3 . 
     As may be seen in particular in  FIG. 1 , the controller  3  comprises, in particular, a ring  5  which axially covers the top of the housing  2 . The ring  5  is designed to be coupled to a valve control lever, preferably in a fixed manner, if not via a transmission mechanism, wherein a user of the tap may operate the controller  3  via the control lever and thus control the cartridge  1  and the tap. 
     At a lower end of the housing  2  located axially at the bottom of the cartridge  1 , the cartridge  1  comprises a cold water inlet port  10 , a hot water inlet port  12  and an outlet port  14  for outgoing water. In other words, the housing  2  comprises a base  7  forming a lower axial end part of the housing  2 , wherein the orifices  10 ,  12  and  14  open from this base  7 . These orifices  10 ,  12  and  14  open axially from the bottom end of the cartridge  1  as shown in  FIG. 2 . Typically, the flows of cold water and hot water are supplied to the base of the valve housing in order to enter into the housing  2 . These flows of cold water and hot water are respectively represented by the arrows F 1  and C 1 . The outgoing water is emitted outwards from inside the housing  2  to form an outgoing flow, represented by the arrow M 1 . The flow M 1  is intended to be emitted via a spout. Specifically, when the cartridge  1  is integrated in the valve, the orifices  10  and  12  are in fluid connection with the cold water and hot tap water pipes, while the orifice  14  is in fluid connection with the spout of the tap. 
     More generally, the cartridge  1  comprises two inlets for the incoming flows of liquid F 1  and C 1 , which enter the cartridge  1  from the outside of this cartridge  1 . The cartridge  1  also comprises an outlet for an outgoing flow M 1  of liquid, which exits outside the cartridge  1  from the inside of this cartridge  1 . The liquids of the two incoming flows F 1  and C 1  are preferably provided at a temperature that is different by at least ten degrees, i.e. that of the cold temperature and hot temperature. 
     Alternatively, it may be provided that the liquid concerned is not water. 
     As illustrated in  FIGS. 5 to 10 , the outgoing flow M 1  is obtained by mixing flows F 1  and C 1  with each other, wherein this mixture constitutes the outgoing flow M 1 . Mixing is performed within the cartridge  1 , more specifically in a chamber  16  formed in the housing  2  that is in fluid connection with the orifice  14 . The chamber  16  is fixed with respect to the housing  2  and the main axis X 1 . The incoming flows F 1  and C 1  come into contact with each other in the chamber  16  in order to be mixed, i.e. mixed with each other, to then form the flow M 1 . In normal operation, the flow rate of the flow M 1  is equal to the sum of the flow rates of the flows F 1  and C 1 , whereas the temperature of the flow M 1  is a function of the flow rates and the respective temperatures of the flows F 1  and C 1 . In the present example, the chamber  16  is provided at the height of the base  7 , near the lower end of the cartridge  1 , wherein the orifice  14  is formed at the bottom of the chamber  16 . The chamber  16  is preferably crossed by the axis X 1 . 
     The cartridge  1  of the present example comprises and encloses a plurality of means for modifying and adjusting the respective flow rate F 1  and C 1  admitted into the cartridge in order to allow the regulation of the flow rate and temperature of the flow M 1 . 
     The cartridge  1  comprises a regulator  20 , which is designed to modify or differentially adjust the respective flow rate of the flows F 1  and C 1  as a function of the position of the controller  3 . In other words, the regulator  20  is able to variably limit, the flow rate of the flow F 1  and to variably limit, differently, the flow C 1 , according to the orientation of the controller  3  imparted by the user. Since the incoming flows F 1  and C 1  are each supplied at a certain pressure, the regulator  20  is able to limit the establishment of flow rates for each of the incoming flows F 1  and C 1 , between:
         a null flow rate value, for which concerned the flow does not flow, as a result of closing, and   a maximum flow rate value, for which the flow rate of the concerned flow is allowed to be set at a maximum value upon opening.       

     Preferably, the regulation of the flow rates by the regulator  20  is determined solely by the position of the controller  3 ; it is not dependent on any other element of the cartridge  1 . In particular, the thermo-actuator  62  of the cartridge  1 , defined below, does not actuate the regulator  20 . 
     Any type of regulator performing these functions may be provided for the cartridge  1 . In the present example, as shown in  FIGS. 5 to 10 , there is a disc regulator  20  contained in the housing  2 . The regulator  20  comprises an upper rotary disc  24 , shown only in  FIG. 4 , and a fixed lower disc  22 , shown bare in  FIG. 3 . In  FIG. 3 , only the lower part of the cartridge is shown, including the base  7 . The discs  22  and  24  are coaxial with the axis X 1  and are applied to each other in a sealed manner. For this, the discs  22  and  24  are preferably made of ceramic. 
     The disc  22  is fixed to the base  7  and is thus fixed relative to the chamber  16 . The disc  22  is axially traversed by four openings or channels  26 ,  27 ,  28  and  29 , which are each in the shape of an arc of a circle that is concentric with respect to the axis X 1 . The pair of channels  26  and  27  are arranged diametrically opposite, and approximately symmetrical to the pair of channels  28  and  29  with respect to the axis X 1 . The channels  26  and  27  extend in the same angular sector of the disc  22 , wherein the channel  26  is external while the channel  27  is internal. The channels  28  and  29  extend in the same angular sector of the disc  22 , wherein the channel  28  is external while the channel  28  is internal. As may be seen in  FIGS. 6 to 9 , the orifices  10  and  12  are respectively in fluid connection to the channels  26  and  28 , via a lower axial face  30  of the disc  22 . 
     The disc  24  is linked, even fixedly linked, in rotation about the axis X 1 , to a nut  40  of the controller  3 , via an upper axial face  33  of the disc  24 . The nut  40  that is enclosed in the housing  2  above the discs  22  and  24 , is itself linked, even fixedly linked, in rotation about the axis X 1 , to the ring  5 , wherein the ring  5  extends above the nut  40 . The disc  24  and the nut  40  have a degree of freedom, and preferably a single degree of freedom for rotation about the axis X 1 , with respect to the chamber  16 . The action of the user on the controller  3  directly rotates the disc  24  relative to the chamber  16 . It should be noted that the sectional plane of  FIGS. 5 to 10  is fixed relative to the disc  24  and relative to the controller  3 . Whatever the orientation of the disc  24 , a lower axial face  31  of the disc  24  flatly abuts the upper axial face  32  of the disc  22 , wherein this contact is sealed against the liquid flowing in the cartridge  1 . The disc  24  comprises two pockets  34  and  35 , opening at its lower axial face  31 . The pockets  34  and  35  are blind. The pockets  34  and  35  are arranged diametrically opposite to the axis X 1 . Each pocket  34  and  35  extends over a smaller angular sector than all or part of the channels  26 ,  27 ,  28  and  29 . The pockets  34  and  35  are respectively associated with a pair of channels  26 ,  27  and  28 ,  29 . Each pocket  34  and  35  extends radially so as to be able to open in both channels of the pair of channels associated therewith as a function of the position of the disc  22 . For example, in the configuration of  FIG. 6 , the pocket  34  opens on the channels  26  and  27  in order to be in fluid communication, while the pocket  35  opens on the channels  28  and  29  in order to be in fluid communication. When the channels  26  and  27  are thus in fluid communication, the regulator  20  does not oppose the establishment of a flow rate for the flow F 1 , i.e. the flow F 1  is allowed. When the channels  28  and  29  are thus in fluid communication, the regulator  20  does not oppose the establishment of a flow rate for the flow C 1 , i.e. the flow C 1  is allowed. For certain orientations of the disc  24 , as shown for example in  FIG. 5 , the fluid communication between the channels  26  and  27  is closed by the disc  22 , wherein the pocket  35  opens on a part of the face  32  where at least one of the channels  26  and  27  does not open. Then, the flow rate F 1  is null. Similarly, for some orientations of the disc  24 , as for example in  FIGS. 5 and 6 , the fluid communication between the channels  28  and  29  is closed by the disc  24 , wherein the pocket  35  opens on a part of the face  32  where at least one of the channels  28  and  29  does not open. Then, the flow rate of the flow C 1  is null. 
     Whether related to a disc or another mode of operation, it is preferred that the regulator  20  is configured for sequential operation. In the illustrated example of a sequential disc regulator, it is the distribution of the channels and pockets within the discs  22  and  24  that makes it possible to effect such an operation. To ensure such a sequential operation, it is advantageously provided that the controller  3  performs a stroke greater than 100°, or even greater than 130°. In the example shown, the controller  3  effects a 145° stroke from the initial position to the terminal position. When moved, i.e. rotated, from the initial position to the terminal position in the direction R 3 , the controller  3  passes through a single-opening position and a double-opening position. In this case, when the controller  3 :
         is between the initial position and the single-opening position, the flows F 1  and C 1  are closed by the regulator  20 , i.e. they have a null flow rate, which leads to a null flow rate for the outgoing flow M 1 , as it is the case in  FIG. 5 ;   is between the single-opening position and the double-opening position, the flow C 1  is closed and the flow F 1  is allowed by the regulator  20 , as it is the case in  FIG. 6 , so that, subject to the action of the adjuster  50  described below, the outgoing flow M 1  is exclusively constituted by the flow F 1  due to the absence of C 1  flow in the mixture; and   is between the double-opening position and the terminal position, the flows F 1  and C 1  are allowed by the regulator  20 , as it is the case in  FIGS. 7 to 10 , so that, subject to the action of the adjuster  50  described below, the outgoing flow M 1  is a mixture of the flows F 1  and C 1 .       

     In  FIG. 6 , it may be seen that the channel  28  is not closed by the disc  24 , while the channel  29  is closed, so that the flow C 1  has a null flow rate. 
     In  FIG. 10 , it may be seen that the channels  26 ,  27 ,  28 ,  29 , shown in dashed lines because they are outside the cutting plane, are not blocked by the disc  24 . In  FIG. 10 , the regulator  20  does not oppose to the establishment of a flow rate for the flows F 1  and C 1 . Nevertheless, the opening of the channels  26  and  27  is smaller than that of the channels  28  and  29 , so that the regulator  20  allows the establishment of a high flow rate for the flow C 1  and a lower flow rate for the flow F 1 . As explained below in the case of  FIG. 10 , the adjuster  50  opposes to the establishment of the flow F 1 , so that the flow F 1  has null flow rate even if it is allowed by the regulator  20 . 
     The single-opening position is, for example, reached at a position of the controller  3  between 0° and 35° relative to the initial position, for example about 10°, or in the same proportions of the total stroke of the controller  3 . The double-opening position is, for example, reached between 35° and 70°, for example between 55° and 70°, or in the same proportions of the total stroke. 
     The regulator  20  comprises two separate outlets, respectively for the flows F 1  and C 1 , the flow rate of which has been adjusted by the regulator  20 . These separate outlets are internal to the cartridge  1  and formed in the example shown by the channels  27  and  28  of the fixed disc  22 . The channels  27  and  28 , or more generally the two outlets, are respectively in fluid connection with intermediate ducts  41  and  42  formed in the base  7 . In the present example, the ducts  41  and  42  are respectively in fluid connection with the channels  27  and  28  at the lower axial face  30  of the fixed disc  22  and extend below the regulator  20  in the vicinity of the chamber  16 . 
     The ducts  41  and  42  are respectively in fluid connection to the chamber  16 , so that the flows F 1  and C 1  mix only when they reach the chamber  16  and form the flow M 1 , as shown in  FIG. 8 . 
     The cartridge  1  also comprises a flow rate adjuster  50  for the flows F 1  and C 1 , said adjuster  50  constituting a second means for modifying and adjusting the respective flow rate of the flows F 1  and C 1  admitted into the cartridge  1 . The adjuster  50  is designed to act on the respective flow rate of the flows F 1  and C 1  as a function of both the position of the controller  3  and the value of the outlet temperature of the outgoing flow M 1 . More generally, the adjuster  50  provides a thermostatic regulation of the outlet temperature of the flow M 1 . 
     The adjuster  50  comprises a shutter or slide  52 , which is housed in the upper part of the chamber  16 , i.e. opposite the orifice  14 . The shutter  52  is movable in translation parallel to the axis X 1  relative to the chamber  16 . This is advantageously its only degree of freedom, even if the shutter  52  may be free to rotate about the axis X 1 . The shutter  52  is movable along the axis X 1  between:
         a low position, called a “safety” or “full cold” position, in which the shutter  52  closes off the entering flow C 1  while allowing the flow F 1  as shown in  FIGS. 5, 6 and 9 , by placing a lower collar  54  of the shutter  52  in abutment against a lower seat  56  provided within the chamber  16 , for example at the place where the intermediate duct  42  opens into the chamber  16 ; and   a high position, called the “opposite” or “full hot” position, in which the shutter  52  closes off the incoming flow F 1  while allowing the incoming flow C 1  as shown in  FIG. 10 , by placing an upper collar  58  of the shutter  52  in abutment against an upper seat  60  provided within the chamber  16 , for example at the place where the intermediate duct  41  opens into the chamber  16 .       

     The shutter  52  thus moves between the two seats  56  and  60 . The closing contact between each of the necks  54  and  58  and their seat  56  and  60  respectively, is advantageously of circular shape and coaxial with the axis X 1 . 
     As shown in  FIGS. 7 and 8 , the shutter  52  is capable of adopting intermediate positions between the safety position and the opposite position, according to which the flows F 1  and C 1  are allowed to flow in complementary proportions. In other words, the shutter  52  inversely limits the flows F 1  and C 1 , in other words, limits in an antagonist manner. When the shutter  52  is halfway between the safety and opposite positions, the flows F 1  and C 1  are equitably limited by the shutter  52 . When the flow F 1  is allowed by the shutter  52 , said flow F 1  passes through the shutter  52  from top to bottom via a through-orifice  53  provided through the shutter  52 , as shown for example in  FIG. 8 . The mixture between the flows F 1  and C 1  is effected in the vicinity of the shutter  52  and below it. For example, the mixture is approximately at the height of the seat  56 . 
     The adjuster  50  comprises a thermo-actuator  62 , or thermostatic actuator, which comprises a primary part  64  fixedly attached to the shutter  52 , and a secondary part  66  moving relative to the primary part as a function of the outlet temperature of the flow M 1 . For this, the thermo-actuator  62  is at least partially arranged in the chamber  16 . The secondary part  66  moves, relative to the primary part  64 , from one or more retracted positions that are visible, for example, in  FIGS. 5 and 6 , up to one or more protruding positions that are visible, for example, in  FIGS. 7 to 10 , as a function of the outlet temperature of the flow M 1 . The retracted position corresponds to a state of the thermo-actuator  62  in which its length, measured axially, is at its lowest. In the protruding position, the thermo-actuator  62  has a longer axial length. The retracted position is preferably obtained at lower temperatures, for example below about 25° C., while the protruding position is preferably obtained at higher temperatures, for example above about 25° C. 
     The thermo-actuator  62  itself is movable at least in translation, as a whole, with respect to the chamber  16 , insofar as the primary part is fixedly attached, or is at least linked in translation along the axis X 1 , with the shutter  52 . Preferably, the secondary part  66  of the thermo-actuator  62  moves in translation parallel to the axis X 1  with respect to the primary part  64 , which constitutes its only degree of freedom, except, optionally, for free rotation about the axis X 1 . In the present example, the parts  64  and  66  of the thermo-actuator  62  are geometrically coaxial, or almost coaxial, with the axis X 1 . Preferably, the primary part  64  is located below the secondary part  66 . 
     In the illustrated example, the thermo-actuator  62  comprises a thermostatic element containing a heat-expandable material not visible in the figures, such as a wax. Alternatively, for example, a thermo-actuator comprising or consisting of a shape-memory alloy could be provided. 
     In the illustrated example, the primary part  64  belongs to the thermostatic element and comprises, as shown in  FIGS. 5 to 10 :
         at a lower end, a cup  68 , which encloses the heat-expandable material and extends in the chamber  16  into the passage of the flow M 1 , between the shutter  52  and the orifice  14 ;   at an upper end, a guide  69 , which guides the translation of the primary part  64 ;   at an intermediate part, a fastener  70  for fixing the shutter  52 , for example by screwing, so that the shutter  52  surrounds the primary part  64 .       

     The adjuster  50  further comprises a return spring  63 , which is axially interposed between, on the one hand, the shutter  52  or the primary part  64 , and on the other hand, the chamber  16  or any other fixed element relative to the housing  2 . More specifically, the spring  63  exerts, through elasticity, a return force that tends to return and/or maintain the shutter  52  in the opposite position. In the present example, the spring  63  is in the form of a compression spring that is, for example helical coaxial with the axis X 1 . In the present example, the spring  63  extends around and along the cup  68 . Preferably, the spring  63  is interposed between:
         an axial surface facing downwards, preferably formed by a neck or caliper  67  carried by the cup  68 , or more generally by the primary part  64 , or otherwise formed on the shutter  52 ;   an axial surface facing upwards, advantageously formed by an internal radial collar  17  or any equivalent means of the chamber  16 , at the bottom of the chamber  16 , in particular in the vicinity of the orifice  14 .       

     In the illustrated example, the secondary part  66  comprises:
         a piston  71  that is visible in  FIGS. 7 to 10 , and that is carried and guided in translation by the guide  69  and moved by the heat-expansion material, wherein the piston  71  belongs to the thermostatic element;   an extension rod  72 , whose lower end bears axially against the piston, wherein the rod  72  passes through the discs  22 ,  24  and the nut  40 ,   a limiter  73 , which is axially screwed to the upper end of the rod  72 , with a relatively fine pitch, so that the axial position of the limiter  73  on the rod  72  may be adjusted by screwing with a certain precision, which makes it possible to calibrate the thermostatic regulation of the outgoing flow M 1  provided by the adjuster  50 .       

     In the case of the example, the retracted positions of the thermo-actuator  62  correspond to the cases where the piston  71  is axially completely embedded or retracted in the guide  69 , or more generally in the primary part  64 . The protruding positions correspond to the cases where the piston  71  protrudes axially from the guide  69 . 
     In the example shown, the limiter  73  has an axially-tubular shape, so as to provide an axial through-duct  74 . Preferably, the limiter  73  is coaxial with the axis X 1 . At the bottom of this duct  74  is an internal screw thread, which is screwed onto an external screw thread provided at the upper end of the rod  72 . The duct  74  further allows screwing, since allowing the passage of a tool through the limiter  73  until it reaches the upper end of the rod  72 , where an indentation is advantageously provided for the tool. Alternatively, the secondary part  66  comprises a means for adjusting the axial position of the limiter  73  that is different from the screwing system described above, or is devoid of such means for adjusting the axial position. Alternatively, at least two parts among the piston  71 , the extension rod  72  and the limiter  73  are in the form of a single part. 
     The adjuster  50  comprises a positioner  80 , shown alone in  FIGS. 12 and 13 , which is movable relative to the chamber  16  by being actuated by the controller  3 . The positioner  80  is provided inside the housing  2 , in particular in the vicinity of the upper end of this housing  2 , in an axial chamber  83  of the housing, opposite the chamber  16  and opening upwards under the ring  5 . In the case of this example, the positioner  80  is movable in translation relative to the chamber  16  and parallel to the axis X 1 , from a retracted position, i.e. a low position visible in  FIGS. 5 and 6 , to the extended position, i.e. a high position visible in  FIG. 10 . The positioner  80  advantageously comprises an anti-rotation tooth  81  that is, for example radial and external, or any other anti-rotation means, for it to be fixed in rotation around the axis X 1  relative to the chamber  16 , while being movable in translation parallel to the axis X 1 . In the present example, the tooth  81  is positioned towards the top of the positioner  80 . As may be seen in  FIG. 7 , the tooth  81  of the present example is guided by an axial groove  82  formed in the upper part of the housing  2  and parallel to the axis X 1 , in particular in the chamber  83 . 
     The positioner  80  is of axially-tubular shape, having a duct  84  passing axially therethrough. The positioner  80  and/or its duct  84  are preferably coaxial with the axis X 1 . The limiter  73  is mounted within the positioner  80  by sliding axially relative to the positioner  80 . More generally, the secondary part  66  of the thermo-actuator  62  is movable relative to the positioner  80  between a normal stroke position, which corresponds to a low position of the part  66  with respect to the positioner  80  that is visible, for example, in  FIGS. 7, 8 and 10 , and higher over-travel positions that are visible for example in  FIGS. 5, 6 and 9 . 
     In the duct  84 , the positioner  80  comprises an axial surface that faces downwards and is formed, in the present example, by a collar  85  of the positioner  80 . The collar  85  is preferably radial and protrudes internally into the duct  84  at the upper end of the positioner  80 . The secondary part  66  of the thermo-actuator  62  comprises an axial surface, facing upwards, which is formed, in the present example, by a collar  75  of the limiter  73 . Preferably, the collar  75  is radial and external at the lower end of the limiter  73 . The adjuster  50  comprises an over-travel spring  90  that is axially interposed between the positioner  80  and the secondary part  66 , more precisely between the axial surface of the positioner  80  and the axial surface of the secondary part  66 . The spring  90  is preferably a compression spring, for example helical coaxial with the axis X 1 . The spring  90  preferably extends in the duct  84 , around and axially along the limiter  73 . By means of elasticity, the spring  90  mechanically exerts an axial return force on the secondary part  66  by pressing on the positioner  80 . This effort tends to return and maintain the secondary part  66  in the normal stroke position, especially when the secondary part  66  passes into the over-travel position. 
     The secondary part  66  comprises an axial surface facing downwards and that is advantageously formed by an outer conical flange  76  of the limiter  73 , while the positioner  80  comprises an axial surface facing upwards and that is advantageously formed by a conical surface formed on the top of the collar  85 , to form an axial stop limiting the displacement of the secondary part  66  to the normal stroke position, when the secondary part  66  is moved from the over-travel position to the normal stroke position. 
     The secondary part  66  comprises an axial surface facing upwards that is advantageously formed by the top of the collar  75  of the limiter  73 , while the positioner  80  comprises an axial surface facing downwards that is advantageously formed by an internal shoulder  86  provided in the duct  84  in order to form an axial stop that limits the displacement of the secondary part  66  to the over-travel position when the secondary part  66  is moved from the normal stroke position to the over-travel position. 
     To ensure the operation described here, it is provided that the over-travel spring  90  has a higher stiffness, for example twice as high as the stiffness of the spring  63 . 
     The adjuster  50  comprises a mechanical connection, through which the controller  3  actuates the positioner  80 , which effects the following operation:
         as shown in  FIGS. 5 and 6 , the positioner  80  is held in the retracted position, i.e. fixed in its low axial position with respect to the chamber  16  when the controller is moved from the initial position to an intermediate position that is between the initial position and the terminal position, and   as shown in  FIGS. 7 to 10 , the positioner  80  is moved relative to the chamber  16  from the retracted position to the extended position when the controller  3  is moved from an intermediate position to the terminal position.       

     Preferably, the intermediate position is between 35 and 70° with respect to the initial position, in particular between 55 and 70°, or at an equivalent proportion of the total stroke of the controller  3 . 
     Between the intermediate position and the terminal position, the translation of the positioner  80  is performed at a pitch, preferably a constant pitch, relative to the rotation of the controller  3 . The mechanical connection of the adjuster  50  then advantageously provides a screw-nut connection function. For this angular sector of the controller  3 , each change of orientation of the controller  3  corresponds to a change of the axial position of the positioner  80 . The mechanical connection of the adjuster  50  may then be described as “engaged”. 
     Between the initial position and the intermediate position, the mechanical connection disconnects the rotation of the controller  3  from the translation of the positioner  80 , so that the positioner  80  remains fixed axially relative to the chamber  16 , whatever the orientation of the controller  3  about the axis X 1  in this angular sector. The mechanical connection of the adjuster may be described as “disengaged”. In this situation, it is preferred that the positioner  80  is completely fixed with respect to the chamber  16 , but it could be provided that the positioner  80  is only axially fixed while being rotatable about the axis X 1 . It could also be provided that, in this situation, the positioner  80  is axially displaced over a negligible distance, or at a very small pitch with respect to the displacement pitch effected between the intermediate position and the terminal position. 
     It is preferred that the intermediate position is reached between the single-opening position and the double-opening position, preferably closer to the double-opening position, as is the case in the present example. 
     Alternatively, the initial position may be between the double-opening position or the terminal position, preferably being closer to the double-opening position. However, it may be provided that the intermediate position is reached between the initial position and the single-opening position in the vicinity of the single-opening position. It could also be provided that the intermediate position is coincident with the double-opening position. It could further be provided that the intermediate position is coincident with the single-opening position. 
     As the positioner  80  is kept in the retracted position on the sector extending from the initial position to the intermediate position, it is ensured that, for this sector, the compression of the spring  90  is not too high, which makes it possible to preserve the spring  90 , as illustrated in  FIGS. 5 and 6 . In fact, the axial displacement downwards of the positioner  80  is limited to the retracted position visible in  FIGS. 5 and 6 , so that the total stroke of the positioner  80  is relatively low, wherein the positioner  80  effects this stroke only when its displacement is of interest for the operation of the cartridge  1 , i.e. essentially when regulation of the outlet temperature must be carried out by the adjuster  50  between the double-opening position and the terminal position of the controller  3 . 
     At least when the regulator  20  authorizes the establishment of a flow rate for the two flows F 1  and C 1 , in particular between the double-opening position and the terminal position, the regulator  20  performs a thermostatic regulation of the outlet temperature of the outgoing flow. M 1 , as is the case in  FIGS. 7 to 10 . For this, the axial position of the shutter  52  is modified by the regulator  20 , both as a function of the axial position of the positioner  80 , which depends directly on the position of the controller  3 , and both as a function of the relative position of the primary part  64  and the secondary part  66  of the thermo-actuator  62 , wherein the latter is determined by the outlet temperature itself. The adjuster  50  is able to limit or completely close the flow C 1  by moving the shutter  52  to the safety position, especially when the controller  3  is positioned in the vicinity and slightly after the double-opening position. The regulator  20  is able to limit or completely close the flow F 1  by moving the shutter  52  to the opposite position, especially when the controller  3  is positioned in the vicinity and slightly before the terminal position. In the vicinity of the double-opening position, as illustrated in  FIG. 7 , the position of the positioner  80  is such that, despite being placed in a retracted position, or in a low protruding position of the secondary part  66 , the shutter  52  is in the safety position, or almost in the safety position. In the terminal position, as shown in  FIG. 10 , the position of the positioner  80  is such that, despite a protruding position of the secondary part  66 , the shutter is in the opposite position. 
     Preferably, when the controller  3  is positioned on a range extending from the initial position to a non-forcing position between the initial position and the terminal position, the secondary part  66  of the thermo-actuator  62  is held at the over-travel position against the return force of the over-travel spring  90 , while the shutter  52  is kept in the safety position regardless of the position of the secondary part  66  relative to the primary part  64 . In particular, the shutter  52  is pressed axially downwards, so that the secondary part  66  is in the retracted position or in the protruding position. This situation is shown, for example, in  FIGS. 5 and 6 . More precisely in this situation, the positioner  80  is in the retracted position, or in a position low enough for the shutter  52  to be kept in the safety position, even if the secondary part  66  is in the retracted position. In this situation, the over-travel spring  90  forces the shutter to be in the safety position at full cold. 
     When the controller  3  is between the non-forcing position and the terminal position, the secondary part  66  of the thermo-actuator  62  is free to reach the normal stroke position, in particular when the secondary part  66  is in the retracted position, or even for certain protruding positions, as is the case in  FIGS. 7, 8 and 10 . In this range of positions of the controller, the secondary part  66  may be placed in the protruding position in order to compensate for an over-travel of the thermo-actuator  62 , if the shutter  52  is in the safety position and if the secondary part  66  is placed in a sufficiently strong protruding position, as is the case in  FIG. 9 . The over-travel spring  90  is then compressed and thus absorbs the excess axial length of the thermo-actuator  62  to prevent damage to the cartridge  1 . In this range of positions of the controller  3 , the over-travel spring  90  plays the function of over-travel compensation. Such over-travel compensation occurs, in particular, when the outlet temperature is greater than a threshold value as determined both by the position of the controller  3  and by the design of the thermo-actuator  62 , for example when the water pressure of the cold water supplied to the orifice  10  is very low in comparison with the pressure of hot water supplied to the orifice  12 . The regulator  20  then closes the flow C 1  by placing the shutter  52  in the safety position, which prevents burning of the user. 
     Preferably, the non-forcing position is between the intermediate position and the terminal position, close to the intermediate position. It is preferred that the non-forcing position is between 65° and 70° with respect to the initial position, or an equivalent proportion of the total stroke of the controller  3 . 
     Alternatively, the non-forcing position is between the double-opening position and the terminal position, near the double-opening position. In particular, it may be provided that the non-forcing position is coincident with the double-opening position. 
     In the present example, the nut  40  comprises a through housing  43  that is coaxial with the axis X 1 . Preferably, this housing  43  comprises a lower part, opening downwards, through which the secondary part  66  passes. 
     Advantageously, this housing  43  comprises an upper part, which may have a larger diameter, and that opens upwards. Within this housing, one or more meshing paths are hollowed out. In this example, three paths are provided, as explained below. 
     From the top of the housing  43 , each path comprises an internal thread  44 , i.e. a helical groove coaxial with the axis X 1 . Each thread  44  extends over only a part of the axial length of the housing  43 , called the “engaging part”. In the present example, the three threads  44  are interlaced. 
     Towards the bottom, each path comprises, in the continuity of the concerned thread  44 , a radial notch  45  formed in a recess in the housing  43  and extending the thread  44 . In other words, each notch  45  starts at the end of the thread  44  of the concerned path, at the bottom of this thread  44 . The notches  45  extend axially over only a part of the axial length of the housing  43 , referred to as the “disengaging part” that starts immediately at the bottom of the engaging part. Each notch  45  extends in the same plane orthogonal to the axis X 1 . Each notch  45  is hollowed out radially outwards, i.e. it increases the diameter of the housing  43  locally. Each notch  45  extends over only a part of the circumference of the housing  43  about the axis X 1 , for example less than 90°. The notches  45  are separated from each other by being evenly distributed about the axis X 1 . The notches  45  are advantageously radially through, but could be radially blind. Alternatively, in the case of discrete notches  45  as shown, one could provide a notch or groove that would be continuous over the entire circumference and recessed in the housing  43 . In this case, a single continuous groove would form the radial notch of several or all the meshing paths. 
     Each meshing path, therefore, describes an oblique trajectory, more precisely a helical path, at the height of its thread  44 , and a trajectory forming an arc of a circle in a plane orthogonal to the axis X 1 , at the height of its radial notch  45 . 
     The positioner  80  is coaxially movable in this housing  43  so as to be surrounded by the nut  40 , as may be seen in  FIG. 11 . The positioner  80 , shown alone in  FIGS. 12 and 13 , comprises one or more teeth  87 , in the present example three teeth  87 , that are able to be respectively meshed, i.e. to guided, in the threads  44  and the notches  45  of the meshing path. Advantageously, the same number of teeth  87  is provided as threads  44  and notches  45 . The teeth  87  extend in the same orthogonal plane with respect to the axis X 1 , preferably towards the bottom of the positioner  80 . Each tooth  87  projects radially outwards from an outer wall of the positioner  80 , i.e. increasing the diameter of the positioner  80  locally. Each tooth  87  extends over only a part of the circumference of the positioner  80  about of the X 1  axis. The teeth  87  are separated from each other by being regularly distributed about the axis X 1 . 
     Each tooth  87  occupies an angular sector less than 360°, preferably less than 90° about the axis X 1 . In the present example, each tooth  87  occupies an angular sector between about 70° and 80° about the axis X 1 . Preferably, it is provided that each tooth  87  extends over an angular sector corresponding to this range of values, which is at the same time:
         sufficiently high to allow reliable meshing with the threads  44 ,   sufficiently low, not only to ensure the operation mentioned below by interaction with the corresponding meshing path, but also to allow the manufacture of the positioner  80  through molding, wherein the faces of the positioner  80  are all oriented in relief relative to a joint plane comprising the axis X 1  and passing through, for example, the tooth  81 .       

     Therefore, the positioner  80  is both reliable and particularly easy to manufacture. 
     The axial length of the tooth  87  is preferably equal to, or slightly less than, the axial length of the notch  45 . 
     The axial length of each tooth  87  is, for example, close to the value of the pitch of the corresponding thread  44 . 
     Each tooth  87  preferably forms a helical thread portion that is coaxial with the axis X 1  just like the thread  44 . 
     Preferably, as may be seen in  FIGS. 11 to 13 , each tooth  87  comprises, axially with respect to the axis X 1 , two walls  88  and  89 , inclined obliquely opposite with respect to the axis X 1 , in order to present a helical shape locally. The wall  89  faces downwards in order to slide against a part of the thread  44  extending below the tooth  87  in question, while the other inclined wall  88  faces upwards in order to slide against a part of the thread  44  extending above the tooth  87  in question. 
     Each tooth  87  comprises axially with respect to the axis X 1 , two opposite axial walls  91  and  92 , at least one of which, preferably the wall  91  at the top, is parallel to a plane orthogonal to the axis X 1 . These walls  91  and  92 , or at least the top wall  91 , are provided to slide along the walls of the notch  45  in question. Preferably, these walls  91  and  92  connect the inclined walls  88  and  89  to each other. 
     In the preferred embodiment shown, each tooth  87  has a contour in the form of a non-rectangular parallelogram or trapezoid, with two opposite axial walls  91  and  92  connected by two opposite oblique walls  88  and  89  as may be seen, in particular, in  FIG. 13 . Thus, each tooth  87  meshes with a maximum of the thread  44  in question, while being able to be engaged in the notch  45  in question without hindering the rotation of the controller  3 . 
     The notch  45  advantageously comprises walls with a shape corresponding to that of the walls of the teeth  87 . Consequently, each tooth  87  may be housed entirely in the notch  45 , so that the angular stroke of the nut  40  is particularly important. In particular, the notch  45  comprises an oblique wall  93  corresponding to the oblique wall  88  of the tooth  87 . 
     Alternatively, it is expected that a single wall of the tooth  87  is oblique, or that no wall is oblique. 
     Thanks to the threads  44 , the notches  45  and the teeth  87 , the mechanical connection of the adjuster  50  allows:
         when the controller  3  is moved from the initial position to the intermediate position, the positioner  80  is held in the retracted position by axial engagement of the teeth  87  in their respective notches  45 , wherein the nut  40  rotates without the positioner  80  being axially displaced; and   when the controller  3  is moved beyond the intermediate position, to the terminal position, the positioner  80  is moved relative to the chamber  16 , from the retracted position to the extended position by meshing the teeth  87  with the threads  44  in the manner of a helical link.       

     One could provide a single radial tooth associated with a single meshing path, or two radial teeth respectively associated with two meshing paths. However, it is preferred to provide three radial teeth respectively associated with as many meshing paths to ensure that the actuation of the mechanical connection has a particularly low clearance, high accuracy and high durability, without substantial damage to the mechanical reliability of this connection. If necessary, it would be possible to provide more radial teeth respectively associated with as many meshing paths, in order to reinforce the reliability of the mechanism. 
     One could provide the opposite arrangement to that of the illustrated example, wherein the meshing paths are provided on the positioner  80  and wherein the radial teeth are provided on the nut  40 . In any case at least one radial tooth is provided on a first member of the controller  3  and the positioner  80 , and at least one meshing path of this radial tooth is provided on a second member of the controller  3  and the positioner  80 . 
     The cartridge of the illustrated example makes it possible to implement an operating method, in which, when the controller  3  is moved from the initial position to the intermediate position, the positioner  80  is kept in the retracted position, and when the controller  3  is positioned between the intermediate position and the terminal position, the positioner  80  is moved from the retracted position to the extended position.