Patent Document

TECHNICAL HELD 
     The present invention relates to a pressure regulator device, especially of the hydraulic remote-control type such as a hydraulic remote control for civil engineering machines. 
     BACKGROUND 
     These regulator devices are in particular used to control various hydraulic functions such as setting various receivers in motion that are installed onboard these civil engineering machines. 
     The invention more particularly relates to a regulator device comprising: 
     a body provided with two end faces, lower and upper, respectively, and a peripheral face extending between the two end faces, and comprising at least one so-called control cavity emerging on at least one of said faces, 
     a minimum of a pressure reducer mounted in the body and comprising a control push-piece housed in back and forth motion in the at least one control cavity, said pressure reducer being intended to enable the control of at least one receiver outside the regulator device, 
     a control member pivoting relative to the body, at least one hinge mounted on the upper face of said body, in order to control the back and forth movement of the at least one control push-piece. 
     Such regulator devices are well known by those skilled in the art and are for example described in documents FR 2 507 732, FR 2 376 978, FR 2 793 532, FR 2 854 668, FR 2 857 706 and FR 2 835 574. 
     In these documents, the control member assumes the form of a lever or a handle, which can be actuated manually, extended by a lower shell arranged opposite the upper face of the body of the regulator device; upper face in which the control cavities emerge wherein the control push-pieces are mounted able to move, so that said control push-pieces protrude outside the upper face to abut against the lower shell of the control member. In such designs, the control cavities extend normally opposite the upper face of the body so that, once said body is fastened on a horizontal floor, the control cavities and the control push-pieces extend vertically and the body must have a height adapted to the integration of the pressure reducer. The height of the body leads to a limitation of the height space and a sometimes prohibitive vertical bulk when it involves installing the regulator device in a confined space such as, for example, a cockpit of a civil engineering machine. 
     Traditionally, the control cavities are made by machining and are generally made in the form of a hole passing all the way through the body in the height direction, between the lower and upper faces. Such an embodiment requires that the control cavities be connected via the lower faces, and therefore that connecting hoses be brought through the horizontal floor on which the regulator device is placed flat, thereby hindering the integration of the hoses and of the entire device on the floor. Alternatively, it is possible to consider providing bores transverse to the control cavities, making the production of the body and its various cavities or pipes more complex. 
     It is also known to use such regulator devices in foot-operated hydraulic remote controls. In such an application, the control member assumes the form of a tilting pedal, which can be actuated by foot, and arranged opposite the upper face of the body of the regulator device. Such a pedal can be used in civil engineering machines for forward and backward travel controls of the machine, in other words for forward or backward movement or the translation of the machine. As in the aforementioned documents, these regulator devices comprise control cavities and control push-pieces extending vertically with the same drawbacks as mentioned above. 
     In a known manner, an additional control lever is hinged on one of the ends of the pedal and extends upward to end with a handle that can be manipulated manually in order to add a control for the tilting of the pedal. Such a control lever is used to impose tilting of the pedal from front to back, or vice versa, that is more precise than that obtained directly with the food placed on the pedal, in particular to allow more precise movement of the civil engineering machine. 
     However, such a control lever represents a mass situated at one of the ends of the pedal, therefore off-center relative to the hinge of the pedal, the inertia of which must be combated using a damper. It is thus known to arrange at least one damper mounted in the body and comprising two damping push-pieces arranged on either side of the hinge of the control member (here the pedal) and housed in back and forth motion in a damping cavity provided in the body, said damper being intended to damp the tilting of the control member in both directions, said control member pushing one of said damping push-pieces when it tilts in one direction, on one hand, and the other of said damping push-pieces when it tilts in the other direction, on the other hand. Thus, this damper is adapted to damp the tilting of the pedal, and in particular the tilts imposed by a control lever during movement of the civil engineering machine. 
     In a known manner, the damping cavity is generally U-shaped with two vertical portions extending normally opposite the upper face of the body and in which the respective damping push-pieces move, and a central portion forming the connection between the vertical portions and provided with one or several damping pistons. Thus, the damping push-pieces extend normally opposite the upper face of the body so that, once the body is fastened on a horizontal floor, the damping push-pieces extend vertically with the same drawbacks as those mentioned for the control push-pieces. Moreover, such a damping cavity is difficult to produce, at least by simple machining, due to its complex U shape. 
     Generally, the known regulator devices are too high, requiring hydraulic connections at the lower face of the body, and are complex to produce. 
     BRIEF SUMMARY 
     The aim of the invention is in particular all or some of the aforementioned drawbacks, and to that end it proposes a pressure regulator device, in particular of the hydraulic remote-control type, comprising: 
     a body provided with two end faces, lower and upper, respectively, and a peripheral face extending between the two end faces, and comprising at least one so-called control cavity emerging on at least one of said faces and at least one so-called damping cavity emerging on at least one of said faces, 
     a minimum of a pressure reducer mounted in the body and comprising a control push-piece housed in back and forth motion in the at least one control cavity, said pressure reducer being intended to enable the control of at least one receiver outside the regulator device, 
     a control member pivoting relative to the body, at least one hinge mounted on the upper face of said body, in order to control the back and forth movement of the at least one control push-piece, and 
     at least one damper mounted in the body and comprising two damping push-pieces arranged on either side of said hinge and housed in back and forth motion in said at least one damping cavity, said damper being intended to damp the tilting of the control member in both directions, said control member pushing on one hand one of said damping push-pieces when it tilts in one direction, and on the other hand the other of said damping push-pieces when it tilts in the other direction, 
     the device being remarkable in that: 
     the at least one control cavity has one end emerging in the peripheral face of said body, 
     the at least one damping cavity has two ends emerging in the peripheral face of said body on either side of said hinge of the control member, and 
     the control member has portions opposite the peripheral face to face the emerging ends of the control and damping cavities, respectively, from which the control and damping push-pieces emerge, respectively. 
     Thus, the control and damping cavities do not extend normally to the upper face of the body, and therefore vertically once the device is placed flat on a horizontal floor, thereby contributing to limiting the vertical bulk of the device and saving height space. For example, the control and/or damping cavities can extend parallel to the upper face of the body, and therefore horizontally once the device is placed flat on a horizontal floor. 
     Moreover, with such a configuration, the control and damping cavities cannot emerge in the lower face so that it is not necessary to connect the connecting hoses on said lower faces, thereby facilitating the installation of said hoses at the floor of the machine. 
     According to one feature, the regulator device comprises a single rectilinear damping cavity passing all the way through the body and emerging at both of its ends on its peripheral face. 
     Thus, it is easy to make such a damping cavity by simple machining, in a single and same direction. 
     According to another feature, the at least one control cavity is rectilinear and extends substantially parallel or inclined relative to the damping cavity. 
     Likewise, this control cavity is easy to make by machining. 
     According to still another feature, the damping cavity and the at least one control cavity extend in substantially parallel planes. 
     In one particular embodiment, the damper comprises a damping slide slidingly and adjustably mounted in the damping cavity, and in which the damping cavity comprises two work chambers, with a variable volume in the opposite direction, extending between the two opposite ends of said damping slide and guide sleeves immobilized at the emerging ends of the damping cavity to guide the respective damping push-pieces in translation, said work chambers containing a fluid intended to pass from one to the other by means of at least one communication passage under the effect of the thrust from one or the other of the damping push-pieces on said damping slide. 
     Thus, the damping slide is mounted simply between the two damping push-pieces, making it possible to have a linear damper comprising these three pieces successively aligned one after the other. 
     Advantageously, the communication passage comprises at least one restriction zone adapted to create a load loss in said communication passage when it is passed through by fluid flowing between the two work chambers. 
     This communication passage is made either in the damping slide, or in the body. 
     Advantageously, the damping slide comprises, at its two respective ends, two respective end pistons sliding in the damping cavity, connected to each other by a central rod, and against which the respective damping push-pieces abut, and wherein the communication passage between the two work chambers is formed in the damping slide between said two end pistons. 
     Thus, the damping push-pieces, mounted back to back or antagonistically, abut against the two ends of the damping slide. 
     In one particular embodiment, the communication passage comprises two end channels formed in said end pistons and a central channel formed axially in the central connecting rod between the two end pistons, said end channels putting the respective work chambers and the central channel in fluid communication. 
     According to one feature, the central channel passes all the way through the two end pistons, wherein the damping push-pieces are dimensioned to cover the respective emerging ends of the central channel, and wherein the end channels assume the form of grooves formed on the end faces of the respective end pistons and putting the respective work chambers and the respective emerging ends of the central channel in fluid communication. 
     Advantageously, the grooves have a general spiral shape adapted to form a throttle in the flow of the fluid between the respective work chambers and the central channel. 
     According to another feature, the central channel is inwardly provided with two antagonistic jets designed to create load losses in the flow of the fluid inside said central channel. 
     According to another feature, the distribution slide comprises two intermediate pistons sliding in the damping cavity and arranged around the central rod between the end pistons, so that the distribution slide inwardly defines three inner chambers with a constant volume, i.e. two lateral inner chambers arranged between the end pistons and the adjacent intermediate pistons, and a central inner chamber arranged between the two intermediate pistons. 
     In one particular embodiment of the invention, the at least one pressure reducer comprises: 
     a compensation chamber provided in the control cavity and in which the control push-piece is mobile, 
     a return pipe emerging in the compensation chamber and connected to a low pressure fluid source, 
     a distribution channel provided in the control cavity in extension of the compensation chamber with which it is in communication at one of its ends, 
     an intake pipe emerging in the distribution channel and connected to a high pressure fluid source, 
     an outlet pipe connected to the distribution channel and intended to be connected to the outer receiver to control, 
     a plunger able to be moved in translation by the control member, via the control push-piece, inside the compensation chamber, and 
     a distribution slide secured in motion with the plunger between a start position and an end-of-travel position, said distribution slide comprising a blind axial channel emerging at the free end of the slide in the distribution channel in order to communicate with the outlet pipe, said axial channel also communicating with a lateral channel capable of being put selectively in communication with the compensation chamber or the intake pipe to perform the pressure reducing function during movement of the distribution slide in the distribution channel. 
     According to other advantageous features of the invention, considered alone or in combination: 
     the intake pipe of the at least one pressure reducer emerges in the central inner chamber of the damping slide; 
     the device also comprises a connecting pipe for the at least one reducer, said connecting pipe emerging on one hand in the compensation chamber of said reactor and on the other hand in one of the lateral inner chambers of the damping slide; 
     the device comprises two pressure reducers arranged in two respective control cavities, wherein the intake pipes of the two pressure reducers emerge in the central inner chamber of the damping slide, and wherein the connecting pipe of one of the pressure reducers emerges in one of the lateral inner chambers of the damping slide while the connecting pipe of the other of the pressure reducers emerges in the other of the lateral inner chambers of the damping slide; 
     the central rod of the distribution slide includes two channels putting the lateral inner chambers and the central channel in communication, such that the respective compensation chambers of the two pressure reducers are in communication via the connecting pipes, the lateral inner chambers, said communication channels and the central channel. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Other features and advantages of the present invention will appear upon reading the following detailed description of two non-limiting examples of embodiments, done in reference to the appended figures, in which: 
         FIGS. 1 to 8  illustrate a regulator device according to the invention, where the figures are perspective, top, front, side, bottom, vertical cross-sectional along axis VI-VI of  FIGS. 3 and 5 , vertical cross-sectional along axis VII-VII of  FIGS. 3 and 5 , and horizontal cross-sectional along axis VIII-VIII of  FIGS. 3 and 4  views of the device, respectively; 
         FIGS. 9 and 10  illustrate an alternative embodiment of the regulator device according to the invention, where the figures are views of the device identical to  FIGS. 6 and 4 , respectively. 
     
    
    
     DETAILED DESCRIPTION 
     A regulator device according to the invention is described below in reference to  FIGS. 1 to 8 , which more particularly illustrate a regulator device designed for a foot-operated hydraulic remote control, of the hydraulic pedal type, intended for example to control the translation of a civil engineering machine. 
     In reference (X, Y, Z), illustrated in the figures, the various axes are as follows, in reference to the machine intended to be equipped with the regulator device: 
     the X axis indicates the longitudinal direction of the machine corresponding to the normal direction of travel of the machine in a straight line, in other words the direction of translational movement, oriented from back to front; 
     the Y axis indicates the transverse direction of the machine, oriented from right to left, where the two axes X and Y are perpendicular and horizontal; and 
     the Z axis indicates the vertical direction of the machine, oriented from bottom to top. 
     The regulator device is provided to be placed flat on a horizontal floor, i.e. a floor parallel to plane (X, Y), and fastened thereon. The regulator device comprises a body  1  in which two pressure reducers  2  and a damper  3  are housed, and on which a control member  4  is installed. This control member  4  is capable of modifying the pressure regulated by the pressure reducers  2  described below. 
     The body  1  is provided with two end faces, i.e. a lower face  11  and an upper face  10 , as well as a peripheral face  12 , or lateral face, extending between the two end faces  10 ,  11 . The end faces  10 ,  11  extend in a horizontal plane, while the peripheral face  12  extends vertically and forms the perimeter of the body  1 . The body  1  here has a generally parallelepiped shape with rectangular end faces  10 ,  11  and a peripheral face  12  having facets that are also rectangular. 
     The control member  4  assumes the form of a pedal able to be actuated by foot and comprises: 
     a planar base  40  fixedly attached on the horizontal upper face  10  of the body  1 , in particular using fastening screws  41 , and supporting a hinge pin  42  parallel to the transverse direction Y; 
     a pedal  44 , rotatably mounted relative to the base  40  around the hinge pin  42 ; 
     a return means  48 , of the helical spring type, mounted around the hinge pin  42  to return said pedal  44  to the idle position illustrated in the various figures. 
     To support the hinge pin  42 , the base  40  has two rebates  43  protruding normally at the base  40 , where said rebates  43  are parallel to the vertical plane (X, Z) and spaced apart from each other in the transverse direction Y in order to support the transverse hinge pin  42 . 
     The pedal has a general arch or inverted “U” shape and includes: 
     a planar central portion  45  having two rebates  46  parallel to the rebates  43  of the base  40  in order to also support the hinge pin  42 , where the central portion  45  extends horizontally in the idle position and where said central portion  45  offers a support surface for a foot; and 
     two parts laterally folded down  47  opposite each other in the longitudinal direction X, said laterally folded-down portions  47  extending at a right angle relative to the central portion  45 , in a plane parallel to the plane (Y, Z) in the idle position, and coming opposite the peripheral face  12  of the body  1 . 
     The laterally folded-down portions  47  extend parallel to the hinge pin  42  so that, during tilting of the pedal  44 , said laterally folded-down portions  47  more or less approach or move away from the peripheral face  12 , antagonistically, in the direction of the tilting. 
     Several cavities are formed in the body  1 , i.e.: 
     a single damping cavity  30  extending rectilinearly and horizontally in longitudinal direction X, perpendicular to the axis of rotation  42  of the pedal  44 , and emerging at both of its opposite ends  31  in the peripheral face  12  of the body  1 ; and 
     two control cavities  20  also extending rectilinearly and horizontally in the longitudinal direction X, and emerging at both of their respective opposite ends  21  in the peripheral face  12  of the body  1 . 
     The damping cavity  30  assumes the form of a bore with a constant diameter over part of its length and centered around an axis A 3  parallel to the longitudinal direction X; said damping cavity  30  being obtained by a traditional machining technique that is easy to implement. 
     The control cavities  20  assume the form of two successive bores with different diameters and centered around an axis A 1  or A 2  parallel to the longitudinal direction X. 
     Each pressure reducer  2  comprises: 
     a control push-piece  21  housed in back and forth movement in the corresponding control cavity  20 ; 
     a compensation chamber  200  provided in the control cavity  20  and in which the control push-piece  21  is able to move, said compensation chamber  200  corresponding to a bore with a given diameter that is centered around an axis A 1  or A 2  parallel to the longitudinal direction X and that emerges in the peripheral face  12  of the body  1 ; 
     a return pipe  22  emerging in the compensation chamber  200  and connected to a low-pressure fluid source, said return pipe  22  emerging in the lower face  11  of the body  1  and extending parallel to the vertical axis Z; 
     a distribution channel  210  directly extending the compensation chamber  200  with which it is in communication at one of its ends, the distribution channel  210  corresponding to a bore with a diameter smaller than that of the compensation chamber  200 , which is centered around the same axis A 1  or A 2  as the adjacent compensation chamber  200 , and which emerges in the peripheral face  12  of the body  1 , opposite the compensation chamber  200 , with a stopper  211  screwed at the emerging end of said distribution channel  210 ; 
     an intake pipe  23  emerging in the distribution channel  210  and connected to a high-pressure fluid source, said intake pipe  23  being formed by a bore passing through the distribution channel  210 , parallel to the transverse direction Y and emerging in the peripheral face  12  of the body  1 , with a stopper  231  screwed at the emerging end of said intake pipe  23 ; 
     an outlet pipe  24  emerging in the distribution channel  210  and intended to be connected to the outer receptor to be controlled, said outlet pipe  24  emerging in the lower face  11  of the body  1  and extending parallel to the vertical axis Z; 
     a plunger  25  able to be moved in translation, along axis A 1  or A 2 , by the control member  4 , via the control push-piece  21 , inside the compensation chamber  200 ; and 
     a distribution slide  26  secured in movement to the plunger  25  between a starting position and an end-of-travel position, said distribution slide  26  comprising a blind axial channel  260  emerging at the free end of said slide  26  in the distribution channel  210  in order to communicate with the outlet pipe  24 , said axial channel  260  also communicating with a lateral channel  261  capable of being selectively put in communication with the compensation chamber  200  or the inlet pipe  23  to perform the pressure reducing function when the distribution slide  26  is moved in the distribution channel  210 . 
     The fluid circulating in the intake pipe  23  and the fluid circulating in the compensation chamber  200  (and also in the return pipe  22 ) are respectively qualified as high pressure and low pressure relative to each other, independently of any absolute pressure value. 
     The plunger  25  essentially comprises a rod extending between a widened head facing the control member  4  and a connecting foot facing the distribution channel  210 . The connecting foot of the plunger  25  is mounted secured in translation to a first end of the distribution slide  26 ; the second end of said slide  26  corresponding to its free end in which the axial channel  260  emerges. 
     Each reducer  2  also comprises a shell  27  mounted coaxial to the shaft of the plunger  25  while bearing against the lower portion of the broadened head of said plunger  25  to be elastically pushed back using a first return spring  270  against the control plunger  21 . The first return spring  270  is inserted between the shell  27  and a shoulder defined in the control cavity  20 , to push the shell  27  back towards the control push-piece  21 . 
     The reducer  2  may comprise a second return spring  271 , called calibrating or regulator spring, arranged inside the first return spring  270  and inserted between a shoulder of the plunger  25  and the shell  27 . 
     The translational guiding of each control push-piece  21  is ensured by a guide sleeve  28  immobilized at the emerging end of the compensation chamber  200  in the peripheral face  12  of the body  1 ; said guide sleeve  28  being immobilized using a closing plate  280  fastened on the peripheral face  12  of the body  1 , in particular using a screw  281 . Two peripheral grooves are formed in each guide sleeve  28 , respectively at the inner surface and the outer surface of said sleeve  28 , to receive sealing devices in order to ensure the sealing between the control push-piece  21  and the sleeve  28  and body  1 , respectively. 
     The operation of such pressure reducers is well known and will not be described in more detail here. For precisions, one may for example refer to the aforementioned documents FR 2 507 732, FR 2 376 978, FR 2 793 532, FR 2 854 668, FR 2 857 706 and FR 2 835 574. 
     According to one essential feature of the invention, the control cavities  20 , and more particularly the compensation chambers  200 , emerge in the peripheral face  12  of the body  1 , such that the control push-pieces  21  partially protrude outside the peripheral face  12  of the body  1  in order to bear against the respective laterally folded-down portions  47  of the pedal  44 . In this case, one of the control push-pieces  21  protrudes outside the body  1  to bear against one of the laterally folded-down portions  47 , while the other of the control push-pieces  21  protrudes outside the body  1  to bear against the other of the laterally folded-down portions  47 . The control push-pieces  21  move antagonistically, or in the opposite direction in the longitudinal direction X, under the action of the control member  4 . 
     When the pedal  44  tilts in one direction, one of the laterally folded-down portions  47  approaches the peripheral face  12  and pushes the corresponding control push-piece  21  inside the corresponding compensation chamber  200 , while the other of the laterally folded-down portions  47  moves away from the peripheral face  12  while keeping the contact with the other control push-piece  21 , which is pushed towards the outside of the corresponding compensation chamber  200  by the first return spring  270 . When the pedal  44  tilts in the other direction, the movements are reversed. 
     The laterally folded-down portions  47  each support a finger  52  designed to bear against the respective control push-piece  21 ; said finger  52  assuming the form of a screw whereof the head offers a slightly rounded support surface, for the corresponding control push-piece  21 , and the free end of which cooperates with a nut for fastening on the corresponding laterally folded-down portion  47 . 
     The damper  3  comprises: 
     two damping push-pieces  31  housed in back and forth motion in the damping cavity  30  at its respective emerging ends so that the tilting of the control member  4  in one direction pushes one of said damping push-pieces  31  and the tilting in the other direction pushes the other of said damping push-pieces  31 ; and 
     a damping slide  32  slidingly and adjustably mounted in the damping cavity  30  between the two damping push-pieces  31  in order to damp the movements of the damping push-pieces  31  and therefore of the tilting of the control member  4 . 
     The translational guiding of each damping push-piece  31  is ensured by a guide sleeve  38  immobilized at the emerging ends of the damping chamber  30  in the peripheral face  12  of the body  1 ; said guide sleeve  38  being immobilized using the aforementioned closing plate  280 , which is fastened on the peripheral face  12  of the body  1 . Two peripheral grooves are formed in each guide sleeve  38 , respectively at the inner surface and the outer surface of said sleeve  38 , to receive sealing devices in order to ensure the sealing between the damping push-pieces  31  and the respective sleeves  38  and the body  1 , respectively. 
     The damping slide  32  comprises: 
     two end pistons  33  formed at the respective opposite ends of said slide  32 , said end pistons  33  being slidingly mounted in the damping cavity  30 , at its two emerging ends, on one hand, and on the other hand abutting against the respective damping push-pieces  31 ; 
     a central rod  34  connecting the two end pistons  33 , centered on the longitudinal axis A 3 ; and 
     two intermediate pistons  35  formed on the perimeter of the central rod  34  and arranged spaced apart from each other between the two end pistons  34 , said intermediate pistons  35  on one hand being slidingly mounted in the damping cavity  30  and on the other hand each provided with a peripheral groove formed on the outer surface of said intermediate pistons  35  to receive the sealing devices. 
     The damping cavity  30  thus comprises two work chambers  300 , with variable volume in opposite directions (in other words whereof the volumes vary antagonistically), extending between the two opposite end pistons  33  and the adjacent guide sleeves  38 ; said work chambers  300  containing a fluid intended to go from one to the other via at least one communication passage under the effect of the thrust from one or other of the damping push-pieces  31  on one or the other of the end pistons  33  of the damping slide  32 . 
     The damping push-pieces  31 , mounted back to back or antagonistically, abut against the two end pistons  33  of the damping slide  32 , and move in said work chambers  300 . 
     In reference to  FIG. 7 , when the pedal  44  tilts towards the left, in other words pivots in the counterclockwise direction, the left laterally folded-down portion  47  pushes the left damping push-piece  31  inside the damping cavity  30 , the damping push-piece  31  thus pushes the damping slide  32  to the left, said damping slide  32  thus pushes the right damping push-piece  31  outside the damping cavity  30 , so that said right damping push-piece  31  thus remains in contact with the right laterally folded-down portion  47 , which moves away from the peripheral face  12  of the body  1 . Thus, the volume of the left work chamber  300  increases while that of the right work chamber  300  decreases, such that a fluid portion contained in the right work chamber  300  goes into the left work chamber  300 . 
     According to another essential feature of the invention, the damping cavity  30  emerges at both of its ends in the peripheral face  12  of the body  1 , such that the damping push-pieces  31  protrude partially outside the peripheral face  12  of the body  1  in order to bear against the respective laterally folded-down portions  47  of the pedal  44 . In that case, one of the damping push-pieces  31  protrudes outside the body  1  to bear against one of the laterally folded-down portions  47 , while the other of the damping push-pieces  31  protrudes outside the body  1  to bear against the other of the laterally folded-down portions  47 . The damping push-pieces  31  move antagonistically, or in the opposite direction in the longitudinal direction X, under the action of the control member  4 . 
     The laterally folded-down portions  47  each bear a finger  53  designed to bear against the respective damping push-piece  31 ; said finger  53  assuming the form a screw whereof the head offers a support surface, slightly rounded, for the corresponding damping push-piece  31 , and the free end of which cooperates with a nut for fastening on the corresponding laterally folded-down portion  47 . Thus, each laterally folded-down portion  47  supports two fingers  52 ,  53  side by side and extending in a longitudinal plane. 
     The damping slide  32  inwardly defines three inner chambers with a constant volume, i.e.: 
     a central inner chamber  320  arranged between the two intermediate pistons  35 , around the central rod  34 ; and 
     two lateral inner chambers  321 , arranged between the end pistons  33  and the adjacent intermediate pistons  35 , around the central rod  34 . 
     Moreover, the damping slide  32  comprises a longitudinal (or axial) central channel  340  formed in the central rod  34 ; said central channel  340  passing through the central rod  34  over the entire length thereof and also passing through the two end pistons  33  such that said central channel  340  has two ends  341  emerging in the end pistons  33 . The central channel  340  is also inwardly provided with two antagonistic jets  342  designed to create load losses in the flow of the fluid inside said central channel  340 ; said jets  342  are formed substantially inside the end pistons  33 . 
     The damping slide  32  comprises two radial channels  344  formed in the central rod  34  and putting the central channel  340  in communication with the respective lateral inner chambers  321 ; said radial channels  344  being arranged between the two jets  342  and emerging in the respective lateral inner chambers  321  and in the central channel  340 . 
     Moreover, the damping slide  32  comprises two end channels  343  formed in said end pistons  33  in order to put the respective work chambers  300  and the central channel  340  in fluid communication. The end channels  343  are made in the form of grooves formed on one of the end faces of the respective end pistons  33 , corresponding to the end faces of the damping slide partially defining the work chambers  300 , and putting said respective work chambers  300  and the respective emerging ends  341  of the central channel  34  in fluid communication. 
     The damping push-pieces  31  are sized to cover the respective emerging ends  341  of the central channel  34  such that, when the damping push-pieces  31  are moved, the fluid circulates between the work chambers  300  and the central channel  340  via the respective grooves  343 , and not directly in the emerging ends  341  that are plugged. The grooves  343  have a general spiral shape adapted to form a throttling in the flow of the fluid between the respective work chambers  300  and the central channel  340 , in order to participate in the desired damping of the movement of the push-pieces  31 . The spiral grooves  343  thus have a first end far enough from the axis A 3  so as not to be obstructed by the corresponding damping push-piece  31 , and a second end emerging in the respective emerging end  341  of the central channel  340 . 
     Thus, the passage of fluid between the two work chambers  300  comprises the grooves  343  and the central channel  340 , with four restriction zones in the flow of the fluid, i.e. the two jets  342  and the two spiral grooves  343 . 
     Several communications are provided between the reducers  2  and the damper  3 . 
     First, the intake pipes  23  of the reducers  2  emerge in the central inner chamber  320  of the damping slide  32 . Thus, the intake pipes  23  of the two reducers  2  are made in the form of a single bore passing through the body  1  on either side along the transverse direction Y. As a reminder, the intake pipes  23  are connected to a high pressure fluid source. To that end, a main intake pipe  290  emerges on one hand in the central inner chamber  320  of the damping slide  32 , and on the other hand in the lower face  11  of the body  1  to be connected to a low-pressure fluid source; said main intake pipe  290  extending parallel to the vertical axis Z. 
     Secondly, the device comprises two connecting pipes  291  to put the compensation chambers  200  of the two reducers  2  in communication, i.e.: 
     a first connecting pipe  291  emerging on one hand in the compensation chamber  200  of one of the reducers  2 , and on the other hand in one of the distal inner chambers  321  of the damping slide  32 ; 
     a second connecting pipe  291  emerging on one hand in the compensation chamber  200  of the other of the reducers  2 , and on the other hand in the other of the distal inner chambers  321  of the damping slide  32 . 
     The connecting pipes  291  are made in the form of bores parallel to the transverse direction Y, passing through the respective compensation chambers  200 , and emerging in the peripheral face  12  of the body  1 , with a stopper  292  screwed at the respective emerging ends of said connecting pipes  291 . 
     Moreover, as described above, the two distal inner chambers  321  of the damping slide  32  are in communication via the radial channels  344  and the central channel  340 . In this way, the compensation chambers  200  of the two reducers  2  are in fluid communication via the two connecting pipes  291 , the two distal inner chambers  321 , the two radial channels  344  and the central channel  340 . Thus, as visible in  FIG. 5 , only one of the reducers  2  includes a return pipe  22  emerging in the lower face  11  of the body  1  to be connected to a low pressure fluid source. 
     In the embodiment illustrated in  FIGS. 1 to 8 , the axes A 1  and A 2  of the reducers  2 , the control cavities  20  and the control pistons  21  are horizontal and parallel to the longitudinal direction X. 
     In the embodiment illustrated in  FIGS. 9 and 10 , the axes A 1  and A 2  of the reducers  2 , the two control cavities  20  and the two control pistons  21  are inclined relative to the longitudinal direction X symmetrically relative to the median plane parallel to the plane (Y, Z). Thus, the axis A 1  is inclined relative to the longitudinal direction X by an angle α given in degrees, while the axis A 2  is inclined relative to the longitudinal direction X by an angle of (180−α) in degrees. The angle α is greater than or equal to 0 degrees (embodiment illustrated in  FIGS. 1 to 8 ) and strictly less than 90 degrees, preferably between 0 and 45 degrees, or even between 0 and 25 degrees, for reasons of vertical bulk. Indeed, a slight incline of the axes A 1  and A 2  makes it possible to improve the control of the pedal  44  on the control push-pieces  21 . 
     Thus, the regulator device according to the invention makes it possible to reduce the overall height of the device, in particular by reducing the height of the body  1 , and to make cavities inside the body  1  simply, with or without through bores. It also makes it possible to ensure the damping in both directions of tilting of the control member  4  using a single damping slide  32 , of the piston type, mounted in a rectilinear damping cavity  30 . 
     Moreover, the outlet pipe  24  described in reference to  FIGS. 1 to 8  was made in the form of a vertical bore emerging in the lower face  11 , but it could be done in the continuation of the distribution channel  210 , along the longitudinal axis Y, instead and in place of the end that emerges in the peripheral face  12  and which is plugged by the screw  211 , as is the case in the embodiment illustrated in  FIGS. 9 and 10 . In this case, the outer receiver is connected at the peripheral face  12  of the body  1 . 
     Of course, the example embodiment mentioned above is in no way limiting and other details and improvements can be made to the regulator device according to the invention, without, however, going beyond the scope of the invention where other forms of pressure reducer and/or damper can be carried out.

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