• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a hydraulic pump (1) in which the cylinder (20) is slidably connected to the shaft (30) and rotated by the shaft (30), and in which a housing (27) is provided. in the barrel (20), the shaft (30) sliding in said housing (27) protruding from the front face (23) of the barrel (20), said housing (27) and the shaft (30) defining between a balancing chamber (90), said balancing chamber (90) being connected to the discharge port (10, 110), so that the fluid in the balancing chamber (90) exerts on the barrel (20), a pressing force tending to apply the barrel (20) against the dispensing ice (80).
    公开号:FR3059731A1
    申请号:FR1662061
    申请日:2016-12-07
    公开日:2018-06-08
    发明作者:Louis Claude Porel
    申请人:Hydro Leduc SAS；
    IPC主号:
    专利说明:

    Technical area
    The present invention relates to the field of hydraulic pumps with axial pistons.
    Technological background
    Hydraulic pumps with an inclined plate, or bias plate, actuating axial pistons have been known for a long time.
    It is known to use for this kind of pump what is called a distribution by ice, the pistons being carried by a barrel driven in rotation, the rear face of said barrel being applied by a spring against a glass, constituted by a disc with arched holes.
    The discharge pressure exerts on the surface of the barrel facing the distribution lumen connected to the outlet, a force proportional to the discharge pressure and the surface of the distribution lumen. This force tends to separate the barrel from the distribution glass if it is in excess of the thrust exerted by the pistons of the pump.
    Furthermore, the discharge pressure exerts, on the bottom wall of the piston housings, a force proportional to the number of pistons subjected to the discharge pressure. However, the number of pistons subjected to the discharge pressure varies during the rotation of the barrel.
    Consequently, the force exerted on the barrel and tending to apply the barrel against the distribution glass varies during the rotation of the barrel, which disturbs the operation of the hydraulic pump and can accelerate the aging of the distribution glass. .
    The known solution consisting in increasing the number of pistons to reduce the variation in the force tending to apply the barrel against the distribution glass during the rotation of the barrel is not satisfactory because it contributes to increasing the manufacturing cost of Sa pump.
    summary
    A basic idea of the invention is to provide a hydraulic pump with axial pistons in which the variation in the force applying the barrel against the distribution glass is reduced, even for a pump having a small number of pistons.
    According to one embodiment, the invention provides a hydraulic pump comprising:
    - a casing, in which are formed a first orifice and a second orifice, one of the first and second orifices being an inlet orifice, the other orifice being a discharge orifice,
    - a shaft rotatably mounted in the housing,
    - a bias plate fixed to the housing,
    - a barrel in sliding connection with the shaft and driven in rotation by the shaft around an axis, piston housings being provided in the barrel,
    - at least three pistons each sliding in one of the piston housings, its pistons projecting with respect to the front face of the barrel and bearing against the bias plate,
    a dispensing glass bearing against the rear face of the barrel, the dispensing crystal being provided with a first lumen connected to the first orifice, and a second lumen connected to the second orifice, a housing being formed in the barrel, l 'shaft being engaged in said housing projecting from the front face of the barrel, said housing and the shaft defining therebetween a balancing chamber, said balancing chamber being connected to the outlet orifice through ié casing, so that the fluid in the balancing chamber exerts, on the barrel, a pressure force tending to apply the barrel against the distribution glass.
    The pressure force exerted by the fluid in the balancing chamber tends to bring the barrel closer to the distribution glass. This force does not vary with its rotation of the barrel relative to the distribution glass. Hydrostatic balancing of the barrel can be achieved by appropriately dimensioning the sections of the piston housings and the balancing chamber. Thanks to these provisions, it is possible to construct a distribution ice pump having a small number of pistons, for example three.
    According to embodiments, such a pump can include one or more of the following characteristics.
    According to one embodiment, the hydraulic pump comprises a key placed between a longitudinal groove made in the shaft and a hole made in the barrel, so that the key makes the sliding connection between the barrel and the shaft.
    According to one embodiment, the shaft has longitudinal grooves, a cylindrical longitudinal wall of the housing having complementary grooves, the grooves of the shaft and its grooves of the housing together forming the sliding connection.
    According to one embodiment, a cavity is formed in the shaft, its cavity opening from the rear end of the shaft into the housing formed in the barrel.
    According to one embodiment, the hydraulic pump further comprises a seal interposed between a cylindrical longitudinal wall of the housing and the shaft. The seal seals the balancing chamber while allowing the shaft to translate relative to the barrel.
    According to one embodiment, a balancing duct is formed in the barrel, said balancing duct connecting the balancing chamber to its rear face of the barrel, the dispensing glass having a balancing orifice connected to the orifice delivery through housing, said balancing orifice being attached to the balancing duct. The balancing pipe and the balancing port connect the balancing chamber to the discharge port.
    According to one embodiment, the balancing duct and the balancing orifice are centered on the axis. In this way, the balancing duct and the balancing hole are always aligned during the rotation of the shaft.
    According to one embodiment, the cross section Σ of the balancing chamber, the cross section s of a piston, the section S of the distribution lumen, the surface S 2 of the area of the rear face of the barrel subjected to a pressure between the discharge pressure P and the pressure prevailing in the pump casing ,, and N Se number of pistons of the pump, check the following equation:
    ΣΝ- 1 + “
    S-
    This equation guarantees that the barrel remains pressed against the distribution glass.
    According to one embodiment, the cross section of the balancing chamber is greater than twice the cross section of a piston. Thus, the pressure force exerted by the liquid in the balancing chamber on the barrel is large compared to its pressure force exerted by the liquid on the bottom wall of the piston housings and the variation of the force tending to bring the barrel closer together. distribution ice during shaft rotation is negligible.
    According to one embodiment, the hydraulic pump is capable of operating in the two directions of rotation of the shaft. In a first direction of rotation of the shaft, the first orifice constitutes the inlet orifice and the second orifice constitutes the discharge orifice, and in the second direction of rotation of the shaft, the second orifice constitutes the inlet port and the first port constitutes the discharge port. The pump also comprises a valve housed in the casing and is configured to selectively connect the balancing chamber to the first or to the second orifice, depending on the direction of rotation of the shaft. Thus, in the two configurations corresponding to the two operating directions of the pump, the balancing chamber can be placed in fluid communication with the discharge orifice, so that the fluid in the balancing chamber is at the discharge pressure.
    According to one embodiment, the balancing chamber is connected to the first port by a first pipe and to the second port by a second pipe, this valve being able to be produced by a free ball of a diameter greater than the diameter of the first and second pipes. , so that the ciapet is pressed by the pressure of the liquid discharged through the discharge orifice against the entry of its pipe connected to the intake orifice. Thus, in the two configurations corresponding to the two directions of operation of the pump, the balancing chamber is automatically placed in fluid communication with the discharge orifice, so that the fluid in the balancing chamber is at the discharge pressure.
    According to one embodiment, the hydraulic pump further comprises a return member bearing, on the one hand, against the shaft, and on the other hand, against the barrel, to exert an elastic force tending to apply the barrel against Its distribution ice. The return member keeps the barrel pressed against the dispensing glass when the pump delivers without pressure.
    According to one embodiment, the hydraulic pump comprises a thrust bearing supporting and guiding in rotation the shaft and limiting the translation of the shaft relative to the casing in the direction of the axis at least in the direction away from the shaft of the barrel. The pressure force exerted by the fluid in the balancing chamber tends to move the shaft away from the barrel. The translation of the shaft relative to the casing being constrained by the thrust bearing, the pressure force tends to bring the barrel closer to the distribution glass.
    According to one embodiment, the shaft is provided with a flange resting on a rear face of the thrust bearing. The flange abuts on the rear face of the bearing, thus limiting the movement of the shaft Se along its axis in the direction away from the shaft from its distribution glass.
    Brief description of the figures
    The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly during the following description of several particular embodiments of the invention, given solely by way of illustration and without limitation. , with reference to the accompanying drawings.
    FIG. 1 is a view in longitudinal section of a hydraulic pump according to an embodiment of the invention in a first configuration,
    FIG. 2 is a view in longitudinal section of the hydraulic pump of FIG. 1 in a second configuration,
    FIG. 3 is a cross-sectional view of the pump of FIG. 1 according to the section plane AA identified in FIG. 1,
    FIG. 4 is a cross-sectional view of the pump of FIG. 1 according to the cutting plane BB identified in FIG. 1,
    - Figure 5 is a longitudinal sectional view of a hydraulic pump according to an embodiment of the invention in which the peripheral zone is delimited by an elevation of the rear face of the barrel.
    - Figure 6 is a longitudinal sectional view of a hydraulic pump 5 according to an embodiment of the invention in which the peripheral zone is delimited by an elevation of the front face of the dispensing glass.
    Detailed description of embodiments
    FIG. 1 represents a hydraulic pump 1 comprising a hollow cylindrical casing 100, one rear end of which is closed by a cylinder head 101 and in which are formed a first 10 and a second orifice 1110. A shaft 30, a barrel 20, pistons 3, a bias plate 40, and a distribution glass 80 are housed in the casing 100.
    In particular, the pump can be a reversible pump, that is to say that it can operate in two configurations, a first configuration, illustrated by FIG. 1, in which the shaft 30 rotates clockwise, the first orifice 10 being the inlet orifice, the second orifice 110 being the discharge orifice, and a second configuration, illustrated by FIG. 2, in which the shaft rotates anticlockwise, the second orifice 110 being the intake port, the first port 10 being the discharge port.
    In the following text, we will describe the pump in the first configuration, it being understood that it works similarly in the second configuration.
    The shaft 30 is driven in rotation relative to the housing 100. The barrel 20 25 is driven by the shaft 30 in rotation relative to the housing 100 about an axis of rotation A. The barrel 20 is a cylinder of circular section . The casing 100 forms a bearing 51 supporting and guiding in rotation the barrel 20,
    The axis of rotation A of the barrel is generally parallel to the axis of the shaft 30 but a bent shaft would be possible as a variant. In the rest of the text, the terms “front” and “rear” refer to this axis oriented in the direction of the barrel 20 towards the shaft 30.
    The distribution glass 80 is a disc integral with the casing 100 and disposed in a plane transverse to the axis A. The distribution glass 80 has two holes in a circular arc, hereinafter called first 70 and second 170 distribution light 170 , symmetrically arranged with respect to the axis A.
    N is the number of pistons 3. The pistons 3 are usually in an odd number. In particular, the pistons can be three in number. Piston housings 22 are provided in the barrel 20. The piston housings 22 are angularly regularly distributed on a circle centered on the axis of the barrel 20. A piston housing 22 is a cylindrical housing oriented along an axis parallel to the axis of the barrel. A piston housing 22 is defined by a longitudinal cylindrical wall and a bottom wall. A piston channel 24 formed in the barrel 20 connects the bottom wall of the piston housing 22 to the rear face 21 of the barrel. The piston channels 24 are distributed on a circle centered on the axis of the barrel 20 and the diameter of which is between the internal and external diameters of the distribution ports 70 and 170. When the barrel 20 rotates, the piston channels 24 pass alternately in front of the two distribution lights 70 and 170.
    Each piston 3 slides in one of the piston housings 22 of the barrel
    20. The pistons 3 project from a front face 23 of the barrel 20 and bear against the bias plate 40, for example by means of sliding pads 50. The bias plate 40 is fixed to the casing 100 so as to form an angle, called the cam angle, with respect to a plane transverse to the shaft 30. The bias plate 40 plays the role of a cam which imposes on the pistons 3 a reciprocating movement When the rotation of the 'shaft 30. The cam angle is a parameter which determines the quantity of liquid pumped at each revolution of the shaft. In particular, in an embodiment not shown, the cam angle can be adjustable, the pump 1 comprising a mechanism for adjusting the cam angle, such mechanisms being known and will not be described in more detail.
    One of the distribution lights, called the inlet light 70, is connected to the inlet port 10, the other, called the discharge light 170, is connected to the discharge port 110. The liquid is sucked by the inlet light 10 and discharged by the discharge light 110.
    Referring to FIG. 4, S designates the section of the dispensing lumen 70. P designates the pressure of the liquid discharged through the discharge orifice, called the discharge pressure. The pressure exerted on the area of the rear face of the barrel facing the distribution lumen, called the bearing area, is equal to the discharge pressure P. The pressure exerted on the area of the rear face of the barrel surrounding the support zone, called the peripheral zone (delimited in dotted lines in FIG. 4), decreases between a value equal to the discharge pressure P at the junction with the support zone, to a value equal to Sa pressure which adjusts in the pump casing at the level where the rear face of the barrel is not in contact with the distribution glass. S 2 designates its surface of the peripheral zone. The peripheral zone can be delimited by an elevation 201 of the rear face of the barrel around the mouth of the piston channels 24 and of the balancing channel 28 (as illustrated in FIG. 5) and / or of an elevation 801 of the front face of the distribution glass around the distribution lights 70 and 170 and the balancing light 89 (as illustrated in FIG. 6). The pressure force exerted by the fluid on the support section and tending to move the barrel 20 away from the dispensing glass 80 is written PS + ^ S 2 . If s denote the cross section of the pistons 3 and n the number of pistons 3 subjected to its discharge pressure, the pressure force exerted by the fluid on the bottom wall of the piston housings and tending to bring the barrel 20 closer to distribution glass 80 is written Pns. During the rotation of the pump, the number of pistons 3 subjected to the discharge pressure alternates between ~ and N being the number of pistons of the pump.
    The barrel 20 is in sliding connection (also called sliding connection) with the shaft 30, that is to say that the barrel 20 is linked in rotation but free in translation relative to the shaft 30 along the axis A.
    To this end, the shaft 30 may have a longitudinal groove 33, the barrel 20 having a hole 29, optionally through, a key 25 being placed between the longitudinal groove 33 formed in the shaft 30 and the hole 29 formed in the barrel 20, so that the key 25 is integral with the barrel 20 and free in translation along the longitudinal groove 33.
    Alternatively, the shaft 30 may have longitudinal grooves, the longitudinal cylindrical wall of the housing 27 having grooves complementary to those of the shaft 30, the grooves of the shaft 30 and the grooves of the housing 27 together forming a sliding connection.
    The translation of the shaft 30 relative to the casing 100 in the direction of the axis A is limited at least in the direction separating the shaft 30 from the barrel 20. For this purpose, the pump comprises a thrust bearing 31, supporting and guiding the shaft 30 in rotation. The rotation of the shaft 30 relative to the thrust bearing 31 can in particular be facilitated by bearings. The thrust bearing 31 furthermore maintains the shaft 30 in its axial direction and prevents the shaft 30 from moving along its axis A in the direction away from the shaft from the distribution glass. In particular, the shaft 30 can be provided with a flange 32 resting on a rear face 39 of the bearing 31 and possibly a counter-grain. The counter grain is for example made of treated steel and can be provided with grooves to create an oil film which facilitates rotation. The flange 32 can be cut in the mass of the shaft or added in a radial groove formed in the shaft 30. The thrust bearing 31 can also be adapted to avoid displacement of the shaft 30 along its axis A in the direction bringing the shaft closer to the distribution glass. To this end, the shaft 30 can, in particular, be provided with a second flange (not shown) resting on a front face of the bearing 31, the second flange being similar to that described above.
    A housing 27 of cross section complementary to the cross section of the shaft 30 is formed in the barrel 20. The shaft 30 slides in the housing 27 projecting from the front face 23 of the barrel 20. The housing 27 is defined by a cylindrical longitudinal wall and a bottom wall. A seal 26, and in particular a scraper lip seal, can be interposed between the cylindrical longitudinal wall of the housing 27 and the shaft 30, and in particular disposed in a radial groove formed in the shaft 30, to ensure the sealing of the sealing chamber 90 while allowing the translation of the shaft 30 relative to the barrel 20.
    The shaft 30 and the barrel 20 together form a piston system. The tree
    30 and the barrel 20 define between them a balancing chamber 90. The displacement of the shaft 30 relative to the barrel 20 causes a variation in the volume of the balancing chamber 90.
    W
    A cavity 35 can be formed in the shaft 30, said cavity 35 opens from the end of the shaft 30 inserted in the housing 27 formed in the barrel.
    The balancing chamber 90 is in fluid communication with the discharge port 5 of the pump so that the balancing chamber 90 is always filled with fluid at the discharge pressure.
    To this end, a balancing conduit 28 formed in the barrel 20 opens, on the one hand, on the bottom wall of the housing 27, and on the other hand, on the rear face 21 of the barrel 20. The conduit balancing 28 is centered on the axis A. The dispensing glass 80 has a balancing orifice 89 centered on the axis A. The balancing orifice 89 is attached to the balancing conduit 28 formed in the barrel 20. The balancing orifice 89 communicates with the discharge orifice 110 of the pump through one or more channels provided in the cylinder head 101.
    In the case of a pump operating in its two directions, the balancing orifice 89 is connected to the orifice 10 by a first pipe 84, and to the orifice 110 by a second pipe 83, and the pump comprises a valve 85 configured to selectively connect the balancing orifice 89 to the first pipe 84 or to its second pipe 83.
    In particular, the pipes 83 and 84 can be connected to a valve chamber 86, a third inlet of which communicates with the balancing orifice 89 via a channel 88. The valve 85 is arranged in said valve chamber 86, the valve 85 then being an object suitable for closing the entry of the pipes 83 and 84. The valve 85 can in particular be a ball of a size greater than the diameter of the pipes 83 and 84.
    Thus, as illustrated in FIG. 2, when its pump rotates in a direction for which the pressurized liquid is discharged through the orifice 10, the valve 85 is pressed against the inlet of the second pipe 83 by the discharge pressure. so that the valve closes off its second pipe 83. The balancing chamber 90 is therefore in fluid communication with the orifice 10 which is the delivery orifice. The fluid in the balancing chamber 90 is therefore at the discharge pressure.
    Likewise, as illustrated in FIG. 1, when the pump rotates in a direction for which liquid under pressure is discharged through the orifice 110, the valve 85 is pressed by the discharge pressure against the inlet of the first pipe 84 so that the valve 85 closes the first pipe 84. The balancing chamber 90 is therefore in fluid communication with the orifice 110 which is the delivery orifice. The fluid in the balancing chamber 90 is therefore at the discharge pressure.
    In the two configurations corresponding to the two directions of operation of the pump, the fluid contained in the balancing chamber 90 is at the discharge pressure.
    The pressure force exerted by the fluid in the balancing chamber 90 tends to move the shaft 30 away from the barrel 20. The translation of the shaft 30 relative to the casing 100 being constrained by the thrust bearing 31, the force of pressure tends to bring the barrel 20 closer to the distribution glass 80.
    The pressure force exerted by the pressurized liquid in the balancing chamber 90 on the barrel 20 does not vary with the rotation of the barrel 20 relative to the distribution glass 80. If the cross section of the chamber is designated balancing 90, the pressure force exerted by the pressurized liquid in the balancing chamber 90 on the barrel 20 is written by "cross section £ of the balancing chamber" means the maximum cross section of the balancing chamber 90. This is equal to the cross section of the housing 27.
    From a dimensional point of view, the hydraulic pump must check the following equation, which guarantees that the barrel remains pressed against the distribution glass:
    ΣΝ - 1 + -zr s
    S 2 > s + 7 ~~ corresponding to the smallest number of pistons subjected to the discharge pressure during the rotation of the pump, and preferably, the following equation which guarantees the balancing of the pump:
    ΣΝ- 1 + -ΊΓ 5
    With R between 0.8 and 0.99.
    The pump is thus hydrostatically balanced, which makes it possible to prevent the discharge pressure, which creeps in between its rear face 21 of the barrel 20 and the dispensing glass 80, separating the barrel 20 and the dispensing glass 80.
    Furthermore, its pressure force exerted by the liquid on the bottom wall of the 5 piston housings 22 is proportional to the number of pistons subjected to the discharge pressure, and as the number of pistons subjected to the discharge pressure varies during of the barrel rotation, Its force exerted on the barrel and tending to apply the barrel against the distribution glass varies during the barrel rotation, which disturbs the operation of the hydraulic pump. The cross section £ of the balancing chamber 90 is preferably greater than twice its cross section s of a piston 3, and even more preferably greater than ten times the cross section s of a piston 3, which makes it possible to avoid excessive variations in the force tending to bring the barrel closer to the distribution glass. Indeed, if the cross section Σ of the balancing chamber 90 is large in front of the cross section s of a piston 3, then the pressure force exerted by the pressurized liquid in the balancing chamber 90 on the barrel 20 is large compared to the pressure force exerted by the liquid on the bottom wall of the piston housings 22 and the variation of the force tending to bring the barrel 20 closer to the distribution glass 80 during the rotation of the shaft 30 is negligible. Thanks to these provisions, the hydrostatic balancing of the barrel 20 can be achieved by an appropriate dimensioning of the sections of the piston housings 22 and of the balancing chamber 90. Thanks to these provisions, the holding of the distribution glass 80 is not faulted.
    The rear face 21 of the barrel 20 can also be held in abutment against the dispensing glass 80 by a return member 9, typically a compression spring, such as a helical spring, in abutment, on the one hand, against the 'shaft 30, and secondly, against the barrel 20. In particular, the return member 9 may be arranged in the housing 27 and resting, on the one hand, against the bottom wall of the cavity 35 formed in the shaft 30, and on the other hand, against the bottom wall of the housing 27 formed in the barrel 20. The return member 9 keeps the barrel in abutment against the timing glass when the hydraulic pump does not is not in operation
    Although the invention has been described in connection with a particular embodiment, it is obvious that it is in no way limited thereto and that it includes all the technical equivalents of the means described as well as their combinations if these fall within the scope of the invention.
    The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps than those stated in a claim. The use of the indefinite article "one" for an element does not exclude, unless otherwise stated, the presence of a plurality of such elements.
    In the claims, any reference sign in parentheses cannot be interpreted as a limitation of the claim.
    权利要求:
    Claims (14)
    [1" id="c-fr-0001]
    1. Hydraulic pump (1) comprising:
    - a casing (100), in which are formed a first orifice (10) and a second orifice (110), one of the first and second orifices being an orifice
    5 inlet (10, 110), the other opening being a discharge opening (10, 110),
    - a shaft (30) rotatably mounted in the casing (100),
    - a bias plate (40) fixed to the casing (100),
    - a barrel (20) in sliding connection with the shaft (30) and driven in rotation by the shaft (30) around an axis (A), piston housings (22) being provided
    10 in the barrel (20),
    - At least three pistons (3) each sliding in one of the piston housings (22), the pistons (3) projecting from a front face (23) of the barrel (20) and bearing against the bias plate (40) ,
    - a distribution glass (80) bearing against the rear face (21) of the barrel, the distribution glass (80) being provided with a first lumen (70) connected to the first orifice (10), and with a second light (170) connected to the second orifice (10, 110), a housing (27) being formed in the barrel (20), the shaft (30) being engaged in said housing (27) projecting from the front face (23) barrel
    20 (20), said housing (27) and the shaft (30) defining between them a balancing chamber (90), said balancing chamber (90) being connected to the discharge orifice (10, 110) through the casing (100), so that the fluid in the balancing chamber (90) exerts, on the barrel (20), a pressing force tending to apply the barrel (20) against the distribution glass (80 ).
    25
    [2" id="c-fr-0002]
    2. Hydraulic pump according to claim 1, comprising a key (25) placed between a longitudinal groove (33) formed in the shaft (30) and a hole (29) formed in the barrel (20), so that the key (25) makes the sliding connection between the barrel (20) and the shaft (30).
    [3" id="c-fr-0003]
    3. Hydraulic pump according to claim 1, in which the shaft
    30 (30) has longitudinal grooves, a cylindrical longitudinal wall of the housing (27) having complementary grooves, the grooves of the shaft (30) and the grooves of the housing (27) together forming the sliding connection.
    [4" id="c-fr-0004]
    4. Hydraulic pump according to one of the preceding claims, in which a cavity (35) is formed in the shaft (30), the cavity (35)
    [5" id="c-fr-0005]
    5 emerging from the rear end of the shaft (30) in the housing (27) formed in the barrel (20).
    5. Hydraulic pump according to one of the preceding claims, further comprising a seal (26) interposed between a cylindrical longitudinal wall of the housing (27) and the shaft (30).
    10
    [6" id="c-fr-0006]
    6. Hydraulic pump according to one of the preceding claims, in which a balancing duct (28) is formed in the barrel (20), said balancing duct (28) connecting the balancing chamber (90) to the rear face (21) of the barrel (20), the distribution glass (80) having a balancing orifice (89) connected to the delivery orifice (10, 110) through the casing (100), said orifice
    15 balancing (89) being attached to the balancing conduit (28).
    [7" id="c-fr-0007]
    7. Hydraulic pump according to the preceding claim, wherein the balancing duct (28) and the balancing orifice (89) are centered on the axis (A).
    [8" id="c-fr-0008]
    8. Hydraulic pump according to one of the preceding claims,
    20 in which the cross section X of the balancing chamber (90), the cross section s of a piston (3), the section S of the distribution lumen (70), the area S 2 of the area of the rear face of the barrel subjected to a pressure between the discharge pressure P and the pressure prevailing in the pump casing, and N the number of pistons of the pump, verify the following equation:
    [9" id="c-fr-0009]
    9. Hydraulic pump according to one of the preceding claims in which the cross section X of the balancing chamber (90) is greater than twice the cross section s of a piston (3).
    [10" id="c-fr-0010]
    10. Hydraulic pump according to one of the preceding claims, capable of operating in its two directions of rotation of the shaft, in
    30 which, in a first direction of rotation of the shaft, the first orifice (10) constitutes the inlet orifice and the second orifice (110) constitutes the discharge orifice, and in the second direction of rotation of the 'shaft, the second orifice (110) constitutes the intake orifice and the first orifice (10) constitutes the discharge orifice, further comprising a valve (85) housed in the casing (100) and configured to selectively connect the balancing chamber (90) at the first (10) or at the second (110) orifice, depending on the direction of rotation of the shaft.
    [11" id="c-fr-0011]
    11. Hydraulic pump according to the preceding claim, in which its balancing chamber (90) is connected to the first orifice (10) by a first pipe (84) and to the second orifice (110) by a second pipe (83), ie valve (85) being a ball of a diameter greater than the diameter of the first (84) and second (83) pipes, so that the valve (85) is pressed by the pressure of the liquid discharged through the delivery port (10, 110) against the inlet of the pipeline (83, 84) connected to the intake port (10, 110).
    [12" id="c-fr-0012]
    12. Hydraulic pump according to one of the preceding claims, further comprising a return member (9) bearing, on the one hand, against the shaft (30), and on the other hand, against the barrel (20) , to exert an elastic force tending to apply the barrel (20) against the dispensing glass (80).
    [13" id="c-fr-0013]
    13. Hydraulic pump according to one of the preceding claims, comprising a thrust bearing (31) supporting and guiding in rotation the shaft (30) and limiting the translation of the shaft (30) relative to the casing (100) in the direction of the axis (A) at least in the direction moving the shaft (30) away from the barrel (20).
    [14" id="c-fr-0014]
    14. Hydraulic pump according to the preceding claim, wherein the shaft (30) is provided with a flange (32) supported on a rear face (39) of the thrust bearing (31).
    <ν <ψ
    1/3
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    FR2773197A1|1999-07-02|HYDRAULIC CYLINDER WITH A PISTON PROVIDED WITH A SHOCKING SEGMENT
    同族专利:
    公开号 | 公开日
    US20180156207A1|2018-06-07|
    US10690124B2|2020-06-23|
    FR3059731B1|2019-05-10|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1179738A|1956-07-26|1959-05-27|Gusswerk Paul Saalmann & Sohn|Improvements to axial piston pumps|
    US3110267A|1958-06-30|1963-11-12|Linde Eismaschinen Ag|Axial piston pumps and motors with rotary cylinder blocks|
    US4142450A|1976-01-13|1979-03-06|Thoma Jean U|Axial piston rotary hydraulic machines|
    US2608158A|1945-06-08|1952-08-26|Hulman|Pump|US11236736B2|2019-09-27|2022-02-01|Honeywell International Inc.|Axial piston pump with port plate having balance feed aperture relief feature|
    DE102020201803A1|2020-02-13|2021-08-19|Robert Bosch Gesellschaft mit beschränkter Haftung|Hydrostatic axial piston machine in swash plate design|
    DE102020203445A1|2020-03-18|2021-09-23|Robert Bosch Gesellschaft mit beschränkter Haftung|Axial piston machine with controlled cylinder pressure and control pressure transfer to the control surface|
    法律状态:
    2018-01-02| PLFP| Fee payment|Year of fee payment: 2 |
    2018-06-08| PLSC| Publication of the preliminary search report|Effective date: 20180608 |
    2019-12-30| PLFP| Fee payment|Year of fee payment: 4 |
    2020-12-28| PLFP| Fee payment|Year of fee payment: 5 |
    2021-12-30| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1662061|2016-12-07|
    FR1662061A|FR3059731B1|2016-12-07|2016-12-07|HYDRAULIC PUMP WITH AXIAL PISTONS|FR1662061A| FR3059731B1|2016-12-07|2016-12-07|HYDRAULIC PUMP WITH AXIAL PISTONS|
    US15/833,488| US10690124B2|2016-12-07|2017-12-06|Axial piston hydraulic pump|
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