• 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:
    Hydraulic machine (1) comprising first and second braking members (92, 93), a spring washer (65) tending to bias the first and second braking members (92, 93) in a braking direction, a brake release piston (61), configured to urge the spring washer (65) in a counter-direction to the braking direction, characterized in that the brake release piston (61) comprises a primary brake release piston (61a) associated with a primary brake release chamber ( 62a) and a secondary brake release piston (61b) associated with a secondary brake release chamber (62b), said primary (62a) and secondary (62b) chambers extending radially around the shaft (2), so that the projections of the primary brake release chamber (62a) and the secondary brake release chamber (62b) in a plane perpendicular to a longitudinal axis (XX) defined by the axis of rotation of the hydraulic machine (1) overlap at least partially .
    公开号:FR3056662A1
    申请号:FR1658965
    申请日:2016-09-23
    公开日:2018-03-30
    发明作者:Julien Engrand
    申请人:Poclain Hydraulics Industrie；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION The present invention relates to the field of hydraulic machines, and more specifically relates to a braking system for a hydraulic machine, for example for a hydraulic machine with radial pistons and multi-lobe cam.
    STATE OF THE PRIOR ART Hydraulic machines commonly comprise a braking system having a plurality of stacked discs, part of which is linked in rotation to the rotor, and part of which is linked in rotation to the stator. These brake discs are configured so as to immobilize the rotor with respect to the stator due to the friction resulting from contact between the discs.
    Hydraulic machines typically include a static brake, comprising a spring washer adapted to apply a clamping force on the brake discs causing immobilization of the rotor relative to the stator, and a brake release piston configured to apply a brake release force on the spring washer, thus tending to loosen the brake discs and thus allow relative rotation of the rotor relative to the stator.
    The constraints in terms of braking torque are however increasing, which implies that the braking washers used are more and more resistant, and therefore require the application of significant pressure to disengage the static brake, while retaining strict constraints in terms of space.
    This increase in stresses has led to requiring the use of high pressures, typically between 100 and 130 bar to achieve the brake release control of certain hydraulic machines. However, the use of such pressures is not accepted in certain applications, in particular due to the constraints and associated risks.
    PRESENTATION OF THE INVENTION The present disclosure relates to a hydraulic machine comprising a shaft and a casing mounted to rotate relative to one another by means of a bearing, the hydraulic machine comprising
    - first braking elements, integral in rotation with the casing,
    - second braking elements, integral in rotation with the shaft, the first and second braking elements forming a stack and being configured so as to secure the rotation of the casing relative to the shaft when brought into contact ,
    a spring washer mounted in abutment on the casing, and tending to urge the first and second braking elements in a braking direction tending to bring the first and second braking elements into contact,
    - a brake release piston, configured to urge the spring washer in a direction antagonistic to the braking direction, characterized in that the brake release piston comprises a primary brake release piston associated with a primary brake release chamber and a secondary brake release piston associated with a secondary brake release chamber, said primary and secondary chambers being connected and adapted to exert a thrust force on the primary piston and on the secondary piston respectively, said primary and secondary chambers being arranged successively in a longitudinal direction of the shaft and s 'extending radially around the shaft, so that the projections of the primary brake release chamber (62a) and of the secondary brake release chamber (62b) along a plane perpendicular to a longitudinal axis (XX) defined by the axis of rotation of the hydraulic machine (1) overlap at least partially.
    Alternatively, the hydraulic machine further comprises a chamber separator, configured to separate the primary and secondary pistons so that the pressure within each of the primary and secondary chambers is exerted only on one side of a single piston, that is to say that the secondary chamber exerts no pressure on the face of the primary piston opposite to the primary chamber.
    The chamber separator then typically comprises a bore to allow communication of the brake release pressure between the primary and secondary brake release chambers.
    According to one example, the primary brake release chamber is delimited by the casing and by the primary brake release piston, the secondary brake release chamber is defined by the chamber separator and by the primary brake release piston.
    According to one example, in projection along a plane perpendicular to a longitudinal axis defined by the axis of rotation of the hydraulic machine, the projections of the primary brake release chamber and of the secondary brake release chamber overlap at least partially, so that the projection of the secondary brake release chamber covers at least 30% of the projection of the primary brake release chamber.
    According to one example, the hydraulic machine further comprises a braking piston interposed between the stack and the brake release piston, and being associated with a braking chamber configured to apply a force to the braking piston tending to urge it in a braking direction tending to bring the first and second braking elements into contact.
    In one example, the brake release chamber is connected to a pressure supply source configured to deliver a pressure less than or equal to 30 bar.
    In one example, the primary brake release piston moves in translation in an intermediate chamber fluidly connected to an internal volume of the housing.
    The hydraulic machine is for example a hydraulic machine with radial pistons and multi-lobe cam, comprising a cylinder block defining a plurality of cylinders extending radially around the longitudinal axis of the shaft and in which are arranged pistons next to a multi-lobe cam.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention and its advantages will be better understood on reading the detailed description given below of various embodiments of the invention given by way of nonlimiting examples. This description refers to the pages of attached figures, on which:
    FIG. 1 represents a sectional view of a hydraulic machine according to one aspect of the invention, and
    - Figure 2 is a detailed view of a region of Figure 1 detailing the braking system.
    In all of the figures, the elements in common are identified by identical reference numbers.
    DETAILED DESCRIPTION OF EXAMPLES OF EMBODIMENTS FIGS. 1 and 2 show two sectional views of a hydraulic machine according to one aspect of the invention, FIG. 2 being a detailed view of the braking system shown in FIG. 1.
    These figures show a hydraulic machine 1 comprising a shaft 2 and a housing 3 mounted rotating relative to each other by means of a bearing 4. The shaft 2 defines an axis of rotation extending along a longitudinal direction XX. A proximal end 21 and a distal end 22 of the shaft 2 are defined, the proximal end being the closest to the cylinder block 6 defined below.
    This hydraulic machine 1 is here a hydraulic machine with radial pistons, comprising a distributor 5, a cylinder block 6 in which are arranged pistons 7 arranged opposite a multi-lobe cam 8. This multi-lobe cam 8 is here formed by a portion of the casing 3. The cylinder block 6 is mounted fixed relative to the shaft 2, so that these two elements 6 and 2 are linked in rotation, for example by means of grooves. The distributor 5 is positioned in the extension of the proximal end 21 of the shaft 2.
    The hydraulic machine 1 may be with a rotating shaft and a fixed cam, or vice versa. The structure of such a hydraulic machine is well known, and will not be described in more detail below.
    The bearing 4 comprises two rolling elements 41 and 42, here two tapered roller bearings spaced relative to each other in the longitudinal direction of the shaft 2. The rolling element 41 is thus qualified of proximal rolling element 41, while rolling element 42 is qualified as distal rolling element 42.
    The hydraulic machine also includes a braking system 9 comprising a plurality of brake discs 93 secured to the housing 3, and a plurality of brake discs 92 secured to the shaft 2, in particular by grooves or grooves. These brake discs 93 and 92 thus form a stack of brake discs. In the example illustrated, the braking discs 92 are connected to the shaft via an intermediate piece 94. Such an intermediate piece 94 is optional and the braking discs 92 can be connected directly to the shaft 2 .
    The braking system also includes two braking commands 60 and 70, configured so as to selectively apply a compressive force to the braking discs 92 and 93 in order to control locking of the relative rotational movement of the shaft 2 relative to housing 3.
    The brake control 60 defines a brake that is called static. It comprises a brake release piston 61 biased by a spring washer 65 so as to exert a clamping force on the brake discs 92 and 93, and thus keep them in the engaged position. The brake release piston 61 is associated with a brake release chamber 62 adapted to apply a pressure generating a force opposing the thrust force applied by the spring washer 65, and therefore tending to move the brake release piston 61 in one direction moving it away from the brake discs 92 and 93, and thus carrying out an action of disengaging the brake discs 92 and 93 and consequently releasing the relative rotation of the casing 3 and the shaft 2. The brake release chamber 62 is supplied via a pressurizing conduit 63.
    The spring washer 65 thus applies a clamping force on the brake release piston 61 which transmits this force to the brake discs 92 and 93, keeping them then in the engaged position, and locking the relative rotation of the shaft 2 and the casing 3. The application of pressure via the pressurizing conduit 63 makes it possible to achieve a pressure rise in the brake release chamber 62, which results in the application of a brake release force opposing the clamping force exerted by the spring washer 65 and thus making it possible to loosen the brake discs 92 and 93 and therefore to allow the relative rotation of the shaft 2 and of the casing 3.
    The brake control 60 thus typically defines a parking brake, applying by default in the absence of the application of brake release pressure.
    The brake release piston 61 is formed by two pistons; a primary brake release piston 61a and a secondary brake release piston 61b. These two brake release pistons 61a and 61b can be independent, and the brake release chamber 62 thus also comprises two chambers: a primary brake release chamber 62a and a secondary brake release chamber 62b respectively controlling the movement of the primary brake release piston 61a and the piston of secondary brake release 61b.
    A chamber separator 64 is interposed between the primary brake release piston 61a and the secondary brake release piston 61b. This chamber separator 64 also makes it possible to define the secondary brake release chamber 62b so that the pressure therein does not apply to the primary brake release piston 61a. Indeed, in the absence of such a chamber separator 64, the pressure within the secondary brake release chamber 62b would apply to the primary brake release piston 61a so as to oppose the force resulting from the pressure within the primary brake release chamber 62a. The chamber separator 64 is thus an element fixedly mounted on the casing 3. The chamber separator 64 is mechanically linked to the casing 3 in a fixed and sealed manner, for example by means of fixing screws. The chamber separator 64 also comprises at least one bore 66 to allow communication of the brake release pressure between the brake release chambers 62a and 62b, this at least one bore 66 being able to open out in relation to a bore made in the casing 3 and opening into the primary brake release chamber 62a. So that the hole in the housing 3 is aligned opposite the hole 66 in the chamber separator 64, an indexing system is provided between the chamber separator 64 and the housing 3.
    As seen in the figures, the primary brake release chamber 62a and the secondary brake release chamber 62b are arranged successively along the longitudinal axis XX defined by the shaft 2. The primary brake release pistons 61a and secondary 61b are also arranged successively along the longitudinal axis XX defined by the shaft 2.
    The primary brake release chamber 62a and the secondary brake release chamber 62b are arranged so as to extend at least partially over the same region delimited by an internal diameter and an external diameter around the longitudinal axis XX defined by l 'shaft 2. This overlap or superposition region is identified by the reference R in Figure 2. More precisely, if we consider the projections of the primary brake release chamber 62a and the secondary brake release chamber 62b according to a plane perpendicular to the longitudinal axis XX, these two brake release chambers 62a and 62b overlap at least partially.
    The radial size of these two brake release chambers 62a and 62b is therefore less than the sum of their two respective radial dimensions. The value of the overlap defines the gain achieved in terms of brake release effort and size. According to one embodiment, considering the projections of the primary brake release chamber 621a and of the secondary brake release chamber 62b along a plane perpendicular to the longitudinal axis XX, the projection of the secondary brake release chamber 62b covers at least 30% of the surface of the projection of the primary brake release chamber 62a, more precisely at least 50%, or even at least 60%, or even at least 75% of its surface.
    Note also that in the example shown, this overlap of the primary and secondary brake release chambers 62a and 62b also results in an overlap of the primary and secondary brake release pistons 61a and 61b.
    The chamber separator 64 and the primary brake release piston 61a and the secondary brake release piston 61b are each provided with sealing elements so as to ensure in particular the sealing of the various brake release chambers 62a and 62b.
    The area between the chamber separator 64 and the primary brake release piston 61a defines an intermediate chamber 67, this intermediate chamber 67 defining the maximum possible displacement for the primary brake release piston 61a.
    In operation, the application of brake release pressure via the pressurizing conduit 63 will cause a pressure rise in the primary brake release chambers 62a and secondary 62b, which will cause displacement of the brake release pistons primary 61a and secondary 62b in a direction tending to oppose the clamping force exerted by the spring washer 65. The primary brake release piston 61a will thus move until it comes into abutment against a stop section of the piston of secondary brake release 61b if the two pistons are not already in contact.
    The primary brake release piston 61a thus moves by translation in the longitudinal direction in the intermediate chamber 67 located between the primary brake release piston 61a on the one hand, and the secondary brake release piston 61b and the chamber separator 64 d 'somewhere else. This intermediate chamber 67 is typically fluidly connected to the internal volume of the casing 3 (typically by a bore or a groove arranged in the chamber separator 64, in a plane not visible in the figures), and is therefore at the casing pressure, c that is to say typically at substantially zero pressure. The casing is typically connected to a drain, thus making it possible to avoid a rise in pressure within the casing. The seal between the chamber separator 64 and the casing 3 is for example produced by a flat seal, of the metal-plastic type, which allows a passage of fluid at the level of the bore 66. An O-ring around the interface with the drilling 66 can also be used. This seal prevents the oil from the main brake release chamber 62a from communicating with the intermediate chamber 67 and the crankcase.
    The secondary brake release piston 61b is in turn already in abutment against the spring washer 65, the clamping force of which therefore opposes the result of the pressure within the secondary brake release chamber 62b. It is therefore understood that in the case where the primary brake release piston 61a is not in contact with the secondary brake release piston 61b, the primary brake release piston 61a moves faster than the secondary brake release piston 61b under the effect of the pressure introduced via the pressurizing conduit 63, insofar as only the internal pressure of the casing prevents it from moving while the spring washer 65 opposes the movement of the secondary brake release piston 61b. The secondary brake release piston 61b can be made in one piece, or be made up of several pieces linked together in particular by assembly means such as screws or by contact points.
    Once the brake release pistons 61a and 61b in contact, the forces resulting from the pressures within the primary and secondary brake release chambers 62a and 62b will add up, thereby increasing the brake release force generated. It is noted that the brake release pistons 61a and 61b may be in contact from the outset, or the primary brake release piston 61a may have only a very small stroke before coming into contact with the secondary brake release piston 61b. the operation then remains similar.
    It is understood which, on reading the above and in view of the figures, that the two brake release pistons 61a and 61b thus proposed make it possible to obtain a brake release force greater than a single brake release piston having an identical radial size. The pressure required to oppose the clamping force applied by the spring washer 65 and thus loosen the brake discs is therefore reduced, and is typically between 12 and 30 bar. This solution makes it possible to brake with a lower pressure at constant overall dimensions or to reduce the overall dimensions while maintaining the same brake release pressure. Alternatively, the brake release pistons 61a and 61b can be secured after being positioned in the hydraulic machine 1, typically by assembly elements such as bolts. The operation is then similar to that described above, the primary brake release 61a and secondary 61b pistons then being held in contact with one another and secured in translation.
    The hydraulic machine as shown also includes a brake control 70, which is called dynamic braking.
    This braking command comprises a braking piston 71 adapted to selectively apply a clamping force on the braking discs 92 and 93. This braking piston 71 is controlled by a braking chamber 72 supplied by a setting conduit pressure 73. As can be understood from the figures, a rise in pressure within the braking chamber 72 causes the braking piston 71 to move in a braking direction, tending to exert a clamping action on the braking discs 92 and 93. In the example shown, the brake piston 71 is interposed between the brake release piston 61 (more precisely the secondary brake release piston 61b) and the stack of brake discs, and the brake chamber 72 as well as the pressurizing conduit 73 are formed in the brake release piston 61, more precisely in the secondary brake release piston 61b. This brake piston 71 can be produced in the form of an annular piston as shown in the figures or else in the form of a plurality of essentially cylindrical brake pistons. Seals are present around the brake piston 71, in order to avoid any communication between the brake chamber 72 and the secondary brake release chamber 62b, as well as between the brake chamber 72 and the casing and / or the intermediate chamber 67.
    Alternatively, the hydraulic machine may have only a static brake without dynamic brake.
    In the embodiment shown in the figures, the braking elements 92 and 93 are arranged between the distributor 5 and the distal end 22 of the shaft 2 It is clear that such an embodiment is not not limiting, and that the braking system comprising the braking elements 92 and 93 can be positioned elsewhere, for example in the extension of the distributor 5 and the proximal end 21 of the shaft 2, and collaborate with a brake shaft linked to the bloccylindres, in particular by grooves.
    The hydraulic machine 1 as shown in Figures 1 and 2 typically forms a wheel spindle for a vehicle. It is clear that the hydraulic machine as presented is not limited to such an application.
    Although the present invention has been described with reference to specific embodiments, it is obvious that modifications and changes can be made to these examples without departing from the general scope of the invention as defined by the revendications. In particular, individual features of the various illustrated / mentioned embodiments can be combined in additional embodiments. Therefore, the description and the drawings should be considered in an illustrative rather than restrictive sense.
    It is also obvious that all the characteristics described with reference to a process can be transposed, alone or in combination, to a device, and conversely, all the characteristics described with reference to a device can be transposed, alone or in combination, to a method.
    权利要求:
    Claims (9)
    [1" id="c-fr-0001]
    1. Hydraulic machine (1) comprising a shaft (2) and a casing (3) mounted rotating relative to each other by means of a bearing (4), the hydraulic machine (1) comprising
    - first braking elements (93), integral in rotation with the casing (3),
    - second braking elements (92), integral in rotation with the shaft (2), the first and second braking elements (92, 93) forming a stack and being configured so as to secure the rotation of the casing ( 3) relative to the shaft (2) when brought into contact,
    - a spring washer (65) mounted in abutment on the casing (3), and tending to urge the first and second braking elements (92, 93) in a braking direction tending to bring the first and second elements into contact braking (92, 93),
    - a brake release piston (61), configured to urge the spring washer (65) in a direction antagonistic to the braking direction, characterized in that the release brake piston (61) comprises a primary release brake piston (61a) associated with a primary brake release chamber (62a) and a secondary brake release piston (61b) associated with a secondary brake release chamber (62b), said primary (62a) and secondary (62b) chambers being connected and adapted to exert a thrust force on the primary piston (61a) and on the secondary piston (61b) respectively, said primary (62a) and secondary (62b) chambers being successively arranged in a longitudinal direction of the shaft (2) and extending radially around the shaft (2), so that the projections of the primary brake release chamber (62a) and of the secondary brake release chamber (62b) along a plane perpendicular to a longitudinal axis (XX) defined by the axis of rotation of the machine hy hydraulics (1) overlap at least partially.
    [2" id="c-fr-0002]
    2. Hydraulic machine (1) according to claim 1, further comprising a chamber separator (64), configured to separate the primary (61a) and secondary (61b) brake release pistons so that the pressure within each of the chambers primary (62a) and secondary (62b) is exerted only on a single face of a single brake release piston (61a, 61b).
    [3" id="c-fr-0003]
    3. Hydraulic machine (1) according to claim 2, in which the chamber separator (64) comprises at least one bore (66) to allow the release of the brake release pressure between the primary (62a) and secondary ( 62b).
    [4" id="c-fr-0004]
    4. Hydraulic machine (1) according to one of claims 2 or 3, in which the primary brake release chamber (62a) is delimited by the casing and by the primary brake release piston (61a), the secondary brake release chamber (62b ) is delimited by the chamber separator (64) and by the primary brake release piston (61b).
    [5" id="c-fr-0005]
    5. Hydraulic machine (1) according to one of claims 1 to 4, in which in projection along a plane perpendicular to a longitudinal axis (XX) defined by the axis of rotation of the hydraulic machine (1), the projections of the primary brake release chamber (62a) and the secondary brake release chamber (62b) overlap at least partially, so that the projection of the secondary brake release chamber (62b) covers at least 30% of the projection of the brake release chamber primary brake release (62a).
    [6" id="c-fr-0006]
    6. Hydraulic machine (1) according to one of claims 1 to 5, further comprising a brake piston (71) interposed between the stack and the brake release piston (61), and being associated with a brake chamber ( 72) configured to apply a force to the braking piston (71) tending to urge it in a braking direction tending to bring the first and second braking elements (92, 93) into contact.
    [7" id="c-fr-0007]
    7. Hydraulic machine (1) according to one of claims 1 to 6, in which the brake release chamber (62) is connected to a pressure supply source (63) configured to deliver a pressure less than or equal to 30 bars .
    [8" id="c-fr-0008]
    8. Hydraulic machine (1) according to one of claims 1 to 7, in which the primary brake release piston (61a) moves in translation in an intermediate chamber (67) fluidly connected to an internal volume of the casing (3) .
    [9" id="c-fr-0009]
    9. Hydraulic machine (1) according to one of claims 1 to 8, 10 comprising a cylinder block (6) defining a plurality of cylinders extending radially around the longitudinal axis of the shaft (2) and in which are arranged pistons (7) arranged opposite a multilobe cam (8).
    1/2
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    同族专利:
    公开号 | 公开日
    US10364792B2|2019-07-30|
    FR3056662B1|2018-11-23|
    CN107869534A|2018-04-03|
    EP3299656A1|2018-03-28|
    CN107869534B|2021-06-29|
    US20180087486A1|2018-03-29|
    EP3299656B1|2020-11-18|
    引用文献:
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    EP2638248B1|2010-11-10|2015-09-30|R.&D. S.r.l.|Radial cylinder hydraulic machine with improved oscillating radial cylinder|
    JP5622561B2|2010-12-27|2014-11-12|カヤバ工業株式会社|Caliper brake device|
    CN203161909U|2012-11-29|2013-08-28|芜湖伯特利汽车安全系统有限公司|Brake caliper assembly of electronic parking brake system for vehicle|
    FR3010007B1|2013-09-03|2016-12-30|Poclain Hydraulics Ind|VEHICLE COMPRISING A HYDROSTATIC TRANSMISSION COMPRISING A CLUTCH PROVIDING A DIFFERENTIAL FUNCTION|
    FR3014940B1|2013-12-17|2016-01-15|Poclain Hydraulics Ind|HYDRAULIC SYSTEM WITH DRAIN CARTER|
    EP2949959B1|2014-05-30|2018-07-04|Eaton Corporation|Disc brake assembly and method of making same|
    US20160178022A1|2014-12-18|2016-06-23|Caterpillar Inc.|Clover Leaf Hub|FR3079777B1|2018-04-06|2020-09-18|Poclain Hydraulics Ind|MOTORIZATION KIT FOR MOTORIZATION ASSISTANCE OF A WHEEL AND VEHICLE THUS EQUIPPED|
    FR3080899B1|2018-05-02|2020-05-22|Poclain Hydraulics Industrie|IMPROVED BRAKING DEVICE|
    GB2575076B|2018-06-28|2021-10-20|Bamford Excavators Ltd|An actuation mechanism for a multi-plate brake|
    US10995936B1|2018-07-13|2021-05-04|Volt, LLC|Fully adjustable landscape lighting system|
    JP2020094615A|2018-12-11|2020-06-18|株式会社ジェイテクト|Clutch device|
    FR3094419A1|2019-03-28|2020-10-02|Poclain Hydraulics Industrie|Hydraulic machine including an improved brake.|
    法律状态:
    2017-09-22| PLFP| Fee payment|Year of fee payment: 2 |
    2018-03-30| PLSC| Search report ready|Effective date: 20180330 |
    2018-09-24| PLFP| Fee payment|Year of fee payment: 3 |
    2019-09-23| PLFP| Fee payment|Year of fee payment: 4 |
    2020-09-21| PLFP| Fee payment|Year of fee payment: 5 |
    2021-09-22| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1658965A|FR3056662B1|2016-09-23|2016-09-23|IMPROVED BRAKING SYSTEM FOR HYDRAULIC MACHINE|FR1658965A| FR3056662B1|2016-09-23|2016-09-23|IMPROVED BRAKING SYSTEM FOR HYDRAULIC MACHINE|
    US15/712,219| US10364792B2|2016-09-23|2017-09-22|Braking system for a hydraulic machine|
    EP17192610.8A| EP3299656B1|2016-09-23|2017-09-22|Improved braking system for hydraulic machine|
    CN201710873714.7A| CN107869534B|2016-09-23|2017-09-25|Improved braking system for hydraulic machine|
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