Hydraulic machine comprising claw brake

Abstract

A hydraulic machine (2) includes a bearing support member (8), a cylinder block (16), a brake piston (20) movably mounted relative to the bearing support member between a braking position in which the piston is positively engageable with the cylinder block such that rotation of the cylinder block relative to the piston is prevented, and a brake release position in which the brake piston is released from the cylinder block relative to the piston. The piston (20) has a brake release position in which the piston freely rotates relative to the cylinder, and at least one bearing (14) supported by a bearing support member (8), the piston and the bearing being located on the same side of the cylinder with respect to the direction of a main axis (X-X) of the machine, a periphery (59) of the piston (20) oriented in a direction opposite the axis, the periphery is configured such that rotation of the piston relative to the bearing support member is prevented.

Description

Technical Field

[0001] The present invention relates to a hydraulic press. Background Art

[0002] From document FR-2 765 637 a rotary hydraulic machine is known which comprises a shaft, a cam and a cylinder block fixed to the rotary shaft and carrying a piston capable of following the cam. The shaft is carried by a bearing supported by a bearing support. The machine comprises a brake of the pawl brake type comprising a piston mounted so as to be movable with the bearing support between a braking position in which the piston blocks the rotation of the cylinder block and a brake release position in which the piston allows the cylinder block to rotate freely. The bearing and the brake piston are located on different sides of the cylinder block with respect to the direction of the axis of rotation of the machine.

[0003] However, in particular for reasons of compactness, it is desirable to provide a machine in which, on the contrary, the brake piston and the bearing are located on the same side of the cylinder block. However, this configuration raises the problem that the housing of the brake piston is bulky.

[0004] An object of the present invention is to obtain a hydraulic machine that meets this desire. Summary of the invention

[0005] To this end, the present invention provides a hydraulic press comprising:

[0006] Bearing support member,

[0007] Cylinder block,

[0008] a brake piston movably mounted relative to the bearing support member between a braking position in which the piston is form-matchedly engaged with the cylinder block such that rotation of the cylinder block relative to the piston is prevented, and a brake release position in which the piston allows free rotation of the cylinder block relative to the piston, and

[0009] at least one bearing supported by a bearing support member, the piston and the bearing being located on the same side of the cylinder block relative to the direction of the main axis of the machine,

[0010] A periphery of the piston, the periphery being oriented radially in a direction opposite to the axis, is shaped to prevent rotation of the piston relative to the bearing support member.

[0011] In the present application, the expression "in a direction opposite to the axis" means radially outward, and "in a direction of the axis" means radially inward.

[0012] This arrangement thus allows the brake piston to be properly accommodated without loss of volume, even if the piston and bearing are located on the same side of the cylinder block.

[0013] It may be provided that the bearing support member comprises a first part and a second part assembled to the first part, the first part and the second part together forming a housing for receiving the piston.

[0014] This is an advantageous solution to obtain the device of the invention. In particular, by means of such a two-part device, the bearing support member is easy to manufacture, although its shape may be complex since it must cooperate with the piston.

[0015] It may be provided that the second portion forms an abutment to prevent the piston from moving outside the housing.

[0016] It may be provided that the bearing support member forms a groove opening in the direction of the cylinder block; the groove receives the piston.

[0017] The machine has rotational symmetry and the groove is annular. For example, the groove can be arranged to continue around the bearing.

[0018] The machine may include a cam and a fixed member passing through the cam, the periphery of the piston including extensions extending in a radial direction of the axis, such that these extensions coincide with areas located between the fixed members, or coincide with continuations of these areas in a direction parallel to the axis.

[0019] Thus, the extensions securing the piston against rotation are accommodated without taking up too much volume, ie in the free spaces left by the fixing members or in the continuation of these spaces in the axial direction.

[0020] The piston may be provided with a cavity which opens in the axial direction and extends perpendicularly to the extension portion in the radial direction of the axis.

[0021] The mass of the piston is thus reduced. In addition, the extension on the bearing ensures its reinforcement, and the extension on the piston also participates in the reinforcement of the piston, in particular if they form ribs.

[0022] It may be provided that the bearing support member has an extension extending into the cavity of the piston.

[0023] These extensions thus ensure a reinforcement of the bearing support member in order to better absorb the forces transmitted by the bearing shaft or shafts.

[0024] It may be provided that the periphery of the piston and / or the bearing support member has surfaces which are shaped to prevent rotation of the piston relative to the bearing support member and which are obtained by a forming operation without machining.

[0025] Therefore, if these surfaces remain untreated, the manufacture of the machine is simplified.

[0026] It may be provided that the machine comprises a shaft which carries an abutment forming an obstacle to sliding movement of the cylinder block in the axial direction.

[0027] Without such an obstacle, the demands of the brake piston on the cylinder block could cause an axial displacement of the cylinder block relative to the shaft. This abutment allows this risk to be avoided with a reduced number of parts, since the shaft carries the abutment. This avoids the use of a large number of parts that would generate a stacking of tolerances due to the dimensional chain involved.

[0028] The invention also provides a method for manufacturing the machine of the invention, wherein

[0029] The piston is not formed by machining, some of the peripheral surfaces are formed to prevent rotation of the piston relative to the bearing support member, and these surfaces are in the formed state, and

[0030] The piston is assembled to the bearing support member with the faces in the formed state.

[0031] Thus, the need for one or more machining operations is avoided, in particular cutting operations (e.g. milling) on ​​the peripheral faces, which are shaped to prevent the piston from rotating relative to the bearing support member. The manufacture of the machine is thus simplified. However, it is still possible to obtain some parts of the piston by machining. Thus, a piston deburring step and a piston lathing step can be performed. The shaping step can be performed by forging or molding the piston.

[0032] The invention also provides a method for manufacturing the machine of the invention, wherein:

[0033] The bearing support member is not formed by machining, some faces of the bearing support member are formed to prevent rotation of the piston relative to the bearing support member; the faces of the bearing support member formed to prevent rotation are in a formed state, and

[0034] The piston is assembled to a bearing support member, and the bearing support member is formed so that the surface that prevents rotation is in a formed state.

[0035] The present invention also provides a manufacturing method, wherein

[0036] The bearing support member is not formed by machining, and the extension is in a formed state; and

[0037] The piston is assembled to the bearing support member with the extension in the formed state.

[0038] Provision may be made for machining the piston and / or the bearing support member.

[0039] The method may be arranged to include:

[0040] Assembling the brake piston with the bearing support member, and

[0041] Mount the component on the housing or rotating part of the machine.

[0042] It can be arranged that the method includes at least one of the following features:

[0043] The first portion is assembled to the second portion by placing a piston between the first portion and the second portion;

[0044] At least one spring is arranged in the first part, and the brake piston is assembled to the second part, with a seal interposed between the brake piston and the second part; and

[0045] A sealing element is interposed between oppositely facing surfaces of the first portion and the second portion.

[0046] Such sealing may be achieved by using seals, sealants or any other sealing means at the interface between the parts. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] Below is given a description of one embodiment of the invention, as a non-limiting example supported by the accompanying drawings, in which:

[0048] Figure 1 is a half view of a representative axial section of a machine according to one embodiment of the present invention;

[0049] Figure 2 and Figure 3 is an axial cross-sectional view of the machine in this embodiment;

[0050] Figures 4 to 7 yes Figure 2 A perspective axial section view of some parts of the machine;

[0051] Figures 8 to 11 They are Figure 2 a perspective view of a first portion of a bearing support member, a brake piston, and a second portion of a bearing support member of a machine in FIG.

[0052] Fig.12 yes Figure 2 A cross-sectional view of the machine showing some of its parts. DETAILED DESCRIPTION

[0053] machine

[0054] Combination Figures 1 to 12 , a description will now be given of a rotary hydraulic machine 2 according to an embodiment of the present invention.

[0055] Special References Figures 1 to 3, the machine comprises a shaft 4 having a longitudinal axis XX forming the axis of rotation of the machine. The machine comprises a housing 6 comprising a bearing support member 8 and a distribution cover 10 arranged on either side of a multileaf cam 12 to which they are rigidly fixed. The machine comprises two rolling bearings 14. The bearings carry the shaft 4 and, in radial direction of the axis XX, bear against the bearing support member in a shoulder formed in the bearing support member 8. The shaft forms an output shaft and comprises at its outer end a drive element, i.e., for example, a flange for a wheel, or a pinion for a chain or a track.

[0056] The machine is included Figure 2 and Figure 3 The cylinder block 16 shown in particular in the figure is rotatably connected to the shaft 4 and has a structure known per se, which will not be described in detail. The cylinder block has a cylindrical housing radial to the axis, in which the cam piston is accommodated, is mounted slidingly in the radial direction, and is supported on the cam 12 by means of bearing rollers.

[0057] A chamber defined by the housing contains a liquid at housing pressure. Figure 2 The drain opening 13 visible in the drawing allows drainage whenever necessary.

[0058] The machine comprises a distributor 18 extending in the axial continuation of the shaft 4 and the distributor cap 10. The distributor 18 ensures the connection of the piston housing with the high-pressure and low-pressure fluid circuits in a manner known per se. The machine can operate as a motor or as a pump. When operating in motor mode, the high pressure of the fluid in the high-pressure circuit causes the movement of the piston, the rolling of the rollers on the multi-leaf cam 12 and the fine rotation of the shaft 4 relative to the housing 6, thereby causing the rotational drive of the load fixed to the shaft or the housing. On the contrary, in pump mode, this input rotation causes the movement of the piston in its housing and puts the fluid in the high-pressure circuit under pressure and moves. For more details about the overall structure of the machine and how it operates, reference can be made, for example, to the aforementioned document FR-2765 637.

[0059] The machine comprises a brake piston 20, Fig. 9 and Fig.10 As with most parts of the machine, the shape of the actuating piston as a whole has rotational symmetry about the axis XX. The brake piston 20 and the bearing 14 are located on the same side of the cylinder block 16 relative to the direction of the main axis XX, as in Figures 1 to 3 This can be particularly seen in.

[0060] The brake piston 20 has a substantially annular shape. On an axial end face 22 leading toward the cylinder block 16, the actuating piston has a transmission with teeth 24, which protrude outwardly from this face in the axial direction. The cylinder block 16 has a matching transmission with teeth 26 on the axial end face leading toward the piston.

[0061] The brake piston is received in a housing 28 of the bearing support member 8. The actuating piston is mounted to slide relative to the bearing support member 8 in an axial direction between a braking position and a brake release position:

[0062] In this actuated position, the piston 20 is in form-fitting engagement with the cylinder body 16 so as to prevent rotation of the cylinder body relative to the piston, and

[0063] In this actuated release position, the piston 20 allows the cylinder block to rotate freely relative to the piston.

[0064] In the braking position closest to the cylinder block, the teeth 24 of the piston engage with the teeth of the cylinder block 16, and the shaft 4 cannot rotate relative to the housing. In the brake release position farthest from the cylinder block, the teeth of the piston are disengaged from the teeth of the cylinder block, and the shaft can rotate relative to the housing. Therefore, this is a dog brake.

[0065] The bearing support member 8 here comprises a first part 30 and a second part 32 assembled to the first part, the first and second parts together forming the housing 28. The two parts have a generally annular shape that is rotationally symmetrical about an axis.

[0066] Part 1 30 Figure 8 As shown in Figure 2 The first part, seen in section along a mid-radial plane, has a substantially U-shaped profile on one side of the axis. The first part thus has a recess 34 opening in the direction of the cylinder block 16, which receives the brake piston 20. Thus, in the first part, the recess separates a peripheral part 38, which is farthest from the axis, from a central part 40, which is closest to the axis. Unlike the central part 40, which does not bear on the cam, the peripheral part 38 bears against the cam 12 in the axial direction.

[0067] The central portion 40 is in contact with the bearing 14 , which bears on an inner surface 42 oriented towards the axis, against two shoulders of the central portion. A seal 44 bears on the shaft and on the inner surface 42 .

[0068] The skirt 41 of the second part 32 extends in the axial direction into the first part 30 and bears radially on the peripheral part 38. The peripheral part ensures mutual centering of the two parts 30 and 32 of the bearing support member.

[0069] As in Figure 1 , Figure 6and Figure 7 , the first and second parts 30, 32 are rigidly and directly fixed to each other via fixing members 46, which extend in a direction parallel to the axis and away from the axis. Here, each of the two parts comprises a raised portion or extension 48 on its periphery. Each fixing member 46 passes through an extension 48 of the first part 30 and an extension 48 of the second part 32. These members 46 are formed here by screws, the heads of which bear against the second part 32.

[0070] As in Figure 3 and Figure 7 As particularly shown in the figure, the dispensing cap 10, the cam 12 and the second part 32 are rigidly fixed to each other via fixing members 50, which extend in a direction parallel to the axis and away from the axis. Each fixing member 50 passes through the dispensing cap 10, the cam 12 and the second part 32. These members 50 are formed here by screws, the heads of which bear against the dispenser.

[0071] The machine 2 comprises a return spring 52 which tends to exert a demand on the brake piston 20 in the direction of the cylinder block 16 and thus in the braking position. Figure 1 and Figure 8 , the first part 30 has a cavity 54 arranged at the bottom of the groove 34. Each spring 52 bears against the bottom of the associated cavity 54 and also against a plane surface 53 of the axial end of the brake piston 20, which is perpendicular to the axis and oriented towards the groove.

[0072] The machine includes a hydraulic control chamber for the brake. The hydraulic control chamber is a brake release chamber 56 located in the housing 28 of the bearing support member 8. The brake release chamber is bounded by an inner periphery 57 of the second portion 32 oriented in the axial direction and an outer periphery 59 of the piston 20 oriented in the opposite direction to the axis opposite to the inner periphery. Two seals 61 in contact with these peripheries define the chamber 56. A control line 58 passes through the second portion 32 in the axial direction to supply control fluid to the chamber 56. Since the chamber is formed by a plane surface 60 of the piston (which is on the Fig. 9 ) and the planar surface 62 of the second portion (in Fig.11 5 (determined in detail in FIG. 5 ), all planar surfaces are perpendicular to the axis, so that appropriate pressure of the fluid in the brake release chamber 56 causes the piston to resist the spring 52 to rebound, so that the piston moves to the brake release position. Here, by means of these oppositely facing surfaces 60, 62, the second portion 32 forms an abutment that prevents the piston from moving outside the housing 28. The bearing support member is thus configured alone to prevent any movement of the piston from the housing 28.

[0073] The piston 20 changes from the brake release position to the braking position via a sliding movement in the second portion 32 .

[0074] The guidance of the axial sliding of the piston can be achieved by the sliding of the seal 61 on the machined surface. In the embodiment shown, the seal is carried by the brake piston (in a groove formed on the outer radial portion of the piston 20), but it is conceivable that the seal 61 is located in a groove formed in the inner periphery 58 oriented in the axial direction of the second part 32 (it is also conceivable that one of the seals 61 is located on the piston 20 and the other seal 61 is located on the second part 32). Generally, the surface on which the seal-carrying groove is formed can be machined or not; on the other hand, the surface on which the seal slides (the opposite surface) must be machined. In the embodiment described, the surface 71 of the piston in which the groove is formed is machined, and the surface 73 of the second part on which the seal 61 slides is also machined.

[0075] Anti-rotational protection of the sliding movement is achieved by the forged or knocked-out surface of the extension 64 of the brake piston 20 cooperating with the forged or knocked-out surface of the extension 68 of the second portion 32 , as will be seen below.

[0076] The guiding of the brake piston 20 in sliding relative to the bearing support member 8 is accompanied by an anti-rotation function, thereby preventing relative rotation thereof. This function is ensured by the shape of the piston 20 and the second part 32. More specifically, in addition to defining the brake release chamber 56 as explained above, the outer periphery 59 of the piston oriented in the direction opposite to the axis and the inner periphery 57 of the second part 32 oriented toward the axis are shaped to prevent the piston from rotating relative to the bearing support member.

[0077] As in Fig. 9 As particularly shown in FIG. 5 , for this purpose, the outer periphery 59 of the piston here comprises an extension 64 which forms spaced serrations which protrude from the cylindrical surface 66 of the periphery in the radial direction of the axis. Similarly, and matching therewith, as in Fig.11 As particularly shown in FIG. 5 , for this purpose, the inner periphery 57 of the second portion 32 comprises an extension forming spaced serrations which protrude from the cylindrical surface 70 of the periphery in a radial direction of the axis. The extension 64 of the piston is arranged between the extensions 68 of the second portion. The extensions 64, 68 thus prevent the rotation of the piston via their respective flanks 67, 69 lying in a plane radial to the axis. As will be seen below, these flanks 67, 69 are in the forged state and are not produced by a machining operation. As in FIG. Figure 5 and Fig.12As shown in , in this example, the extension 64 of the piston extends in the continuation along the axis of a region 65 which forms an arch and is positioned between the fixing members 50 which fix the distributor and the cam to the bearing support member 8 .

[0078] Each extension 64 of the piston 20 is inserted between the two extensions 68 of the second part, which means that one of the extensions 68 contacts the extension 64 of the piston when braking in the rotational direction, and correspondingly the other extension 68 contacts the extension 64 when braking in the other rotational direction. This is equivalent to a machine that can be driven and braked in two rotational directions of travel forward and backward. The extension 64 of the piston contacts the extension 68 of the second part in one braking direction via one of its side surfaces 67, and contacts the extension of the second part in another braking direction via the other side surface 67. The extensions 64 and 68 participate in the sliding connection of the piston in the bearing support member. In particular, the unmachined sides 67, 69 of the extensions 64 and 68 slide relative to each other during braking or brake release operations. When the piston 20 moves, the machined surfaces 64 and 70 and 71, 73 extending in the circumferential direction slide on each other.

[0079] In addition, as in Fig.10 As shown in FIG. 1 , the piston 20 has a cavity 72 that is open in the axial direction and extends perpendicularly to the extension portion 64 in the radial direction of the axis. Figure 8 , the bearing support member has extensions 74 extending into the cavity 72 of the piston. These extensions are here located on the outer periphery of the central portion 40 of the first portion 30 of the bearing support member. These extensions form reinforcements to absorb the forces transmitted by the bearing 14.

[0080] As in Figure 6 As shown in FIG. 1 , the shaft 4 includes a spline 75 (shown only in some of the figures, especially in FIG. Figure 4 and Figure 6) to drive the cylinder body in rotation, and the shaft 4 also carries an abutment 76, which forms an obstacle to prevent the cylinder body 16 from sliding in the axial direction relative to the shaft. In this example, the abutment is formed by a disk or washer 78, which is rigidly fixed to the end of the shaft and is coaxial with the shaft, for example by means of a screw 78. The washer extends via its outer edge protruding from the cylindrical surface of the shaft and is opposite in the axial direction to the surface of the cylinder body 16 oriented in the direction opposite to that of the brake piston, thereby preventing it from sliding when the cylinder body is subjected to pressure from the piston. The prevention of sliding of the cylinder body relative to the shaft can also be obtained by means of a stop portion pressed at the axial end of the shaft (for example by an interference fit) or by a (circlip-type) stop ring received in a groove of the shaft. The advantage of all the solutions proposed herein is that they allow a controlled axial clearance of the cylinder body relative to the shaft. Without these stop solutions, the axial blocking of the cylinder block could be obtained by abutting against the housing 6 or the distributor 18, but this would result in a greatly reduced flexibility of the dimensional chain of the axial clearances of the different parts of the motor relative to each other and, in the worst case, would risk deteriorating the distributor or the housing or even the cylinder block. Alternatively, such a solution would require the insertion of a rotary sliding member, such as a sliding washer or a ball or roller thrust bearing, between the housing and the cylinder block.

[0081] Manufacturing method

[0082] The machine 2 can be manufactured according to an embodiment of the method of the present invention, which comprises the following steps.

[0083] In a preferred embodiment, Fig. 9 and Fig.10 The brake piston 20 shown in FIG. 1 is obtained by a die forging step. A forged part is more suitable for obtaining the brake piston 20 , in particular in view of the mechanical strength that is desired to be obtained at the claw teeth.

[0084] In this step, the piston is forged so that the cylindrical face 66 and the side face 67 of the extension 64 are formed on the outer periphery 59 to prevent the piston from rotating relative to the bearing support member 8. The piston is then removed from the die, leaving its side face in the forged state. Alternatively, the piston forged in the preferred embodiment and other components presented as molded in the preferred embodiment can be obtained by other uniaxial conformity means, such as injection molding or sintering along the axis XX, or obtained in an equivalent manner via other means, such as additive manufacturing or 3D printing. In the remainder of the description, the term "forming" is used to indicate all such obtaining means except machining.

[0085] The next step is a step of re-machining (in particular by lathe machining) of some surfaces of the piston. Here, this involves the axial end face 53 oriented towards the bottom of the groove 34 and the cylindrical face 71 oriented in the direction opposite to the axis, except for the face 66 bearing the extension 64. These are Fig. 9 and Fig.10 Thus, all non-machined surfaces of the piston, and in particular the side surfaces 67, remain in the formed state (thereby avoiding a more expensive milling operation to obtain the serrations).

[0086] Similarly, refer to Figure 8 The first part 30 of the bearing support member is obtained by injection molding. In this step, the part is molded with reinforcing extensions 74 on the periphery. The part is then released from the mold so that these extensions are in a demoulding state.

[0087] A remachining step (in particular by lathing) is then performed on some faces of the portion 30. Here, this remachining step is carried out on the peripheral portion and the oppositely facing surfaces of the axial end face in contact with the second portion 32. In the central portion, the remachining step also involves the plane and cylindrical surfaces which form the shoulders for receiving the bearing 14. The machined surfaces are Figure 8 All other faces remain demoulded (thereby avoiding a more expensive milling operation to form the serrations).

[0088] Similarly, the second portion 32 of the bearing support member is formed by injection molding, as in Fig.11 In this step, the part is molded by shaping the cylindrical surface 70 on the inner periphery and the surface 69 of the extension 68 to prevent the piston from rotating relative to the bearing support member. The part is then released from the mold so that these surfaces 69 are in a demolded state.

[0089] A remachining step (in particular by lathing) is then performed on some faces of this portion 32. Here, these are the face of the skirt 41, the face perpendicular to the axis that bears against the first portion 30, and the cylindrical face 73 on which the piston bears when sliding. Fig.11 However, all other faces remain demoulded, in particular the side faces 69 (thus avoiding a milling operation to form the serrations).

[0090] For the piston 20, as for the first part 30 or the second part 32 of the bearing support member, the faces of the extension have a draft angle in the axial direction, that is, they are slightly inclined to allow ejection from the die (or from the forging die) along the axis XX. For example, these non-remachined faces are not cylindrical along the axis XX, and are actually slightly conical. In this embodiment, all demolding (or forging) faces have this draft angle feature. The demolded (or forged) faces also have a greater roughness than the remachined surfaces.

[0091] The draft angle on the non-remachined face of the piston 20 is typically 4°, as on the face of the second portion 32. This draft angle allows limiting the force required to move the piston relative to the bearing support member in the brake release direction. The smaller the draft angle, the greater the friction to be overcome to disengage the brake piston from the second portion 32 of the bearing support member.

[0092] Thereafter, the piston 20, the first part 30 and the second part 32 and other parts of the machine are assembled, and the above-mentioned faces kept in the demoulding (or forging) state are kept in this state during assembly. When installing, the first part 30 is assembled to the second part 32, and the piston 20 is inserted therebetween so that the piston is captured in the housing.

[0093] The assembly of the first part 30 onto the second part 32 is obtained by the following steps:

[0094] Insert the spring 52 into the cavity 54 of the groove 34 of the first portion 30;

[0095] The brake piston 20 equipped with its two seals 61 is inserted into the second portion 32, which forms an abutment to retain the brake piston 20 in the direction of movement, and then

[0096] The first part 30 equipped with its spring is assembled with the second part 32 comprising the brake piston 20 equipped with its seal 61 via screws 46. Preferably, the assembly is a sealed assembly (using seals, sealants or any other sealing means at the interface between parts 30 and 32).

[0097] Once assembled, the parts 30 and 32 form a subassembly of the motor (parts of which are integral) which can be mounted independently. This subassembly is then assembled to other parts of the machine.

[0098] Thus, the anti-rotation function of the piston is obtained on the non-remachined bearing surface. The molded (or forged) part does not require complex machining steps. It is sufficient to use a lathe machining step. This allows to reduce the manufacturing costs.

[0099] The present invention therefore provides a kind of pawl type negative parking brake that is positioned on the same side of cylinder block as bearing.Here, the sliding connection of brake piston and the prevention of rotation are obtained between two seals 61 in control chamber 28.

[0100] As already seen, the brake piston has a specific shape on its inner and outer diameters. The internal shape formed by the cavities 72 does not serve to prevent its rotation, but serves to prevent any interference with the extensions 74 that rigidify the first portion 30 of the bearing support member. Since the anti-rotation function of the brake piston 20 is obtained on its outer periphery, a usable volume is reserved in the bearing support member to position these reinforcing extensions 74 therein, thereby increasing the thickness to solidify the component.

[0101] Since anti-rotation is achieved on the outer diameter of the brake piston 20, applying the equivalent braking torque transmitted to the cylinder body requires less force on the sides of the extensions 64, 68 (because of the greater leverage) compared to an arrangement having brake piston anti-rotation on the inner diameter of the brake piston.

[0102] Many modifications may be made to the present invention without departing from the scope of the invention.

[0103] The shape of the housing 28 receiving the piston may vary.The bearing support member may be manufactured in a single part or in more than two parts.

Claims

1. A hydraulic press (2), comprising: A bearing support member (8), Cylinder block (16), a brake piston (20) movably mounted relative to the bearing support member between a braking position in which the piston is form-matchedly engaged with the cylinder block so as to prevent the cylinder block from rotating relative to the piston and a brake release position in which the piston allows the cylinder block to freely rotate relative to the piston, and at least one bearing (14) supported by the bearing support member (8), the piston and the bearing being located on the same side of the cylinder block with respect to the direction of the main axis (XX) of the machine, A periphery (59) of the piston (20) is radially oriented in a direction opposite to the axis, the periphery being configured to prevent rotation of the piston relative to the bearing support member.

2. Machine according to the preceding claim, wherein: The bearing support member (8) comprises a first portion (30) and a second portion (32) assembled to the first portion, the first portion and the second portion together forming a housing (28) receiving the piston.

3. Machine according to the preceding claim, wherein: The second portion (32) forms an abutment to prevent the piston from moving outside the housing.

4. A machine according to any one of the preceding claims, wherein: The bearing support member (8) forms a groove (34) opening in the direction of the cylinder body, and the groove receives the piston (20).

5. A machine according to any one of the preceding claims, comprising a cam (12) and a fixed member (50) passing through the cam, the periphery of the piston comprising an extension (64) extending in a radial direction of the axis to coincide with areas (65) located between the fixed members (50) or with the continuation of these areas in a direction parallel to the axis.

6. Machine according to the preceding claim, wherein: The piston (20) has a cavity (72) which is open in the axial direction and extends perpendicularly to the extension portion (64) in the radial direction of the axis.

7. A machine according to any one of the preceding claims, wherein: The bearing support member (8) has an extension (74) extending into the cavity (72) of the piston.

8. A machine according to any one of the preceding claims, wherein: The periphery of the piston and / or the bearing support member has faces (67, 69) adapted to prevent rotation of the piston relative to the bearing support member and produced by a forming operation without machining.

9. Machine according to any one of the preceding claims, comprising a shaft (4) carrying an abutment (76) forming an obstacle preventing the cylinder block (16) from sliding in the axial direction.

10. A method for manufacturing a machine (2) according to any one of the preceding claims, wherein: The piston (20) is not formed by machining, some faces (67) of the periphery (59) are shaped to prevent the piston from rotating relative to the bearing support member (8), the faces (67) being in a shaped state, and The piston is assembled to the bearing support member with the faces in a formed state.

11. A method for manufacturing a machine (2) according to any one of claims 1 to 9, wherein: The bearing support member (8) is not formed by machining, the surface (69) of the bearing support member is shaped to prevent the piston (20) from rotating relative to the bearing support member, the surface of the bearing support member that is shaped to prevent rotation is in a shaped state, and The piston is assembled to the bearing support member, and the surface (69) of the bearing support member that is shaped to prevent rotation is in a shaped state.

12. The method of manufacturing a machine according to claim 7, wherein: The bearing support member (8) is not formed by machining, the extension (74) is in a formed state, and The piston is assembled to the bearing support member via the extension portion in a formed state.

13. The method according to any one of claims 10 to 12, wherein: The piston (20) and / or the bearing support member (8) are machined.

14. The method according to any one of claims 10 to 13, wherein: preparing an assembly comprising a brake piston connected to the bearing support member, and The assembly is mounted on a housing or a rotating part of the machine.

15. A method of manufacturing a machine according to claim 2 according to any one of claims 10 to 14, wherein: The first part (30) is assembled to the second part (32), and the piston (20) is inserted between the first part and the second part.

16. The method according to the preceding claim, wherein: At least one spring is arranged in the first part (30), and the brake piston (20) is assembled to the second part (32), with a seal interposed between the brake piston and the second part.

17. The method according to any one of claims 15 to 16, wherein: A sealing element is interposed between oppositely facing surfaces of the first and second parts.

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