Radial piston machine with brake

Abstract

A radial piston machine includes: a housing; a rotor within the housing, wherein the rotor is rotatable about an axis; a shaft coupled to the rotor for torque transmission; a distributor about the shaft and not rotatable with the rotor, and which contacts the rotor in an axial direction for fluid communication to and from the rotor; a plurality of brake discs, including a first brake disc and a second brake disc arranged side-by-side along an axis, wherein the first brake disc is coupled to the housing for torque transmission, and the second brake disc is coupled to the shaft for torque transmission; and an actuator configured to releasably apply a braking force on the brake discs in an axial direction, wherein the distributor is axially located between the rotor and the actuator, and the brake discs are axially located between the distributor and the actuator, characterized in that, when the braking force is applied, the braking force is supported in the axial direction by the distributor.

Description

Technical Field

[0001] The present invention relates to a radial piston machine, particularly the preamble of claim 1. Background Technology

[0002] Radial piston machines are considered in the art to be rotary hydrostatic machines capable of operating as pumps or motors. A radial piston machine has a rotor in fluid communication, which is achieved via a distributor, which is a non-rotating part, with its end face in contact with the end face of the rotor. A brake is also known in the art, wherein a braking force can be applied to frictionally limit the rotation of the rotor. Such a machine incorporating a brake is known from DE 4407563C2.

[0003] However, it is believed that improvements such as performance, ease of manufacturing, and simplicity of design can be achieved. Summary of the Invention

[0004] The object of the present invention is to provide a structure that can achieve improvements in the above aspects.

[0005] The invention is defined by the subject matter of claim 1. Advantageous developments are set forth in the dependent claims.

[0006] The present invention provides a radial piston machine comprising: a housing; a rotor located within the housing, wherein the rotor is rotatable about an axis; a shaft coupled to the rotor for torque transmission; a distributor about the shaft and not rotatable with the rotor, and contacting the rotor in an axial direction for fluid communication to and from the rotor; a plurality of brake discs including a first brake disc and a second brake disc arranged side-by-side along an axis, wherein the first brake disc is coupled to the housing for torque transmission, and the second brake disc is coupled to the shaft for torque transmission; and an actuator configured to releasably apply a braking force on the brake discs in an axial direction, wherein the distributor is axially located between the rotor and the actuator, and the brake discs are axially located between the distributor and the actuator; when the braking force is applied, the braking force is supported by the distributor in an axial direction.

[0007] For the configuration defined in the previous paragraph, the braking force is supported by the distributor along the axial direction. Therefore, the brake disc can transmit the braking force to the distributor, which in turn can transmit the braking force to the rotor; the braking force maintains contact between the faces of the distributor and the rotor, such as surface-to-surface contact, even when no other load is pushing the distributor toward the rotor. In particular, it is unnecessary to provide components such as additional springs to press directly onto the distributor along the rotor direction, nor is it necessary to provide a lower-diameter portion of the housing, such as a partition, to support the springs. Access to the interior of the housing is facilitated, especially during its manufacture.

[0008] It can be specified that when no braking force is applied, the distributor is inserted with axial clearance between one rotor and the other brake disc; and / or when braking force is applied, the distributor is axially pushed by the rotor on one side and by the brake disc on the other side, preferably by only these two. This allows for more reliable transmission of braking force.

[0009] It can be specified that the distributor does not make direct axial contact with the housing. Therefore, the distributor can more reliably transmit braking force to the rotor.

[0010] It can be specified that the housing contains the distributor and brake disc, without inserting between them. Therefore, the distributor can more reliably transmit braking force to the rotor.

[0011] It can be specified that when braking force is applied, the brake disc transmits all braking force to the distributor. Preferably, the distributor can transmit all braking force to the rotor. Therefore, when braking is applied, the distributor can press more reliably against the rotor.

[0012] It can be specified that when braking force is applied, one of the brake discs directly contacts the distributor.

[0013] Using the configuration defined in the previous paragraph, one of the first brake discs or one of the second brake discs can act directly on the distributor. This facilitates a more efficient design and allows for more reliable transmission of braking force. Because the load from the brake discs is not distributed into the load path, which could potentially transfer at least a portion of the braking force from the distributor to, for example, the housing, this eliminates the need for a portion of the housing (such as a diaphragm) to be pressed between the distributor and the brake discs. This reduces the weight of the housing.

[0014] It can be specified that one or more components are provided between a brake disc on one side and a distributor on the other side, said one or all components being axially movable relative to the housing (e.g., with axial clearance fit), and that when braking force is applied, one of the brake discs contacts the distributor via said one or all components.

[0015] Using the construction defined in the previous paragraph, even if components such as spacers or springs are provided between the distributor and the brake disc, the transmission of braking force from the brake disc to the distributor (and further to the rotor) can be ensured, because all of the aforementioned components are neither axially fixed to the housing nor integral with the housing.

[0016] Clearance can be provided to allow axial play between any of the rotor, distributor, one or more brake discs, and actuator, especially when no braking force is applied.

[0017] It can be specified that the actuator can be operated by a pressurized fluid hydraulically, such that: when the pressure is a first pressure, no braking force is applied, and when the pressure is a second pressure lower than the first pressure or when there is no pressure, braking force is applied.

[0018] Using the structure defined in the previous paragraph, it is possible to hydraulically control the braking force.

[0019] It can be specified that the biasing device, preferably a biasing member (e.g., a spring), and more preferably a disc spring, pushes the actuator toward the brake disc. In other words, the actuator and the biasing device can form a piston-spring assembly. Preferably, the preloaded spring can act as a piston-driven actuator in a first direction (such as the braking actuation direction).

[0020] The actuator may be able to move axially relative to the housing.

[0021] Fluid pressure can be transmitted to one side of the actuator to generate force on the actuator in a second direction opposite to the first direction (such as the direction of brake release).

[0022] It can be specified that the pressure acts directly on the distributor to generate a force along the axis pointing towards the rotor.

[0023] Using the construction defined in the previous paragraph, the liquid contacts the distributor and can also contact the brake disc. Contact between the rotor and distributor can be further ensured by any forces generated by pressure transmission. Furthermore, since the distributor is not isolated from the fluid, fewer sealing surfaces need to be controlled (smaller runout tolerances); components such as the housing are easier to manufacture.

[0024] It can be stipulated that at least the distributor is isolated from any fluids operating the actuator (e.g., by means of a seal).

[0025] Using the configuration defined in the previous paragraph, the first pressure, which is the first actuator pressure, does not contact the distributor. Since the axial load on the distributor is essentially only due to the forces generated by the braking force and any driving pressure (the pressure that drives the rotor to rotate), the movement of the distributor and / or brake disc can be controlled more reliably.

[0026] The seal can be positioned in the (radial) gap defined by the housing and the actuator, thereby isolating the distributor from any fluids operating the actuator.

[0027] The seal can be located on one axial side of the brake disc, which faces the actuator.

[0028] The seal can be disposed between the circumferential surface of the actuator and the circumferential surface of the housing.

[0029] Seals may include or be formed as sealing members, such as O-rings and / or lip seals.

[0030] It can be stipulated that the first adjacent part, which is the adjacent part between the rotor and the distributor, produces a sealing effect between them.

[0031] Using the construction defined in the previous paragraph, a sealing effect is achieved while allowing relative rotation. This is because the distributor can be axially pushed (e.g., supported thereon) by the rotor due to the braking force transmitted to it by the brake disc and / or by the fluid pressure acting on it. This improves the sealing effect at the first adjacent portion.

[0032] The first adjacent part can be a direct contact between the rotor and the distributor, such as surface-to-surface contact, and more preferably metal-to-metal contact.

[0033] It can be specified that the shaft is axially supported by the bearing, the shaft is connected to the rotor to allow axial movement between them, and as a second adjacent part between the rotor and the bearing, it creates a sealing effect between them.

[0034] The sealing effect at the second adjacent part can be improved by using the structure defined in the paragraph above.

[0035] The second adjacent part can be a direct contact between the rotor and the bearing, such as surface-to-surface contact, and more preferably metal-to-metal contact.

[0036] Contact can occur on planes and / or surfaces perpendicular to the axis. This achieves a sealing effect between them. The bearing can support the distributor axially, at least via the rotor. The rotor and bearing can move axially relative to each other.

[0037] It can be specified that the housing includes a single-piece housing that at least accommodates the distributor and brake disc.

[0038] Using the construction defined in the previous paragraph, the housing can have a simpler transition from its portion surrounding the distributor to its portion surrounding the brake disc. The manufacture of the housing, particularly any broaching within it, is facilitated.

[0039] It can be specified that the inner circumference of the housing is provided with splines, and preferably, all areas of the housing excluding the spline area are arranged to be radially further away from the axis than the root of the spline.

[0040] Utilizing the construction defined in the previous paragraph, manufacturing is further facilitated because no broaching tool is obstructed by a housing region that is closer to the axis than the radial direction of the internal spline (e.g., closer to the axis than the radial direction of the large diameter of the spline). Therefore, the distributor and brake disc can be easily housed in a single-piece housing component.

[0041] It can be specified that the distributor has at least one channel, such as an annular channel disposed on its outer periphery, to communicate fluid between ports on the rotor and the housing. First and second channels can be provided. This channel can communicate with one or more axially extending channels in the distributor.

[0042] The channel can be sealed by at least one channel seal, which may include or be formed as an O-ring and / or a bushing. The seal can fill the gap defined by the distributor and the housing. In this way, the channel seal maintains its sealing function while allowing axial movement between the distributor and the housing. Attached Figure Description

[0043] The embodiments are described below with reference to the accompanying drawings, in which: Figure 1 A radial piston machine according to an embodiment is shown. Figure 2 Modifications to the embodiments are shown, and Figure 3 A radial piston machine is shown according to a comparative example. Detailed Implementation

[0044] Figure 1 A longitudinal cross-sectional view of a radial piston machine (hereinafter referred to as "machine 1") incorporating a brake is shown. When used in a driving vehicle, the brake can function as a parking brake. The machine has a housing (as a stator) in which a rotor 4 is disposed. A shaft 8 is coupled to the rotor 4 such that torque can be transmitted between them. For example, the rotor 4 is slidably fitted onto the shaft 8 in a torque-transmittable manner (such as by means of a keyway or spline). The shaft 8 may include or be formed as several shafts. The rotor 4 contacts a distributor 10, which will be described in more detail later. The shaft 8 is rotatably supported by the housing 2 and axially fixed to the housing 2.

[0045] Rotor 4 is rotatable about axis 6. Rotor 4 has an annular cylinder block with an axial bore passing through its center, through which shaft 8 passes. Rotor 4 has a plurality of radially extending cylindrical bores 16 (hereinafter referred to as "bore 16") arranged in a circumferential pattern, each bore 16 receiving a reciprocating piston 18. The radially outer end of each piston 18 is connected to a cylindrical roller 20. Each piston 18 can reciprocate under the impingement of pressurized fluid in the cylinder block, while its roller 20 is supported on a cam ring 22. It is known that rotor 4 can be rotated by coordinating the fluid communication in and out of bore 16 with the angular position of rotor 4.

[0046] The rotor 4 abuts against a bearing 24 on one axial side, the bearing 24 being axially supported on the shaft 8. The bearing 24 may be configured to support thrust loads. Alternatively or additionally, the rotor 4 may abut on a stepped portion of the shaft 8, or on a locating member axially fixed to the shaft 8, such as a resilient retaining ring.

[0047] The groove 26 is provided at the radial inner end of the rotor 4 to allow space for the spacer 27 and the locating ring 28 to be fixed to the shaft 8, and to limit the axial movement of the bearing 24.

[0048] Axially extending fluid channels (hereinafter referred to as "rotor channels 12") are arranged in a circumferential pattern around axis 6 relative to the radially inner end side of the bore 16 near the rotor 4. The channels 12 open at a face of the rotor 4 (hereinafter referred to as "rotor face 14"), which may be called the timing face or the connecting face. Each rotor channel 12 is fluidly connected to a corresponding bore 16. The rotor face 14 includes a planar surface perpendicular to axis 6.

[0049] The distributor 10 is a cylindrical portion about the shaft 8 and cannot rotate with the shaft 8. The outer periphery of the distributor 10 is configured to fit tightly with the inner periphery of the housing, with a clearance. The distributor 10 is axially slidably coupled to the housing so that torque can be transmitted between them. For example, the distributor 10 can be rotatably fixed to the housing.

[0050] An axially extending fluid channel (hereinafter referred to as "distributor channel 32") is arranged in a circumferential pattern around axis 6 in distributor 10. Channel 32 opens at a face of distributor 10 (hereinafter referred to as "distributor face 34") facing rotor 4. Distributor face 34 may be referred to as timing face or communication face, and it includes a planar surface perpendicular to axis 6. The pitch circle diameter of distributor channel 32 is substantially equal to the pitch circle diameter of rotor channel 12.

[0051] Two annular grooves, corresponding to the first and second channels 40, 42, are formed in the outer periphery of the distributor 10. The first channel 40 communicates with some distributor channels 32. The second channel 42 communicates with other distributor channels 32. Each seal 44, 46, 48 disposed in the corresponding groove occupies the gap between the outer periphery of the distributor 10 and the inner periphery of the housing. Therefore, the channels 40, 42 can be isolated from each other and from their exterior. The channels 40, 42 are fluidly connected to corresponding high-pressure ports and low-pressure ports (not shown) disposed in the housing, these ports being referred to as drive ports. Each seal 44, 46, 48 includes an O-ring and a bushing. Each seal 44, 46, 48 may be referred to as a channel seal.

[0052] The outer periphery of the distributor 10 is provided with a series of surfaces of different diameters in a stepped manner. By setting the dimensions of the channels 40, 42 in a manner known in the prior art, when the channels 40, 42 are filled with pressurized fluid for driving the rotor, a force is realized on the distributor 10 to generate a compensating force (hereinafter referred to as "channel thrust") along the axis 6 and pointing toward the rotor 4. The distributor 10 can be pressed against the rotor 4 by the channel thrust.

[0053] The distributor 10 (particularly distributor face 34) can directly or indirectly contact the rotor 4 (particularly rotor face 14) to axially push it. Therefore, fluid can flow between the rotor 4 and the distributor 10. A sealing effect is achieved between them by pushing the distributor 10 toward the rotor 4. The mating parts can have surface-to-surface contact, optionally metal-to-metal contact.

[0054] As a braking device, a friction brake is connected between the rotor 4 and the housing 2. The brake includes a braking assembly comprising a plurality of first and second brake discs 50, 52 arranged side-by-side as disc-shaped or plate-shaped rings along axis 6, each surrounding shaft 8. The braking assembly is disposed adjacent to the distributor 10 at its axial end opposite to the rotor 4. Some, preferably all, of the first and second brake discs 50, 52 are arranged alternately in the axial direction. The housing 2 is provided with splines 56 in portions such as the smallest diameter portion of the inner circumference of the housing. The shaft 8 is provided with splines 54 on its outer circumference, at least in the region of the shaft 8 that axially coincides with the splines 56 of the housing. Each first brake disc 50 is provided with splines on its outer circumference, which slidably engage with the splines 56 of the housing to allow torque transmission between them. Each second brake disc 52 is provided with splines on its inner circumference, which slidably engage with the splines 54 of the shaft 8 to allow torque transmission between them. The first and second discs 50 and 52 are allowed to contact each other in the axial direction and move apart.

[0055] Machine 1 is provided with an actuator 60 for releasably compressing brake discs 50, 52 together. The actuator 60 is formed as a disc-shaped or plate-shaped member and faces the brake discs. The actuator 60 fits with a clearance within the inner circumference of the housing 2 to allow axial sliding between them. A seal 62 is disposed in the clearance and may include or be formed as an O-ring in a groove on the actuator 60. The actuator 60 has an annular protrusion 64 located halfway between its inner diameter and its outer diameter extending axially toward the brake discs 50, 52, to be directly or indirectly supported on these brake discs by surface-to-surface contact. The outer diameter of the protrusion 64 is configured to have a radial clearance with the spline 56. A shaft 8 does not penetrate the actuator 60 and provides axial clearance between them.

[0056] A biasing device, forming a disc spring 68, is arranged between the actuator 60 and the cover 69, wherein the cover closes the open end of the housing 2 and is fixed to the housing 2. The disc spring 68 is preloaded such that it pushes the actuator 60 and the cover 69 apart by spring force. When braking is applied, the friction generated between the opposing surfaces of the first and second brake discs 50, 52 achieves braking of the rotating part. At this time, the distributor 10 transmits the load from the disc spring 68 to the rotor 4 via the actuator 60 and the brake discs 50, 52. In this way, the brake discs 50, 52 can transmit substantially all the braking force to the distributor 10; that is, the braking force does not bypass the distributor 10 completely or partially, for example, by transmitting it to the housing 2 or the portion axially fixed to the housing 2.

[0057] Therefore, rotor 4 is positioned adjacent to bearing 24 at one axial end of the rotor and adjacent to distributor 10 at the other axial end of the rotor. Brake discs 50 and 52 are positioned adjacent to distributor 10 at one axial end of them and adjacent to actuator 60 at the other axial end of them. Actuator 60 is positioned between brake discs 50 and 52 on one side and disc spring 68 on the other side.

[0058] A pressurizable cavity 70 is provided within the housing 2, which is at least exposed to the shaft 8, bearing 24, rotor 4, distributor 10, actuator 60, and housing 2, and houses the brake disc. When the cavity 70 is filled with pressurized fluid having a first actuator pressure (e.g., via a third port, not shown, provided in the housing), pressure is transmitted to the actuator 60 to generate a first axial force opposite to the spring force. Thus, the compressive force (“braking force”) on the brake disc can be at least partially released. The braking force is restored when the actuator pressure drops to a second actuator pressure below the first actuator pressure, or when there is no pressure. Fluid for actuating the actuator contacts the distributor 10, thus the actuator pressure is transmitted to the distributor 10 to generate a second axial force in the direction of the rotor 4. The second axial force maintains or improves the contact between the rotor face 14 and the distributor face 34. Channel seals 44, 46, and 48 isolate the channel 10 from the fluid from the cavity 70.

[0059] In typical operation, rotor 4 rotates because its cylinder is connected to the aforementioned drive port via distributor 10. The direction of rotation is determined by the selected control mode. Simultaneously, cavity 70 is pressurized by fluid under the pressure of the first actuator, causing actuator 60 to be pushed away from brake discs 50 and 52, thereby releasing the brake. The sealing contact between distributor 10 and rotor 4 is achieved not only by the aforementioned second axial force but also by the channel thrust.

[0060] When the distributor 10 is pushed against the rotor 4, the rotor 4 is in turn pushed against the bearing 24, thus achieving a sealing effect at the contact surface between the latter two.

[0061] During braking, the actuator pressure decreases to the second actuator pressure, or there is no pressure, causing actuator 60 to move towards brake discs 50 and 52 under the load of disc spring 68 to compress them. Brake discs 50 and 52 act directly on distributor 10. Therefore, even when the channel thrust is removed or reduced, distributor 10 is pushed against rotor 4 by braking force. Contact between rotor 4 and distributor 10 is reliably maintained. Similarly, when the machine is started, contact can be reliably maintained even when the brake is released, regardless of the state of channel thrust.

[0062] Modifications to the Implementation Examples Modifications to the above embodiments are described below, with differences between these modifications identified. For example... Figure 2 As shown, the main difference from this embodiment is the addition of a seal 171, which is disposed between a) the protrusion 164 on the actuator 160 and b) the axially extending annular inner wall 166 of the housing 102, to seal the radial clearance defined by them while allowing axial movement between them. The seal 171 is disposed on one side of the brake discs 50, 52, facing the actuator 160. The seal 171 may include or be formed as an O-ring and / or a lip seal. Thus, a cavity 170 is created that exposes the radially higher portions of the actuator 160 and the housing 102. The seal 171 isolates the cavity 170 from portions such as the rotor 4, shaft 8, distributor 10, and brake discs 50, 52. In this way, the pressure in the cavity 170 can be controlled to operate the brake without being transmitted to at least the distributor 10. Fluid in the cavity 170 can be easily sealed. A suitable surface area on the actuator 160 exposed to the actuator pressure in the cavity 170 can be more easily achieved. Nevertheless, the distributor 10 can still be pushed toward the rotor 4 by providing the aforementioned corridor thrust and optionally by braking force.

[0063] To illustrate the effects and advantages of the embodiments and their modifications, a comparative example of a radial piston machine is described below. For example... Figure 3As shown, the machine 201 of the comparative example has a housing including a first housing 202a and a second housing 202b. The first housing 202a surrounds a distributor 210. The first housing 202a has a partition 211 positioned between brake discs 250, 252 and the distributor 210, and has an inner diameter lower than the inner diameter of the other parts of the first housing 202a. A helical spring 205 is disposed between the partition 211 and the distributor 210 to push the distributor 210 against the rotor 204. Braking force from a disc spring 268 is applied to the brake discs 250, 252 via an actuator 260. A force opposite to the braking force causes the brake to be released by pressurizing fluid in a cavity 270 defined by the actuator 260 and the housing 202b. The distributor 210 does not support the braking force. The braking force is supported by the partition 211. Furthermore, since the spline 256 on the inner side of the housing 202b is made by broaching, the housing must be made into separate parts 202a and 202b, wherein the partition 211 must be provided on the first housing 202a so that the broaching operation on the second housing 202b is not hindered.

[0064] However, in this embodiment and its variations, since the braking force is supported by the distributor 10, it is possible to maintain contact between the distributor 10 and the rotor 10 even when the channels 40, 42 are not pressurized (e.g., during periods when the machine is not rotating). Therefore, it is not necessary to provide features such as additional springs supported by the housing. A partition is not required between the distributor and the braking assembly. Additional components, such as washers or springs, inserted between the actuator and the distributor can still be provided, wherein such components are not axially fixed to the housing. A combination of direct and indirect contact between the brake disc on one side and the distributor on the other can be provided, for example by providing a groove on the surface of the distributor facing the brake disc, in which a component (e.g., a spring) has been fitted.

[0065] Therefore, it facilitates providing splines for the area of ​​the inner periphery of the housing, wherein other areas of the housing 2, 102 are set further away from the axis 6 than the spline 56, such as further away from the axis 6 than the main circle 20 of the spline 56.

[0066] The housings 2 and 102 that accommodate at least the distributor 10 and the brake discs 50 and 52 can be formed as a single piece (integral) housing, in particular, wherein the spline 56 is integrally formed on the housings 2 and 102, for example by means of broaching.

[0067] When seal 171 is omitted, such as in the unmodified embodiment, housing 2 and / or actuator 60 can be manufactured (e.g., machined) with less runout (e.g., concentricity). Manufacturing and inspection work can be further reduced when actuators 60, 160 do not have a center bore.

[0068] Figure Labels Radial piston machine................ 1,201 Shell...................... 2, 102, 202a, 202b Rotor...................... 4,204 Axis axis...................... 6 Shaft........................ 8 Distributor.................... 10, 210 Rotor channel.................. 12 Rotor face.................... 14 Hole........................ 16 Piston...................... 18 Roller...................... 20 Cam ring.................... 22 Bearings...................... 24 Groove...................... 26 Spacer..................... 27 Positioning ring..................... 28 Distributor channels................. 32, 20 Distributor face................... 34 First Corridor...................40 Second Corridor................... 42 Corridor seals................. 44, 46, 48 First brake disc (stator)......... 50, 250 Second brake disc (rotor)......... 52,252 Spline shaft..................... 54 Casing spline................... 56, 256 Actuators..................... 60, 160, 260 Seal (actuator outer diameter)....... 62 Protrusion (actuator)............. 64,164 Disc spring................... 68, 268 Cover......................... 69 Cavity....................... 70, 170, 270 Inner wall....................... 166 Seals...................... 171 Spring........................ 205 Partition........................ 211

Claims

1. A radial piston machine, comprising: Shell (2) The rotor (4) is located within the housing, and the rotor is rotatable about an axis (6). The shaft (8) is connected to the rotor for torque transmission. A distributor (10), which is about the shaft and cannot rotate with the rotor, and which contacts the rotor in the axial direction, is used to communicate fluid to and from the rotor. A plurality of brake discs, including a first brake disc (50) and a second brake disc (52) arranged side-by-side along an axis, wherein the first brake disc is coupled to the housing for torque transmission, and the second brake disc is coupled to the shaft for torque transmission, and Actuator (60), configured to releasably apply braking force on brake disc in the axial direction, wherein The distributor is axially located between the rotor and the actuator, and the brake disc is axially located between the distributor and the actuator, characterized in that... When braking force is applied, the braking force is supported by the distributor in the axial direction. When braking force is applied, one of the brake discs directly contacts the distributor.

2. The radial piston machine according to claim 1, wherein one or more components are disposed between the brake disc on one side and the distributor on the other side, and one or all of the components are axially movable relative to the housing, and When braking force is applied, one of the brake discs contacts the distributor via one or all of the components.

3. The radial piston machine of claim 1, wherein the housing defines a cavity in which pressurized fluid acts on the actuator, and the pressure of the pressurized fluid acts directly on the distributor to generate a force along the axis toward the rotor.

4. The radial piston machine according to any one of the preceding claims, wherein The actuator can be operated by a pressurized fluid hydraulically, such that: When the pressure is the first pressure, no braking force is applied, and When the pressure is a second pressure lower than the first pressure, or when there is no pressure, braking force is applied.

5. The radial piston machine of claim 4, wherein, The pressure acts directly on the distributor to generate a force along the axis pointing towards the rotor.

6. The radial piston machine according to claim 4, wherein At least the dispenser is isolated from any fluid operating the actuator by means of a seal (171).

7. The radial piston machine according to any one of the preceding claims, wherein The first adjacent part is the adjacent part between the rotor and the distributor, which creates a sealing effect between them.

8. The radial piston machine according to any one of the preceding claims, wherein, The shaft is axially supported by bearings. The shaft is coupled to the rotor to allow axial movement therebetween, and The second adjacent portion, which serves as the adjacent portion between the rotor and the bearing, creates a sealing effect between them.

9. The radial piston machine according to any of the preceding claims, wherein, The housing includes a single-piece housing that at least accommodates the distributor and the brake disc.

10. The radial piston machine according to any of the preceding claims, wherein, The area around the inner periphery of the housing is provided with a spline (56), and all areas of the housing excluding the spline area are arranged to be radially further away from the axis than the root of the spline (56).

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