DE102016215211A1 - Radial piston machine with multi-disc brake - Google Patents

Abstract

The invention relates to a radial piston machine (10) having a housing (20) in which a rotor (30) is rotatably mounted by means of at least one pivot bearing (12; 13) with respect to a rotation axis (11), wherein on the housing (20) an endless at least one piston (21) is movably received radially to the axis of rotation (11) in the rotor (30), wherein its movement path through the control surface (24) defines radially outward wherein a braking device (50) is provided which has a plurality of first and a plurality of second brake disks (51, 52) which are arranged alternately next to one another in the direction of the rotational axis (11), wherein a second or a first brake disk (52, 51) in the direction of the axis of rotation (11) directly on a contact surface (36) on the rotor (30) can be supported. According to the invention, the first and the second brake discs (51, 52) are arranged in the direction of the axis of rotation (11) between the abutment surface (36) and a pivot bearing (12) closest to the abutment surface (36).

Description

The invention relates to a radial piston machine according to the preamble of claim 1.

From the US 6357558 B1 and the US 5115890 A In each case, a radial piston machine with a braking device is known, which has a plurality of first and second brake disks.

In the GB 2283541 A is also described as prior art, a radial piston engine having a basic structure in which the radial piston engine between the rotary bearings and the fluid distributor is arranged. The rotor of the radial piston engine is connected to a separate drive shaft in rotary drive connection, which protrudes with drive means from the housing.

The object of the present invention is to integrate a brake device with a plurality of first and second brake plates in a radial piston machine, which according to the GB 2283541 A is constructed. The radial piston machine according to the invention has the advantage that it is particularly space-saving. In addition, the fluid distributor and the radial piston engine of a known radial piston machine can be used almost unchanged. Only the first housing part with the rotary bearing and the drive shaft must be changed in the context of the invention over the prior art. As a result, the radial piston machine can be manufactured inexpensively because it has many parts which are also present in a radial piston machine which has no braking device.

According to claim 1, it is proposed that the first and the second brake discs are arranged in the direction of the axis of rotation between the contact surface and a pivot bearing closest to the contact surface. The housing preferably comprises a first, a second and a third housing part, which are fixedly connected to each other, wherein the second housing part is arranged in the direction of the axis of rotation between the first and the third housing part, wherein the control surface is arranged on the second housing part. In the third housing part, a fluid distribution device is preferably accommodated, wherein the at least one rotary bearing is accommodated in the first housing part. The contact surface is preferably flat and aligned perpendicular to the axis of rotation.

In the dependent claims advantageous refinements and improvements of the invention are given.

It can be provided that all pivot bearings are arranged in the direction of the axis of rotation on the same side of the contact surface. Preferably, a plurality, in particular two, pivot bearings are provided, which are all received in the first housing part. In a radial piston machine, which has this basic structure, the invention results in a particularly large space saving.

A fluid distribution device may be provided, which has a first and a second fluid connection, wherein the fluid distribution device is configured such that the at least one first fluid chamber can be brought into fluid communication with the first or the second fluid port by rotation of the rotor, wherein the fluid distribution device in Direction of the axis of rotation on the side facing away from the first and second brake plates side of the contact surface is arranged. In a radial piston machine, which has this basic structure, the invention results in a particularly large space saving.

It can be provided a separate drive shaft, which is rotatably supported by means of the at least one pivot bearing on the housing, wherein the rotor is received on the drive shaft, wherein the drive shaft has an external toothing, which engages in a first internal toothing on the rotor such a positive fit, that the rotor with respect to the axis of rotation rotatably connected to the drive shaft, wherein a separate coupling part is provided, which engages with a second internal toothing in the outer toothing of the drive shaft, wherein the second brake plates are rotatably connected with respect to the rotational axis with the coupling part. By introducing the coupling part, the known drive shaft must be extended only in the region of the external toothing in order to adapt it to the invention. It can therefore be made particularly inexpensive. The coupling part is very simple. The external teeth and the first and the second internal teeth are preferably formed as splines. The coupling part is preferably formed as a profile body, which has a constant cross-sectional shape in the direction of the axis of rotation. Externally on the coupling part a plurality of grooves are preferably provided, which run parallel to the axis of rotation, wherein the second brake plates engage in each case with adapted projections in said grooves form-fitting manner.

It can be provided that the coupling part is arranged between the rotor and the bearing surface nearest bearing pivot bearing. The bearing surface closest to the first rotary bearing is preferably supported via the coupling part in the direction of the axis of rotation on the rotor. The coupling part thus fulfills two functions, namely the rotational drive of the second brake plates and the axial support of the rotor.

It can be provided that the rotor is provided with a recess pointing in the direction of the axis of rotation, wherein the coupling part protrudes into said recess. In this way, it is ensured that the outermost first or second brake disk bears against the contact surface over its entire surface. Especially in the corner transition between contact surface and coupling part local voltage peaks are excluded.

It may be provided a brake piston which surrounds the axis of rotation annularly, wherein it is movable in the direction of the axis of rotation, wherein the brake piston is at least partially disposed around the bearing surface of the nearest pivot bearing around, wherein the first and second brake plates by means of the brake piston against the rotor are braced. With the brake piston, the brake device, in particular hydraulically actuated. The proposed arrangement of the brake piston almost no additional space is required in the direction of the axis of rotation. The brake piston is preferably rotationally symmetrical with respect to the axis of rotation.

It can be provided that the housing has a ring-like extension, wherein the bearing surface of the next nearest pivot bearing is radially inwardly received on the annular extension, wherein the brake piston is at least partially outside arranged around the annular extension around. As a result, the space required for receiving the brake piston free space is provided in the housing, at the same time a sufficient support for said rotary bearing is ensured. The annular extension is preferably formed rotationally symmetrical with respect to the axis of rotation.

It can be provided that the brake piston is designed in the manner of a stepped piston having a first and a separate second outer peripheral surface, wherein the second outer peripheral surface is arranged offset radially inwardly relative to the first outer peripheral surface, wherein the first outer peripheral surface rests against the housing. Thus, the brake piston can be brought into direct contact with the brake discs, without further parts are required. The second outer circumferential surface preferably forms a radially inner boundary surface of a second fluid chamber assigned to the brake piston. The first and second outer peripheral surfaces are preferably circular-cylindrical with respect to the axis of rotation, wherein they may be interrupted, for example by sealing grooves. The first and second outer circumferential surfaces are preferably arranged immediately adjacent to one another in the direction of the longitudinal axis. The first outer circumferential surface is preferably fluid-tight against the housing.

It may be provided a separate locking ring, which rests with its outer side on the housing, wherein it rests with its inner side on the second outer peripheral surface of the brake piston, wherein the locking ring is supported in the direction of the axis of rotation on the housing. As a result, the assembly of the brake piston is much easier, since it can be installed before or together with the lock ring. The brake piston, the closure ring and the housing preferably define a second fluid chamber. By pressurizing the second fluid chamber, the braking engagement on the first and the second brake discs can be canceled. The closure ring is preferably rotationally symmetrical with respect to the axis of rotation. The closure ring is preferably fluid-tight on the housing and on the second outer peripheral surface. It is preferably supported on the housing via a separate first securing ring in the direction of the axis of rotation.

It can be provided that between the brake piston and the housing at least one separate spring is installed, wherein the brake piston is loaded by the spring in the direction of the contact surface with a force. Thus, the rotor can not rotate relative to the housing, as long as the second fluid chamber is not pressurized. The spring is preferably designed in the form of a plate spring.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination indicated, but also in other combinations or in isolation, without departing from the scope of the present invention.

The invention will be explained in more detail below with reference to the accompanying drawings. It shows:

1 a longitudinal section of a radial piston machine according to the invention; and

2 an enlarged section of 1 ,

1 shows a longitudinal section of a radial piston engine according to the invention 10 , in which 2 an enlarged section of 1 shows. The radial piston machine 10 includes a housing 20 , which consists of a first, a second and a third housing part 21 ; 22 ; 23 is composed. The parts mentioned are made by several bolts 26 firmly held together, the second housing part 22 between the first and the third housing part 21 ; 23 is arranged. In the first housing part 21 are all pivot bearings 12 ; 13 and the brake device 50 arranged such that the corresponding assembly are pre-assembled can. In the third housing part 23 is the fluid distribution device 80 arranged such that the corresponding assembly can be pre-assembled.

The second housing part 22 overruns the rotor 30 , which by means of the pivot bearing 12 ; 13 with respect to the axis of rotation 11 is rotatably mounted. The pivot bearings 12 ; 13 are preferably designed as a radial roller bearing, in particular as a tapered roller bearing. In the rotor 30 are several pistons 31 radial to the axis of rotation 11 movably received, wherein they are preferably identical and uniformly distributed around the axis of rotation 11 are arranged around. At its radially inner side, each piston limits 31 together with the rotor 30 a respectively associated first fluid chamber 35 , Outside around the pistons 31 around is a control surface 24 on the second housing part 22 arranged on the pistons 31 to assign. The control area 24 runs endlessly around the axis of rotation 11 around, with their distance to the axis of rotation 11 along the circumference of the control surface 24 varied. By centrifugal forces and by those in the first fluid chambers 35 acting hydraulic forces become the pistons 31 against the control surface 24 pressed. The pistons 31 are preferably hydrostatically in the piston 31 rotatably mounted rollers 34 at the control area 24 to minimize frictional forces. The result is a rotational movement of the rotor 30 with a stroke of the piston 31 accompanied, the pistons 31 during one revolution of the rotor 30 preferably perform several strokes.

The fluid distribution device 80 located in 1 on the left side of the rotor 30 at. The fluid distribution device 80 is with respect to the axis of rotation 11 rotatably received in the housing, so that the rotor 30 relative to the fluid distribution device 80 rotates.

The fluid distribution device 80 is by pressurizing the first and second fluid port 81 ; 82 and by means of a spring in the third fluid chamber 83 against the rotor 30 pressed so that the leaks at the junction of the Fluidverteilvorrichtung 80 to the rotor 30 are low. The fluid distribution device 80 forms a first and a second fluid port 81 ; 82 , each associated with an associated (in 1 and 2 not visible) connecting hole outside the housing is connected. In the fluid distribution device 80 and the rotor 30 a channel system is provided, which is designed so that each first fluid chamber 35 by rotation of the rotor 30 optionally with the first or second fluid port 81 ; 82 is fluidically connectable. If the radial piston machine 10 For example, operated as a motor, pressurized fluid is supplied under pressure at the first fluid port, wherein it via the second fluid port 82 flowing back to the tank. The pressurized fluid is preferably a liquid and most preferably hydraulic oil. The momentarily radially outwardly moving piston 31 are fluidic with the first fluid port in the above example 81 connected, wherein the remaining piston with the second fluid port 82 are connected. It is possible that a piston 31 for a short time with neither of the two fluid connections 81 ; 82 connected is.

Next is a drive shaft 40 provided, which with drive means 42 out of the case 20 protrudes. The drive means 42 are presently designed as a drive pinion for a chain, wherein any other drive means, such as a drive pin with a splined shaft, may be provided. Between the case 20 and the drive shaft 40 is a sealing ring 43 provided, which is formed for example as a radial shaft seal. This prevents pressurized fluid from the housing 20 exit. The two pivot bearings 12 ; 13 are in the direction of the axis of rotation 11 between the rotor 30 and the drive means 42 arranged, wherein the drive shaft 40 directly in the inner rings of the pivot bearings 12 ; 13 is included. The corresponding outer rings are directly in the housing 20 , in particular in the first housing part 21 , added. The rotor 30 is with respect to the axis of rotation 11 rotatably on the drive shaft 40 added. The drive shaft 40 is this with an external toothing 41 provided, which is formed for example as a splined shaft, wherein the rotor 30 with an adapted first internal toothing 32 is provided, which in said external teeth 41 positively engages. The pressure force of the Fluidverteilvorrichtung 80 in the direction of the axis of rotation 11 gets off the rotor 30 over the coupling part 53 on the inner ring of the pivot bearing 12 transfer, which is closest to the investment area 36 on the rotor 30 is arranged. The coupling part 53 has a second internal toothing 54 also in the external teeth 41 the drive shaft 40 engages, so it is with respect to the axis of rotation 11 rotatably with the drive shaft 40 connected is. Attention is still on the fixing screw 45 over which the rotor 30 with the drive shaft 40 is bolted, and the second circlip 44 , which in a groove in the area of the external toothing 41 is snapped.

Between the rotor 30 and the pivot bearings 12 ; 13 is a braking device 50 arranged, which requires very little space. Opposite in the GB2283541A As described in the prior art radial piston engine had the length of the housing 20 in the direction of the axis of rotation 11 only by the width of the first and second brake discs 51 ; 52 be enlarged. For the brake piston 70 is almost no additional space in the direction of the axis of rotation 11 needed.

The brake device 50 is designed in the manner of a multi-disc brake, as they for example from the US 6357558 B1 or the US 5115890 A is known. It has first brake discs 51 related to the axis of rotation 11 rotatably with the housing 20 , in particular the first housing part 21 , are connected. The first housing part 21 This is provided with several grooves, which are parallel to the axis of rotation 11 run, with the first brake discs 51 engage with projections positively into said grooves. The second brake discs 52 are with respect to the axis of rotation 11 rotatably with the rotor 30 connected. The coupling part 53 This is provided with several grooves, which are parallel to the axis of rotation 11 run, with the second brake plates 52 with adapted projections positively engage in said grooves. The first and the second brake discs 51 ; 52 are each formed as a flat plates with a constant thickness, which for example consist of sheet steel, where they can be provided with a coating which optimizes the abrasion and frictional forces. In the direction of the axis of rotation 11 are the first and the second brake discs 51 ; 52 alternately arranged side by side, so that a first Bremslammelle 51 is arranged between two associated second brake plates and vice versa. A second brake disc 52 lies directly on a contact surface 36 of the rotor 30 on, with a first brake disk 51 directly on the brake piston 70 is applied. At the two last mentioned contact points there is no relative rotation with respect to the axis of rotation 11 instead of.

The contact surface 36 on the rotor 30 is flat, being perpendicular to the axis of rotation 11 runs. In the area of the coupling part 53 is the contact surface 36 with a recess 33 provided, in which the coupling part 53 dips. This ensures that the outermost second brake plate 52 full surface on the contact surface 36 rests.

The brake piston 70 surrounds the axis of rotation 11 ring-like, wherein it is preferably rotationally symmetrical with respect to the axis of rotation 11 is trained. He has a first and a second outer peripheral surface 71 ; 72 , each circular cylindrical with respect to the axis of rotation 11 are formed. The first outer peripheral surface 71 , which has the larger diameter, is located on the housing 20 , in particular on the first housing part 21 ; fluid-tight. You can be provided for this purpose with a circumferential sealing groove in which a sealing ring is added. The second outer peripheral surface 72 lies fluid-tight on a separate locking ring 73 at. The lock ring 73 is rotationally symmetric with respect to the axis of rotation 11 educated. Its outer peripheral surface lies fluid-tight on the housing 20 , in particular on the first housing part 21 , in the present case in alignment with the first outer peripheral surface 71 of the brake piston 70 is arranged. On the of the first and second brake discs 51 ; 52 opposite side of the brake piston 70 is a spring 56 , which is presently designed as a plate spring, between the brake piston 70 and the housing 20 installed under preload. The feather 56 pushes the brake piston 70 accordingly against the first and second brake discs 51 ; 52 so that the braking device 50 is closed, with the rotor 30 not opposite the case 20 can turn.

The brake piston 70 limited together with the lock ring 73 and the first housing part 21 a second fluid chamber 74 which annularly around the first axis of rotation 11 runs, wherein it has a third fluid connection 75 outside on the housing 20 having. By pressurizing the second fluid chamber 74 via the third fluid connection 75 becomes the brake piston 70 in 1 pressed to the right, leaving the braking device 50 is released, causing the rotor 30 opposite the housing 20 can turn. The corresponding fluid pressure also causes the locking ring 73 in 2 is pressed to the left. He is therefore about a first locking ring 76 on the housing 20 supported, so that he does not move. The lock ring 73 can be provided inside and / or outside with circumferential sealing grooves, in each of which a sealing ring is received.

Next is on the ring-like extension 25 on the first housing part 21 to indicate which is rotationally symmetrical with respect to the axis of rotation 11 is trained. Inside the ring-like extension 25 is the outer ring of the pivot bearing 12 recorded, which closest to the contact surface 36 on the rotor 30 is arranged. The brake piston 70 is in sections around the ring-like extension 25 arranged around. He is accordingly sections of the pivot bearing 12 arranged around. This results in a particularly large space savings.

The inner peripheral surface of the brake piston 70 is circular cylindrical with respect to the axis of rotation 11 educated. The same applies to the outer peripheral surface of the ring-like extension, which is arranged opposite with a small distance 25 to.

LIST OF REFERENCE NUMBERS

10

Radial piston engine

11

axis of rotation

12

the contact surface nearest pivot bearing

13

another pivot bearing

20

casing

21

first housing part

22

second housing part

23

third housing part

24

control surface

25

ring-like extension

26

bolts

30

rotor

31

piston

32

first internal toothing

33

recess

34

role

35

first fluid chamber

36

contact surface

40

drive shaft

41

external teeth

42

drive means

43

seal

44

second circlip

45

fixing screw

50

braking device

51

first brake disc

52

second brake plate

53

coupling part

54

second internal toothing

56

feather

70

brake pistons

71

first outer peripheral surface

72

second outer peripheral surface

73

lock ring

74

second fluid chamber

75

third fluid connection (brake)

76

first circlip

80

fluid distribution

81

first fluid connection

82

second fluid connection

83

third fluid chamber

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 6357558 B1 [0002, 0027]
• US 5115890 A [0002, 0027]
• GB 2283541 A [0003, 0004, 0026]

Claims (11)

Radial piston machine ( 10 ) with a housing ( 20 ), in which a rotor ( 30 ) by means of at least one pivot bearing ( 12 ; 13 ) with respect to a rotation axis ( 11 ) is rotatably mounted, wherein on the housing ( 20 ) one endlessly around the axis of rotation ( 11 ) circumferential control surface ( 24 ) is arranged, which on the rotor ( 30 ), the distance between the axis of rotation ( 11 ) and the control surface ( 24 ) along the circumference of the control surface ( 24 ), wherein in the rotor ( 30 ) at least one piston ( 21 ) radially to the axis of rotation ( 11 ) is movably received, whereby its movement path through the control surface ( 24 ) is limited radially outwards, wherein on the radially inner side of the at least one piston ( 21 ) each have an associated first fluid chamber ( 35 ), which in each case of the respective piston ( 21 ) and the rotor ( 30 ) is limited, wherein a braking device ( 50 ) is provided, the plurality of first and a plurality of second brake discs ( 51 ; 52 ), which in the direction of the axis of rotation ( 11 ) are arranged alternately next to each other, wherein the first brake discs ( 51 ) with respect to the axis of rotation ( 11 ) rotatably with the housing ( 20 ), wherein the second brake discs ( 52 ) with respect to the axis of rotation ( 11 ) rotatably with the rotor ( 30 ), wherein a second or a first brake disc ( 52 ; 51 ) in the direction of the axis of rotation ( 11 ) directly on a contact surface ( 36 ) on the rotor ( 30 ) is supportable, characterized in that the first and the second brake discs ( 51 ; 52 ) in the direction of the axis of rotation ( 11 ) between the contact surface ( 36 ) and one of the contact surface ( 36 ) nearest pivot bearing ( 12 ) are arranged. Radial piston machine according to claim 1, wherein all pivot bearings ( 12 ; 13 ) in the direction of the axis of rotation on the same side of the contact surface ( 36 ) are arranged. Radial piston machine according to one of the preceding claims, wherein a fluid distribution device ( 80 ), which has a first and a second fluid connection ( 81 ; 82 ), wherein the fluid distribution device ( 80 ) is formed so that the at least one first fluid chamber ( 35 ) by rotation of the rotor ( 30 ) optionally with the first or the second fluid connection ( 81 ; 82 ) can be brought into fluid communication, wherein the fluid distribution device ( 80 ) in the direction of the axis of rotation ( 11 ) on the first and second brake discs ( 51 ; 52 ) facing away from the contact surface ( 36 ) is arranged. Radial piston machine according to one of the preceding claims, wherein a separate drive shaft ( 40 ) is provided, which by means of at least one pivot bearing ( 12 ; 13 ) on the housing ( 20 ) is rotatably mounted, wherein the rotor ( 30 ) on the drive shaft ( 40 ), wherein the drive shaft ( 40 ) an outer toothing ( 41 ), which in a first internal toothing ( 32 ) on the rotor ( 30 ) engages in such a form-fitting manner that the rotor ( 30 ) with respect to the axis of rotation ( 11 ) rotatably with the drive shaft ( 40 ), wherein a separate coupling part ( 53 ) is provided, which with a second internal toothing ( 54 ) in the external toothing ( 41 ) of the drive shaft ( 40 ), wherein the second brake discs ( 52 ) with respect to the axis of rotation ( 11 ) rotatably with the coupling part ( 53 ) are connected. Radial piston machine according to claim 4, wherein the coupling part ( 53 ) between the rotor ( 30 ) and the contact surface ( 36 ) nearest pivot bearing ( 12 ) is arranged. Radial piston machine according to claim 4 or 5, wherein the rotor ( 30 ) with one in the direction of the axis of rotation ( 11 ) facing recess ( 33 ), wherein the coupling part ( 53 ) in said recess ( 33 ) protrudes into it. Radial piston machine according to one of the preceding claims, wherein a brake piston ( 70 ) is provided, which the axis of rotation ( 11 ) surrounds it in the direction of the axis of rotation ( 11 ) is movable, wherein the brake piston ( 70 ) at least in sections around the contact surface ( 36 ) nearest pivot bearing ( 12 ) is arranged around, wherein the first and the second brake discs ( 51 ; 52 ) by means of the brake piston ( 70 ) against the rotor ( 30 ) are braced. Radial piston machine according to claim 7, wherein the housing ( 20 ) a ring-like extension ( 25 ), wherein the contact surface ( 36 ) nearest pivot bearing ( 12 ) radially inward on the annular extension ( 25 ), wherein the brake piston ( 70 ) at least partially outside the ring-like extension ( 25 ) is arranged around. Radial piston machine according to claim 7 or 8, wherein the brake piston ( 70 ) in the nature of a stepped piston having a first and a separate second outer peripheral surface ( 71 ; 72 ), wherein the second outer peripheral surface ( 72 ) offset radially inwardly relative to the first outer peripheral surface ( 71 ), wherein the first outer peripheral surface ( 71 ) rests against the housing. Radial piston machine according to claim 9, wherein a separate locking ring ( 73 ) is provided, which with its outside on the housing ( 20 ), with its inside on the second outer peripheral surface ( 72 ) of the brake piston ( 70 ) is applied, wherein the locking ring ( 73 ) in the direction of the axis of rotation ( 11 ) on the housing ( 20 ) is supported. Radial piston machine according to one of claims 7 to 10, wherein between the brake piston ( 70 ) and the housing ( 20 ) at least one separate spring ( 56 ) is installed, wherein the brake piston ( 70 ) from the spring in the direction of the contact surface ( 36 ) is loaded with a force.

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