EP4365436A1

EP4365436A1 - Multi piston machine with at least three switchable displacement volumes and a central first control valve

Info

Publication number: EP4365436A1
Application number: EP22205722.6A
Authority: EP
Inventors: Johann Praeffcke
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2022-11-07
Filing date: 2022-11-07
Publication date: 2024-05-08

Abstract

The invention concerns multi piston machine (10) with a rotor (70), wherein the pistons (1.1 - 1.18) abut against a cam surface (21) with multiple lobes (22). According to the invention the multi piston machine (10) is switchable between at least three non-zero displacement volumes by means of a first and a second control valve, wherein the first and the second control valve are connected to the first and the second working (11; 12) port respectively, wherein the first to fourth fluid chambers (31 - 34) are annular with respect to the axis of rotation (13), being arranged distributed along the axis of rotation (13), wherein the first control valve is arranged radially inside the first to fourth fluid chambers (31 - 34), wherein the first control valve is fluidically connected to the second and the third fluid chamber (32; 33), wherein second control valve is arranged radially outside the first to fourth chambers (31 - 34), wherein the second control valve is fluidically connected to the first and the fourth fluid chamber (31; 34), wherein the first chamber (31) is located closer to the second control surface (80) than the second to fourth chambers (32 - 34).

Description

The invention concerns a multi piston machine according to the preamble of claim 1.
A corresponding multi piston machine is known from US 6 050 173 A , which is configured as a radial piston motor. This multi piston machine has two switchable displacements. In a first switching position all pistons are connected either to the first or the second working port in each rotational position of the rotor. In a second switching position there is in internal short circuit connection between a first group of pistons which are not connected to the first or second working port. The remaining pistons form a second group of pistons which are connected either to the first or the second working port.
US 4 807 519 A shows another radial piston motor with two switchable displacements. To avoid pressure variations within the short-circuited pistons there is a connection to a pilot pressure. Furthermore, the control valve is located within the distributor.
US 5 836 231 A shows a radial piston motor with switchable displacement volumes, wherein a first and a second control valve is used to switch the displacement volumes, wherein two or more displacement volumes are possible.
The aim of the invention is to provide a multi piston machine with at least three switchable non-zero displacement volumes. The multi piston machine should have a high energy efficiency. It should be compact in size so that it can be integrated into a wheel of a vehicle. The torque ripple should be low. The manufacturing of the multi piston machine should be easy and cost effective.
According to claim 1 the multi piston machine is switchable between at least three non-zero displacement volumes by means of a first and a second control valve, wherein the first and the second control valve are connected to the first and the second working port respectively, wherein the first to fourth fluid chambers are annular with respect to the axis of rotation, being arranged distributed along the axis of rotation, wherein the first control valve is arranged radially inside the first to fourth fluid chambers, wherein the first control valve is fluidically connected to the second and the third fluid chamber, wherein second control valve is arranged radially outside the first to fourth fluid chambers, wherein the second control valve is fluidically connected to the first and the fourth fluid chamber, wherein the first fluid chamber is located closer to the second control surface than the second to fourth fluid chambers. With this configuration all fluid connections (No. 82 in Fig. 3 and 4) between a second control opening and a corresponding first to fourth fluid chamber are located radially inside an inner diameter of the annular first fluid chamber. At the first fluid chamber it is typically not possible to have a further fluid channel between two adjacent of the named fluid connections, because there is not enough space. With the claimed configuration the first fluid chamber is only connected to the second control valve, which is located outside the distributor of the multi piston machine. This connection could be established without passing between two neighboring straight sections 82 shown in Figs. 3 and 4. Without this provision it would not be possible to provide a central first control valve to obtain a compact multi piston machine.
Preferably, the first and the fourth fluid chamber are each connected to the same number of second control openings. Preferably, the second and the third fluid chamber are each connected to the same number of second control openings.
Preferably, the first control openings are located equally distributed along the first circle, wherein most preferably, they are identical to each other. Preferably, the second control openings are located, at least nearly, equally distributed along the second circle, wherein most preferably, they are, at least nearly, identical to each other. It is possible the reduce pressure peaks by slightly offsetting the second control openings from the ideal location or by providing somewhat different sized second control openings.
Preferably, the first and the second circle have the same diameter. Preferably, the first control valve is permanently connected to the second and the third fluid chamber.
Preferably, the first control surface is rotationally symmetrical with respect to the axis of rotation. Most preferably, the first control surface is flat and perpendicular to the axis of rotation. Preferably, the multi piston machine is configured as a radial piston motor, i.e., the pistons move radially with respect to the axis of rotation. Preferably, the cam surface is provided by a separate cam ring or a separate second casing part which surrounds the the rotor.
The displacement volume of the multi piston machine is the volume of pressure fluid which is fed through the multi piston machine during one revolution of the rotor. The maximum displacement volume is equal to the sum of the displacement volumes of each individual piston. Preferably, the pressure fluid is a liquid, wherein most preferably, the pressure fluid is hydraulic oil.
Preferably the first fluid chamber is located closer to the second control surface than the fifth to seventh fluid chambers explained below.
Further improvements of the invention are indicated in the dependent claims.
Preferably, the casing comprises a distributor and a first casing part, wherein the distributor has an outer circumferential surface which is rotationally symmetrical with respect to the axis of rotation, wherein the second control openings are located at the distributor, wherein the named outer circumferential surface delimits the first and the fourth fluid chamber in sections, wherein the second and the third fluid chamber are located completely inside the distributor. The corresponding distributor has a small length measured along the axis of rotation. This is especially relevant when the sixth and the seventh fluid chamber explained below are present. Preferably all second control openings are located at the distributor.
Preferably, a spool of the first control valve is received in the distributor in a linear moveable manner, wherein the second and the third fluid chamber are delimited by the named spool and the distributor, such that the second and the third fluid chamber are each part of an orifice which is adjustable by movement of the named spool. The corresponding distributor is very compact in size. Typically spool valves have annular grooves which are part of orifices which are adjustable by movement of the spool. Some of these annular grooves are used to provide the second and the third fluid chamber. Therefore, no further space is required to provide the second and the third fluid chamber.
Preferably, the outer circumferential surface delimits an annular fifth fluid chamber in sections, wherein the first and the second control valve are fluidically connected via the fifth fluid chamber. The fifth annular fluid chamber is preferably used to provide a free-wheeling switching position of the first and the second control valve in which the first and the second working port are short-circuited via the fifth fluid chamber.
Preferably, the first, the fourth and the fifth fluid chamber are arranged in a row along the axis of rotation in the named order. With this configuration the distance between the fifth fluid chamber and the first control valve, namely the fifth annular groove, is very short. It is easy to provide a corresponding fluid connection within the space limited distributor.
Preferably, the outer circumferential surface delimits an annular sixth fluid chamber in sections, wherein the sixth fluid chamber is fluidically connected to the first and the second control valve and the first working port. Preferably the named fluid connections are permanent. The main purpose of the sixth fluid chamber is to provide a fluid connection between the central first control valve and the first working port. This leads to an increased length of the distributor along the axis of rotation. This increase in length is preferably compensated by the configuration according to claims 2 and/or 3.
Preferably, the sixth fluid chamber is located between the first and the fourth fluid chamber. With this configuration the distance between the sixth fluid chamber and the first control valve, namely the first annular groove, is very short. It is easy to provide a corresponding fluid connection within the space limited distributor.
Preferably, the outer circumferential surface delimits an annular seventh fluid chamber in sections, wherein the seventh fluid chamber is fluidically connected to the first and the second control valve and the second working port. Preferably the named fluid connections are permanent. The main purpose of the seventh fluid chamber is to provide a fluid connection between the central first control valve and the second working port. This leads to an increased length of the distributor along the axis of rotation. This increase in length is preferably compensated by the configuration according to claims 2 and/or 3.
Preferably, the seventh fluid chamber is located between the fourth and the fifth fluid chamber. With this configuration the distance between the seventh fluid chamber and the first control valve, namely the fourth annular groove, is very short. It is easy to provide a corresponding fluid connection within the space limited distributor.
Preferably, each fluid connection between a second control opening and a corresponding first to fourth fluid chamber comprises a straight section which is parallel to the axis of rotation. The corresponding fluid connections have a low flow resistance and are easy to manufacture. On the other hand, they are located very close to each other, wherein the resulting problems are solved by the features of claim 1.
It goes without saying that the features mentioned above and those which are still to be explained below can be used not only in the combination indicated but also in other combinations or in independent form without departing from the scope of the present invention.
The invention is explained in more detail below with reference to the accompanying drawings. It shows:

Fig. 1: a perspective view of an inventive multi piston machine;
Fig. 2: a perspective view of the rotor;
Fig. 3: a perspective sectional view of the distributor;
Fig. 4: a schematic diagram comprising the pistons, the first and second control openings and the first to fourth fluid chamber;
Fig. 5: a schematic comprising the first and the second control valve, the first to seventh fluid chamber and the first and the second working port; and
Fig. 6: a partial section of the multi piston machine showing the first and the second control valve.

Fig. 1 shows a perspective view of an inventive multi piston machine 10. The multi piston machine 10 has a casing 60 comprising a first, a second, a third and a fourth casing part 61; 62; 63; 64, which together enclose all components of the multi piston machine 10 in a fluid tight manner. The first, the second and the third casing part 61; 62; 63 are fixed to each other. Preferably, the second casing part 62 has a first flange 65, which can by connected to a frame of a vehicle for example. The fourth casing part 64 is rotatable about an axis of rotation 13 with respect to the remaining casing 61; 62; 63. It has a second flange 66, which can be connected to a wheel of the named vehicle for example.
The cup shaped first casing part 61 holds the distributor (no. 30 in Fig. 3) and the second control valve 42. The first and the second working port 11; 12 and the first and the second control port 43; 44 are located at the first casing part 61.
The second casing part 62 surrounds the rotor (no. 70 in Fig. 2) in a ring-shaped manner. The inner circumferential surface of the second casing part 62 extents along the axis of rotation 13 with a constant cross section, wherein it forms the cam surface (no. 21 in Fig. 4).
The third casing part 63 surrounds a disc brake, which is known from EP 2 841 763 B1 for example. The fourth casing part 64 is fixed to the rotor (no. 70 in Fig. 2), via a splined shaft which is formed by the fourth casing part 64. The named shaft is supported by the third casing part 63 via roller bearings.
Fig. 2 shows a perspective view of the rotor 70. The rotor 70 at hand has eighteen pistons 1.1 - 1.18. The reference numerals 1.1 - 1.18 are assigned in numerical order around the rotor 70. The pistons 1.1 - 1.18 are movable radially with respect to axis of rotation 13, such that the axis of movement intersects axis of rotation 13 at 90°. It should be noted that the invention is not restricted to this angle. The axis of movement of the pistons 1.1 - 1.18 could also be parallel to the axis of rotation 13 for example.
All pistons 1.1 - 1.18 are shown in their most inward position. During operation the pistons 1.1 - 1.18 stick out of the rotor 70 such that they contact the cam surface (no. 21 in Fig. 4) with a roller 74. The roller 74 is held rotatably in the remaining piston 1.1 - 1.18 via a hydrostatic bearing such that it can rotate with low friction despite the high forces acting on the pistons 1.1 - 1.18. All pistons 1.1 - 1.18 are configured identically.
The rotor 70 has a planar first control surface 71, which is perpendicular to the axis of rotation 13. On the first control surface 71 there is a first control opening 2.1 - 2.18 for each piston 1.1 - 1.18 respectively. The numbering (number after the point) of first openings 2.1 - 2.18 is identical to the numbering of the pistons 1.1 - 1.18. This means first control opening 2.1 is connected to the cylinder (no. 73 in Fig. 4) of piston 1.1. The first control openings 2.1 - 2.18 are equally distributed along a first circle 72 whose center is defined by the axis of rotation 13. All first control openings 2.1 - 2.18 are identical to each other, wherein they are circular.
The rotor 70 has a splined bore 75 via which it is connected to the fourth casing part (no. 64 in Fig. 1) in a rotationally fixed manner.
Fig. 3 shows a perspective sectional view of the distributor 30. The section plane contains the axis of rotation 13. The distributor 30 is a one-piece part providing the second control surface 80 and the first to seventh fluid chamber 31 - 37. The planar second control surface 80 is perpendicular to the axis of rotation 13. It has fourteen second control openings 3.1 - 3.14 which are nearly equally distributed along a second circle 81 in numerical order. The center of the second circle 81 is defined by the axis of rotation 13, wherein its diameter is equal to the diameter of the first circle (no. 72 in Fig. 2). The second control openings 3.1 - 3.14 are nearly identical to each other, wherein they are formed like an oblong hole which extends in radial direction.
The distributer 30 has an outer circumferential surface 39 which rotationally symmetric with respect to the axis of rotation 13 and which is adapted to the first casing part (no. 61 in Fig. 1) in a fluid tight manner. The outer circumferential surface 39 delimits the first, the sixth, the fourth, the seventh and the fifth annular fluid chamber 31; 36; 34; 37; 35 in sections each.
The hydraulic pressure in the fluid chambers 31; 36; 34; 37; 35 at the outer circumferential surface 39 urges the distributer 30 in the direction of the axis of rotation 13, such that the second control surface 80 abuts against the first control surface (no. 71 in Fig. 1) in a fluid tight manner. During one revolution of the rotor each first control opening overlaps each second control opening 3.1 - 3.14 in at least in one rotational position of the rotor.
The first, the sixth, the fourth, the seventh and the fifth annular fluid chamber 31; 36; 34; 37; 35 are for formed by annular grooves at the outer circumferential surface 39 of the distributor 30, which are arranged in a row along the axis rotation 13 in the named order.
The connection between the first to fourth fluid chamber 31 - 34 with the second control openings 3.1 - 3.14 will be explained with reference to Fig. 4 below. These permanent connections are formed by channels inside the distributor 30, which were made during the casting of the blank distributor. Each of these connections has a straight section 82 which is parallel to the axis rotation 13. At the leftmost side of the distributor these straight sections 82 are very close to each other such that no further channel can pass between two neighboring straight sections 82. Therefore, the first fluid chamber 31 which is closest to the second control surface 80 is fluidically connected to the second control valve which is located outside of the distributor. The sixth fluid chamber is located next to the first fluid chamber 31 at the outer circumferential surface 39 of the distributor 30. At this location the straight section 83 is no longer present. The corresponding space can be used for a channel 84 connecting the first control valve (at no. 90) and the sixth fluid chamber 36.
The fifth fluid chamber 35 provides a fluid connection between the first and the second control valve, which is marked in Fig. 5 with no. 35.
At the center of the distributor 30 there is a bore for the spool of the first control valve (no. 41 in Fig. 5). The bore 90 is cylindrical with respect to the axis of rotation 13. The bore 90 has a first, a second, a third, a fourth and a fifth annular groove 91; 92; 93; 94; 95 which are located in a row along the axis of rotation 13 in the named order. The first annular groove 91 is permanently connected to the sixth fluid chamber 36 which is permanently connected to the first working port. In Fig. 5 the location of the sixth fluid chamber is marked with no. 36.
The second annular groove 92 delimits the second fluid chamber 32 in part. It has two purposes. Firstly it is part of an orifice, which is adjustable by a movement of the spool of the first control valve. Secondly as part of the second fluid chamber 32 it provides a connection 85 to at least one associated second control opening 3.1 - 3.14, wherein according to Fig. 4 three such connections are provided.
The third annular groove 93 delimits the third fluid chamber 33 in part. It has two purposes. Firstly it as part of an orifice, which is adjustable by a movement of the spool of the first control valve. Secondly as part of the third fluid chamber 33 it provides a connection 86 to at least one associated second control opening 3.1 - 3.14, wherein according to Fig. 4 three such connections are provided.
The fourth annular groove 94 is permanently connected to the seventh annular fluid chamber 37, which is permanently connected the second working port. In Fig. 5 the location of the seventh fluid chamber is marked with no. 37.
The fifth annular groove 95 is permanently connected to the fifth fluid chamber 35, which provides a connection to the second control valve.
Fig. 4 shows a schematic diagram comprising the pistons 1.1 - 1.18, the first and second control openings 2.1 - 2-18; 3.1 - 3.14 and the first to fourth fluid chamber 31; 32; 33; 34. For sake of clarity some of the reference numerals 1.1 - 1.18; 2.1 - 2.18; 3.1 - 3.14 were missed out. In all three cases there is a consecutive numbering, which ascends from left to right in Fig. 4.
The pistons 1.1 - 1.18 are equally distributed around the axis of rotation (no. 13 in Fig. 2), wherein they are shown in an unfolded way in Fig. 4. The cam surface 21, the rotor 70 and the distributor 30 are shown correspondingly. The the two dash-dot lines 15 refer to the same circumferential position with respect to the axis of rotation (no. 13 in Fig. 2, namely the center of piston 1.18.
The cam surface 21 on the inner circumference of the second casing part (no. 62 in Fig. 1) has seven lobes, wherein it is basically sinus shaped. The fluid pressures in the cylinders 73 urges the moveable pistons 1.1 - 1.18 against the cam surface 21 such that they follow the cam surface 21 when the rotor 70 rotates. In consequence during one rotation of the rotor 70 each piston 1.1 - 1.18 executes seven strokes.
The distributor 30 has fourteen second control control openings 3.1 - 3.14, i.e., two for each lobe of the cam surface 21. The rotational position of the distributor 30 relative to the cam surface 21 is fixed by a notch 38 in the distributor 30 which engages with a cylindrical pin fixed in the first casing part (no. 61 in Fig. 1), such that each dead center (maximum or minimum) of the cam surface 21 is located between two neighboring second control openings 3.1 - 3.14.
The rotor 70 has eighteen pistons 1.1 - 1.18 which are accommodated in a respective cylinder 73 of the rotor 70 so that they can move linearly. Each piston 1.1 - 1.18 contacts the cam surface 21 via a roller (no. 74 in Fig. 2) which is not shown in Fig. 4.
Each cylinder 73 has as a respective first control opening 2.1 - 2.18, wherein each first control opening 2.1 - 2.18 overlaps each second control opening 3.1 - 3.14 during one rotation of the rotor 70.
Below no. 30 in Fig. 4 the internal connections of the distributor are shown, which are selected to provide three switchable non-zero displacement volumes. Since the first number of pistons 1.1 - 1.18 and the third number of second control openings 3.1 - 3.14 have number two as a common prime factor there are pairs of pistons which have a 180° phase relation. For instance, pistons 1.2 and 1.11 show a phase relation of 180°. In theory it is possible to short circuit such a pair of pistons so that it does not contribute to the overall displacement volume of the multi piston machine, wherein no pressure peaks are produced. This is the basic working principle of US 6 050 173 A . But exactly this option is not used with the present invention. There is no position of the first and second control valve (no. 41; 42 in Fig. 5) which results in such a short circuit of the named pair of pistons 1.2/1.11, i.e., in a short circuit between the first and third fluid chamber 31; 33 in the rotor position shown in Fig. 4. Instead, the shown connections are used. Namely the first fluid chamber 31 is permanently connected to the second control openings 3.2; 3.4; 3.10; 3.12.
There is a first and second group of second control openings A; B, wherein neighboring second control openings 3.1 - 3.14 belong to a different first or second group A; B. The first fluid chamber 31 is permanently connected to four second control openings 3.2; 3.4; 3.10. 3.12 belonging to the first group A. The second fluid chamber 32 is permanently connected to three second control openings 3.6; 3.8; 3.14 belonging to the first group A. The third fluid chamber 33 is permanently connected to three second control openings 3.1; 3.7; 3.9 belonging to the second group B. The fourth fluid chamber 34 is permanently connected to four second control openings 3.3; 3.5; 3.11; 3.13 belonging to second group B.
It should be noted that the configuration according to Fig. 4 is a preferred embodiment wherein other configurations are possible. The configuration according to Fig. 4 gives a good compromise between a low number of pistons 1.1 - 1.18 and a low torque ripple.
Fig. 5 shows a schematic comprising the first and the second control valve 41; 42, the first to seventh fluid chamber 31 - 37 and the first and the second working port 11; 12. The first and the second control valve 41; 42 and the first and the second auxiliary valve 45; 56 are preferably configured as spool valves respectively. The first control valve 41; has a first and a second position 51; 52, wherein the second control valve 42 has a third and a fourth position 53; 54. In Fig. 5 the first and third positions 51; 53 are active such that all second control openings belonging to group A are connected to the first port 11, wherein all second control openings belonging to group B are connected to the second working port 12. Namely the first control valve 41 connects the first working port 11 with the second fluid chamber 32 and the second working port 12 with the third fluid chamber 33. The second control valve 42 connects the first working port 11 with the first fluid chamber 31 and the second working port 12 with the fourth fluid chamber 34. The fifth fluid chamber 35 is not used in this switching position, in which the multi piston machine works with the maximum displacement volume.
The second to maximum displacement volume is an active, when the first control valve 41 is in the second position 52, wherein the second control valve 42 is in the third position 53. Then the first working port 11 is only connected to the first fluid chamber 31, wherein the second working port 12 is only connected to the fourth fluid chamber 34 wherein both connections are provided by the second control valve 42. The first control valve 41 provides a direct connection between the second and the third fluid chamber 32; 33 via its first short circuit connection 55. Consequently, the second control openings 3.1; 3.6; 3.7; 3.8; 3.9; 3.14 are connected to each other. In this state eight of the fourteen second control openings contribute to the net displacement volume so that the net displacement volume is 8/14 of the maximum displacement volume.
The third to maximum displacement volume is an active, when the first control valve 41 is in the first position 51, wherein the second control valve 42 is in the fourth position 54. Then the first working port 11 is only connected to the second fluid chamber 32, wherein the second working port 12 is only connected to the third fluid chamber 33 wherein both connections are provided by the first control valve 41. The second control valve 42 provides a direct connection between the first and the fourth fluid chamber 31; 34 via its second short circuit connection 56. Consequently, the second control openings 3.2; 3.3; 3.4;3.5; 3.10; 3.11; 3.12; 3.13 are connected to each other. In this state six of the fourteen second control openings contribute to the net displacement volume so that the net displacement volume is 6/14 of the maximum displacement volume.
When first control valve 41 is switch into its second position 52 and the second control valve 42 is switched into its fourth position 54 the multi piston machine is in a free-wheeling state. There is a direct connection between the first and the second working 11; 12 ports via the fifth fluid chamber 35. Furthermore, the first to fourth fluid chamber 31 - 34 are short circuited to each other. When the multi piston machine drives an associated wheel of a vehicle, the wheel can be turned with low resistance, wherein fluid pressure at the first or second working port 11; 12 does not drive the vehicle.
At the first control valve 41 which is located inside the distributor (no. 30 in Fig. 3) the first to fifth annular grooves 91; 92; 93; 94; 95 shown in Fig. 3 are marked.
Fig. 6 show a partial section of the multi piston machine showing the first and the second control valve 41; 42. The spool 48 of the first control valve 41 is accommodated in the central bore 90 of the distributor 30 in a linearly moveable manner. It is urged into the shown first position (no. 51 in Fig. 4) by a spring 47. The first control port is permanently connected to the chamber marked with no. 43. The corresponding pressure acts on the spool 48 and on the first auxiliary valve 45.
The spool 49 of the second control valve 42 is accommodated in the first casing part 61 in a linearly movable manner, i.e., outside the distributor 30. It is urged into the shown third position (no. 53 in Fig. 4) by a spring 47. The second control port is permanently connected to the chamber marked with no. 44. The corresponding pressure acts on the spool 49 and on the second auxiliary valve 46.
The spools 48 and 49 including the auxiliary valves 45; 46 are configured identical to each other.

Reference Numerals

A: first group of second control openings
B: second group of second control openings

1.1: piston

1.18: piston

2.1: first control opening

2.18: first control opening

3.1: second control opening

3.14: second control opening

10: multi piston machine
11: first working port
12: second working port
13: axis of rotation
14: angle of rotation
15: dash-dot line

21: cam surface
22: lobe
23: cam ring
24: dead center
25: dwell section
30: distributor
31: first fluid chamber
32: second fluid chamber
33: third fluid chamber
34: fourth fluid chamber
35: fifth fluid chamber
36: sixth fluid chamber
37: seventh fluid chamber
38: notch (alignment cam surface)
39: outer circumferential surface

41: first control valve
42: second control valve
43: first control port
44: second control port
45: first auxiliary valve
46: second auxiliary valve
47: spring
48: spool of the first control valve
49: spool of the second control valve

51: first position
52: second position
53: third position
54: fourth position
55: first short circuit connection
56: second short circuit connection

60: casing
61: first casing part
62: second casing part (cam ring)
63: third casing part
64: fourth casing part
65: first flange
66: second flange

70: rotor
71: first control surface
72: first circle
73: cylinder
74: roller
75: splined bore

80: second control surface
81: second circle
82: straight section
83: straight section connected to the first fluid chamber
84: channel
85: connection between second fluid chamber and corresponding second control opening
86: connection between third fluid chamber and corresponding second control opening

90: bore for the spool of first control valve
91: first annular groove
92: second annular groove
93: third annular groove
94: fourth annular groove
95: fifth annular groove

Claims

Multi piston machine (10) with a rotor (70), which is located within a casing (60) and which is rotatable about an axis of rotation (13), wherein the casing (60) has a first and second working port (11; 12), wherein a first number of pistons (1.1 - 1.18) are received in the rotor (70) in a linearly movable manner, wherein the pistons (1.1 - 1.18) are able to contact a cam surface (21) of the casing (60), which has a second number of lobes (22), such that the number of strokes of a single piston (1.1 - 1.18) during one revolution of the rotor (70) equals the second number, wherein each piston (1.1 - 1.18) has one associated first control opening (2.1 - 2.18) at a first control surface (71) of the rotor (70), wherein the first control openings (2.1 - 2.18) are located along a first circle (72) whose center is defined by the axis of rotation (13), wherein the the casing (60) has a second control surface (80) which abuts against the first control surface (71), wherein the the second control surface (80) has a third number of second control openings (3.1 - 3.14), which are located along a second circle (81), whose center is defined by the axis of rotation (13), wherein each first control opening (2.1 - 2.18) is able to overlap each of the second openings (3.1 - 3.14) in at least one rotational position of the rotor (70) respectively, wherein there is a first, a second, a third and fourth fluid chamber (31; 32; 33; 34), wherein each second control opening (3.1 - 3.14) is permanently connected to a single one of the first to fourth fluid chamber (31; 32; 33; 34),
characterized in that the multi piston machine (10) is switchable between at least three non-zero displacement volumes by means of a first and a second control valve (41; 42), wherein the first and the second control valve (41; 42) are connected to the first and the second working (11; 12) port respectively, wherein the first to fourth fluid chambers (31 - 34) are annular with respect to the axis of rotation (13), being arranged distributed along the axis of rotation (13), wherein the first control valve (41) is arranged radially inside the first to fourth fluid chambers (31 - 34), wherein the first control valve (41) is fluidically connected to the second and the third fluid chamber (32; 33), wherein second control valve (42) is arranged radially outside the first to fourth fluid chambers (31 - 34), wherein the second control valve (42) is fluidically connected to the first and the fourth fluid chamber (31; 34), wherein the first chamber (31) is located closer to the second control surface (80) than the second to fourth fluid chambers (32 - 34).
Multi piston machine (10) according to claim 1,
wherein the casing comprises (60) a distributor (30) and a first casing part (61), wherein the distributor (30) has an outer circumferential surface (39) which is rotationally symmetrical with respect to the axis of rotation (13), wherein the second control openings (3.1 - 3.14) are located at the distributor (30), wherein the named outer circumferential surface (39) delimits the first and the fourth fluid chamber (31; 34) in sections, wherein the second and the third fluid chamber (32; 33) are located completely inside the distributor (30).
Multi piston machine (10) according to any of the preceding claims,
wherein a spool (48) of the first control valve (41) is received in the distributor (30) in a linear moveable manner, wherein the second and the third fluid chamber (32; 33) are delimited by the named spool (48) and the distributor (30), such that the second and the third fluid chamber (32; 33) are each part of an orifice which is adjustable by movement of the named spool (48).
Multi piston machine (10) according to claim 2 or 3,
wherein the outer circumferential surface (39) delimits an annular fifth fluid chamber (35) in sections, wherein the first and the second control valve (41; 42) are fluidically connected via the fifth fluid chamber (35).
Multi piston machine (10) according to claim 4,
wherein the first, the fourth and the fifth fluid chamber (31; 32; 35) are arranged in a row along the axis of rotation (13) in the named order.
Multi piston machine (10) according to any of the claims 2 to 5,
wherein the outer circumferential surface (39) delimits an annular sixth fluid chamber (36) in sections, wherein the sixth fluid chamber (36) is fluidically connected to the first and the second control valve (41; 42) and the first working port.
Multi piston machine (10) according to claim 6, referenced back to claim 5,
wherein the sixth fluid chamber (36) is located between the first and the fourth fluid chamber (31; 34).
Multi piston machine (10) according to any of the claims 2 to 7,
wherein the outer circumferential surface (39) delimits an annular seventh fluid chamber (37) in sections, wherein the seventh fluid chamber (37) is fluidically connected to the first and the second control valve (41; 42) and the second working port (12).
Multi piston machine (10) according to claim 8, referenced back to claim 5,
wherein the seventh fluid chamber (36) is located between the fourth and the fifth fluid chamber (34; 35).
Multi piston machine (10) according to any of the preceding claims,
wherein each fluid connection between a second control opening (3.1 - 3.14) and a corresponding first to fourth fluid chamber (31 - 34) comprises a straight section (82) which is parallel to the axis of rotation (13).