EP4345284B1 - Machine à pistons multiples avec relation constante entre le volume de fluide et l'angle de rotation dans chaque position de rotation - Google Patents

Machine à pistons multiples avec relation constante entre le volume de fluide et l'angle de rotation dans chaque position de rotation

Info

Publication number
EP4345284B1
EP4345284B1 EP22198761.3A EP22198761A EP4345284B1 EP 4345284 B1 EP4345284 B1 EP 4345284B1 EP 22198761 A EP22198761 A EP 22198761A EP 4345284 B1 EP4345284 B1 EP 4345284B1
Authority
EP
European Patent Office
Prior art keywords
rotor
piston machine
sections
rotation
pistons
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP22198761.3A
Other languages
German (de)
English (en)
Other versions
EP4345284A1 (fr
Inventor
David Hare
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP22198761.3A priority Critical patent/EP4345284B1/fr
Publication of EP4345284A1 publication Critical patent/EP4345284A1/fr
Application granted granted Critical
Publication of EP4345284B1 publication Critical patent/EP4345284B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
    • F03C1/247—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders with cylinders in star- or fan-arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0409—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
    • F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks

Definitions

  • the invention concerns a multi piston machine with a rotor, which is located within a casing and which is rotatable about an axis of rotation, wherein the casing has a first and second working port, wherein a first number of pistons are received in the rotor in a linearly movable manner, such that they define a cylinder with variable volume respectively, wherein the pistons are able to contact a cam surface of the casing, which has a second number of lobes, such that the number of strokes of a single piston during one revolution of the rotor equals the second number, wherein the cam surface defines a second number of first sections and a second number of second sections, which are arranged alternately with respect to a rotation of the rotor, wherein each piston contacts either a first or a second section in each angular position of the rotor, wherein the first sections are formed such that a piston contacting the first section is constantly at a position defining a smallest volume of the corresponding cylinder, wherein there
  • US 4 807 519 shows a corresponding multi piston machine, which is configured as a radial piston motor.
  • the number of switching positions of the valve assembly is two.
  • the first number of pistons and the second number of lobes is typically selected such that the first and the second number have a common factor, which is different from one.
  • the named factor may be three. Due to this common factor the symmetry in the movement of the pistons can be exploited to provide a constant relationship between the volume of pressure fluid provided at the first working port and the rotation angle of the rotor in each rotational position of the rotor. This common factor heavily restricts the possible selections for the first and second number.
  • all first sections can be configured to have an angular extent of zero, i.e. there are only single points within the rotation of the rotor, where the cylinders have their smallest volume.
  • the present invention has the advantage that the first and the second number can be selected arbitrarily. Nevertheless the named constant relationship between the amount of pressure fluid provided at the first working port and the rotation angle of the rotor in each rotational position of the rotor can be achieved.
  • the present invention is used with a multi piston machine having at least three switching positions of the valve assembly providing a non-zero displacement volume each, wherein the named displacement volumes are different from each other.
  • a set of reference positions of the rotor is defined for each of the named switching positions of the valve assembly respectively, wherein at each reference position a piston connected to the first working port enters a second section, due to a rotation of the rotor, wherein an angular extent of at least one first section with respect to the axis of rotation is greater than zero, such that in at least one switching position of the valve assembly the pistons contributing to the displacement volume of the multi piston machine pass the associated reference positions at essentially constant angular intervals during a complete revolution of the rotor.
  • the rotation of the rotor is preferably caused by a pressure at the first working port which is higher than the pressure at the second working port. If the radial piston machine is configured as a pump the rotation of the rotor is caused by drive motor which is in rotational driving engagement with the rotor, wherein the pressure fluid preferably flows from the second working port (lower pressure) through the rotor to the first working port (higher pressure).
  • the named angular intervals are exactly equal among each other.
  • the multi piston machine is a radial piston machine, i.e. the direction of movement of the pistons is perpendicular to the axis of rotation.
  • the multi piston machine is used with a pressure fluid.
  • the pressure fluid is a liquid and most preferably hydraulic oil.
  • an angular extent of at least two first sections with respect to the axis of rotation is greater than zero and different from each other.
  • the named angular interval is essentially constant for all switching positions of the valve assembly providing a non-zero displacement volume of the multi piston machine.
  • the first and the second number have no common factor besides one.
  • the angular extent of at least two second sections is equal to each other. Most Preferably, the angular extent of all second sections is equal to each other.
  • At least two second sections are formed identical to each other. Most preferably, at all second sections are formed identical to each other. With this configuration the named constant relationship between the volume of pressure fluid provided at the first working port and the rotation angle of the rotor in each rotational position of the rotor can be achieved.
  • At least two first sections having the same non-zero angular extent.
  • the maximum angular extent of all first sections is at least 5°. Most preferably, the maximum angular extent of all first sections at least 10°.
  • the second number of lobes is split into a third and fourth number of lobes, wherein the third number is the number of lobes on which cylinders are connected to the first or second working ports and wherein the fourth number is the number of lobes on which cylinders are in a short circuit connection with each other, wherein the third and fourth number have no common factor besides one.
  • the third number is two, wherein the fourth number is three.
  • the third number is three, wherein the fourth number is two.
  • the first switching position full displacement
  • the cam surface is configured mirror-symmetrical with respect to an axis of symmetry. If the inventive configuration is present for one direction of rotation of the rotor, it is also present for the opposite direction of the rotor, if the name mirror symmetry is present.
  • the axis of symmetry intersects the axis of rotation perpendicularly.
  • Fig. 1 a perspective view of a multiple piston machine 10 according to a first embodiment of the invention.
  • the first embodiment has a fist number of eighteen pistons and second number of seven lobes.
  • the valve assembly has four switching positions, wherein three of the them correspond to non-zero displacement volumes.
  • the fourth switching position is a free wheeling position, which is not relevant for the invention at hand.
  • the multiple 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 multiple 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.
  • the third casing part 63 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 first and the second control valve 41; 42, wherein no. 41; 42 actually point to the section of the casing 60, which covers a spool of the first or second control valve 41; 42 respectively.
  • 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 third casing part 63 surrounds the rotor (no. 70 in Fig. 2 ) in a ring shaped manner.
  • the inner circumferential surface of the third casing part 63 extents along the axis of rotation 13 with a constant cross section, wherein it forms the cam surface (no. 21 in Fig. 4 ).
  • the second casing part 62 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 second casing part 62 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 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 piston 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 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 are configured identically.
  • the rotor 70 has a even 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.
  • 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 open 2.1 is connected to the cylinder (no. 73 in Fig. 4 ) of piston 1.1.
  • the first control openings 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 50 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 view of the distributor 30.
  • the distributor 30 is a one-piece part providing the second control surface 36 and the first to fifth fluid chamber 31 - 35.
  • the even second control surface 36 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 37 in numerical order.
  • the center of the second circle 37 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 a oblong hole which extents in radial direction.
  • the distributer 30 has an outer surface 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 hydraulic pressure in the first to fifth fluid chamber 31 - 35 urges the distributer 30 in the direction of the axis of rotation 13, such that the second control surface 36 abuts against the first control surface (no. 71 in Fig. 1 ) in a fluid tight manner.
  • each first control opening overlaps each second control opening in at least in one rotational position of the rotor.
  • the first to fifth fluid chamber 31 - 35 are for formed by grooves on the circumferential surface of the distributor 30, which are arranged along the axis rotation 13 in numerical order.
  • the connection between the first to fourth fluid chamber 31 - 34 with the second control openings 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.
  • the fifth fluid chamber provides a fluid connection between the first and the second control valve, which is marked in Fig. 5 with no. 35.
  • the notch 38 prevents a rotation of the distributor 30 with respect to the axis of rotation 13.
  • a pin, which is held by the second casing part extents into the notch 38.
  • the notch is located between the second control openings 3.1 and 3.2.
  • 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.
  • 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 piston 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. Further details are explained with reference to Fig. 6 .
  • the fluid pressures in the cylinders 74 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 (see Fig. 3 too) which engages with a cylindrical pin fixed in the second casing part (no. 62 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 the 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.
  • first and second group of second control openings A; B wherein neighboring second control openings 2.1 - 2.14 belong to a different first or second group A; B.
  • the first fluid chamber 3.1 is permanently connected to three second control openings 3.6; 3.8; 3.14 belonging to the first group A.
  • the second fluid chamber 32 is permanently connected to four second control openings 3.2; 3.4; 3.10. 3.12 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.
  • Fig. 5 shows a schematic comprising the first and the second control valve 41; 42, the first to fifth fluid chamber 31 - 35 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 an a fourth position 53; 54.
  • 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.
  • first control valve 41 connects the first working port 11 with the first fluid chamber 31 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 second fluid chamber 32 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 a 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 second fluid chamber 32, 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 first and the third fluid chamber 31; 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.
  • the two pairs 3.1/3.8 and 3.8/3.14 provide an exact 180° phase shift.
  • the remaining pair 3.6/3.9 does not exactly provide a 180° phase shift, but nearly.
  • the first auxiliary auxiliary valve 45 provides a connection between the first short connection 55 and the first control port 43, when it is switched into its open position by a pressure in the first control port 43, which urges the first control valve 41 into is second position 52.
  • 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 a 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 first fluid chamber 31, 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 second and the fourth fluid chamber 32; 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.
  • the three pairs 3.3/3.10; 3.4/3.11 and 3.5/3.12 provide an exact 180° phase shift.
  • the remaining pair 3.2/3.13 does not exactly provide a 180° phase shift, but nearly.
  • the second auxiliary valve 46 provides a connection between the second short connection 46 and the second control port 44, when it is switched into its open position by a pressure in the second control port 44, which urges the second control valve 42 into its fourth position 54.
  • 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.
  • first control valve 41 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 an and the second working 11; 12 port 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.
  • Fig. 6 shows a first schematic view of the cam surface 21 and the pistons 1.1 - 1.12 of a second embodiment of the invention, wherein this view is directed to a second switching position of the valve assembly. Only the rollers (no. 74 in Fig. 2 ) of the pistons 1.1 - 1.12 are shown, because they define the contact between a piston 1.1 - 1.12 and the cam surface 21.
  • the second embodiment has a first number of twelve pistons 1.1 - 1.12 and a second number of five lobes 22.
  • the number first and second control openings is selected accordingly.
  • the first and the second number have no common factor besides one.
  • the corresponding valve assembly has four switching positions. In the first switching position all pistons 1.1 - 1.12 contribute to the displacement of the multi piston machine. In the second position only the pistons 1.1 - 1.12 contacting the two lobes marked with no. 83 contribute to the displacement of the multi piston machine, while the remaining pistons 1.1 - 1.12 contacting the remaining three lobes marked with no. 84 are short circuited. In the third switching position only the pistons 1.1 - 1.12 contacting the three lobes marked with no. 84 contribute to the displacement of the multi piston machine, while the remaining pistons 1.1 - 1.12 contacting the remaining two lobes marked with no. 83 are short circuited.
  • the fourth switching position position may be a free wheeling position in which all pistons 1.1 - 1.12 are short circuited.
  • the five second sections 82 of the cam surface 21 are configured identical to each other, wherein the have a sinusoidal shape as with a conventional multi piston machine.
  • the angular extent of the five second sections 82 is identical to each other, wherein the named angular extent equals to 67.5° for example.
  • the first sections 81 of the cam surface 21 are located at the angular positions of the pistons 1.1 - 1.12 where the corresponding cylinders (no. 80 in Fig. 4 ) have their smallest volume.
  • the angular extent of the first sections 81 differ from each other.
  • the fourth and the fifth copies 81d; 81d of the first section 81 have an angular extend of 0° as with a conventional multi piston machine.
  • the first and the third copies 81a; 81c of the first section 81 have an angular extend of 5° for example.
  • the second copy 81b of the first section 81 has an angular extend of 12.5°.
  • first to third copies 81a; 81b; 81c of the first section are configured cylindrical with respect to the axis of rotation 13.
  • the configuration of the second sections 81 is mirror symmetric with respect to an axis of symmetry 86.
  • the first group 83 of lobes is mirror symmetric with respect to the axis of symmetry 86.
  • the second group 84 of lobes is mirror symmetric with respect to the axis is of symmetry 86. Because of this symmetry, the machine works equally well in both opposite directions of rotation of the rotor.
  • first control openings 2.1 - 2.18 in Fig. 2
  • second control openings 3.1 - 3.14 in Fig. 3
  • first and second working port 11; 12 in Fig. 1
  • short circuit connection there is a direct relationship between the position of piston 1.1 - 1.12 with relation to the cam surface 21 and it's connection to the first and second working port (11; 12 in Fig. 1 ) or its short circuit connection.
  • Piston 1.12 is at a transition state from the first working port to the second working port.
  • Piston 1.4 is in a transition state from the second working port to the first working port. Since piston 1.4 is located within the second copy 81b of the first section 81, it does not contribute to the overall fluid flow of the multiple piston machine at the instance of time shown in Fig. 6 .
  • Piston 1.1 is also in a transition state from the second working port to the first working port.
  • Fig. 6 is directed to the second switching position, where the first group of lobes 83 defines the displacement volume of the multi piston machine. Therefore pistons 1.1; 1.7; 1.8; 1.11; 1.12 contribute to the displacement volume of the multi piston machine with the angular position of the rotor shown in Fig. 6 . They are connected to the first and second working port as described with reference to the first switching position above. The remaining pistons 1.2; 1.3; 1.4; 1.5; 1.6; 1.9; 1.10 are assigned to the second group of lobes 84 and are short circuited to each other, such that they do not contribute to fluid flow of the multi pistons machine.
  • one design goal is to have a constant relationship between the volume of fluid flowing into the first working port (higher pressure) and the resulting rotation angle of the rotor in every rotational position of the rotor.
  • this goal may be achieved by having some sort of symmetry which is based on a common factor between the first number of pistons and the second number of lobes. In Fig. 6 no such common factor is present. Therefore with the invention the named goal is achieved in the second switching position by setting the angular extent of the first sections 81 such that the first reference positions 91 are passed by a piston 1.1 - 1.12 at a constant interval of rotation.
  • the first reference positions 91 are at a position where a piston 1.1 - 1.12 connected to the first working port just enters a lobe 83 assigned to the first group (active lobe). In the second switching position there are two first reference positions 91a; 91b, since there are two lobes in the first group 83.
  • piston 1.1 is located exactly at the first reference position 91a.
  • the next piston which which will pass a first reference position 91 is piston 1.9.
  • piston 1.9 With 15° of rotor rotation along the direction 85 starting form the rotor position shown in Fig. 6 piston 1.9 will pass the first reference position 91b.
  • piston 1.2 With a further 15° of rotor rotation piston 1.2 will pass the first reference position 91a. Since the angular distance between two adjacent pistons 1.1 - 1.12 is 30° at this point the multi piston machine has the same configuration as shown in Fig. 6 but with the numbering of the pistons 1.1 - 1.12 shifted by one. Therefore the constant interval of 15° is present for a complete revolution of the rotor.
  • Fig. 7 shows a second schematic view which differs from Fig. 6 only in the angular position of the rotor, wherein this view is directed to the third switching position of the valve assembly.
  • the second group of lobes 84 defines the displacement volume of the multi piston machine. Therefore pistons 1.1; 1.4; 1.5; 1.8; 1.9; 1.10; 1.11; 1.12 contribute to the displacement volume of the multi piston machine with the angular position of the rotor shown in Fig. 7 .
  • the remaining pistons 1.2; 1.3; 1.6; 1.7 are assigned to the first group of lobes 83 and are short circuited to each other, such that they do not contribute to the fluid flow of the multi piston machine.
  • the second reference positions 92 are relevant for the design goal named above.
  • the second reference positions 92 are at a position where a piston 1.1 - 1.12 connected to the first working port (higher pressure) just enters a lobe 84 assigned to the second group (active lobe).
  • the third switching position there are three second reference positions 92a; 92b; 92c since there are three lobes in the second group 84.
  • piston 1.1 is located exactly at first reference position 92a.
  • the next piston which which will pass a second reference position 92 is piston 1.6.
  • piston 1.6 With 10° of rotor rotation along the direction 85 starting form the rotor position shown in Fig. 7 piston 1.6 will pass the second reference position 92c.
  • piston 1.11 With a further 10° of rotor rotation piston 1.11 will pass the second reference position 92b.
  • piston 1.2 With a further 10° of rotor rotation piston 1.2 will pass the second reference position 92a. Since the angular distance between two adjacent pistons 1.1 - 1.12 is 30° at this point the multi piston machine has the same configuration as shown in Fig. 7 but with the numbering of the pistons 1.1 - 1.12 shifted by one. Therefore the constant interval of 10° is present for a complete revolution of the rotor.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)

Claims (11)

  1. Machine multi-piston (10 ; 10') avec un rotor (70), qui est situé à l'intérieur d'un carter (60) et qui est rotatif autour d'un axe de rotation (13), dans laquelle le carter a des premier et second orifices de travail (11 ; 12), dans laquelle un premier nombre de pistons (1.1 - 1.18) sont reçus dans le rotor (70) de manière mobile linéairement, de manière telle qu'ils définissent un cylindre (80) avec un volume variable respectivement, dans laquelle les pistons (1.1 - 1.18) sont capables d'entrer en contact avec une surface à came (21) du carter (60), qui a un deuxième nombre de lobes (22), de manière telle que le nombre de courses d'un seul piston (1.1 - 1.18) durant une révolution du rotor (70) est égal au deuxième nombre,
    dans laquelle la surface à came (21) définit un deuxième nombre de premières sections (81) et un deuxième nombre de secondes sections (82), qui sont agencées en alternance par rapport à une rotation du rotor (70), dans laquelle chaque piston (1.1 - 1.18) entre en contact soit avec une première soit avec une seconde section (81 ; 82) dans chaque position angulaire du rotor (70), dans laquelle les premières sections (81) sont formées de manière telle qu'un piston entrant en contact avec la première section (81) est de façon constante à une position définissant un volume le plus petit du cylindre correspondant (80),
    dans laquelle il y a un ensemble soupape (40) et un distributeur (20), dans laquelle l'ensemble soupape (40) a au moins deux positions de commutation, dans laquelle l'ensemble soupape (40) et le distributeur (20) sont configurés de manière telle que chaque cylindre (80) est soit raccordé au premier orifice de travail (11), au second orifice de travail (12) soit à un raccordement à court-circuit (55 ; 56) à chaque position angulaire du rotor (70), dans laquelle le raccordement à court-circuit (55 ; 56) fournit un court-circuit entre au moins deux cylindres (80), dans laquelle le nombre de cylindres (80) ayant un raccordement à court-circuit (55 ; 56) est différent dans les différentes positions de commutation, caractérisée en ce qu'un jeu de positions de référence (91 ; 92) du rotor (70) est défini pour chacune des positions de commutation nommées de l'ensemble soupape (40) respectivement, dans laquelle, à chaque position de référence (91 ; 92), un piston (1.1 - 1.18) raccordé au premier orifice de travail (21) entre dans une seconde section (82), en raison d'une rotation du rotor (70),
    dans laquelle une étendue angulaire d'au moins une première section (81) par rapport à l'axe de rotation (13) est supérieure à zéro, de manière telle que, dans au moins une position de commutation de l'ensemble soupape (40), les pistons (1.1 - 1.18) contribuant au volume de cylindrée de la machine multi-piston (10 ; 10') passent par les positions de référence associées (91 ; 92) à des intervalles angulaires essentiellement constants durant une révolution complète du rotor (70).
  2. Machine multi-piston (10 ; 10') selon la revendication 1,
    dans laquelle une étendue angulaire d'au moins deux premières sections (81a ; 81b) par rapport à l'axe de rotation (13) est supérieure à zéro et différente par rapport à l'autre.
  3. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle l'intervalle angulaire nommé est essentiellement constant pour toutes les positions de commutation de l'ensemble soupape (40) fournissant un volume de cylindrée non zéro de la machine multi-piston (10 ; 10').
  4. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle les premier et deuxième nombres n'ont aucun facteur commun à part un.
  5. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle l'étendue angulaire d'au moins deux secondes sections (82) est égale à l'autre.
  6. Machine multi-piston (10 ; 10') selon la revendication 5,
    dans laquelle au moins deux secondes sections (82) sont formées de façon identique l'une à l'autre.
  7. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle il y a au moins deux premières sections (81a ; 81c) ayant la même étendue angulaire non zéro.
  8. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle il y a une et seulement une première section (81b) dont l'étendue angulaire est au moins deux fois plus large que la première section plus petite suivante (81a ; 81c).
  9. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle l'étendue angulaire maximum de toutes les premières sections (81) est d'au moins 5°, de préférence d'au moins 10°.
  10. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle, pour au moins une position de commutation de l'ensemble soupape (40), le deuxième nombre de lobes (22) est divisé en des troisième et quatrième nombres de lobes (83 ; 84), dans laquelle le troisième nombre est le nombre de lobes (22) sur lesquels des cylindres (80) sont raccordés au premier ou second orifice de travail (21 ; 22) et dans laquelle le quatrième nombre est le nombre de lobes sur lequel des cylindres (80) sont dans un raccordement à court-circuit les uns avec les autres, dans laquelle les troisième et quatrième nombres n'ont aucun facteur commun à part un.
  11. Machine multi-piston (10 ; 10') selon de quelconques des revendications précédentes,
    dans laquelle la surface à came (21) est configurée de façon symétrique en miroir par rapport à un axe de symétrie (86).
EP22198761.3A 2022-09-29 2022-09-29 Machine à pistons multiples avec relation constante entre le volume de fluide et l'angle de rotation dans chaque position de rotation Active EP4345284B1 (fr)

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EP22198761.3A EP4345284B1 (fr) 2022-09-29 2022-09-29 Machine à pistons multiples avec relation constante entre le volume de fluide et l'angle de rotation dans chaque position de rotation

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EP22198761.3A EP4345284B1 (fr) 2022-09-29 2022-09-29 Machine à pistons multiples avec relation constante entre le volume de fluide et l'angle de rotation dans chaque position de rotation

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Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2853552C3 (de) * 1978-12-12 1981-08-13 Rudolf 7031 Holzgerlingen Bock Hydraulischer Motor
DE3706460A1 (de) 1986-10-31 1988-09-08 Rexroth Mannesmann Gmbh Kolbenmaschine mit umschaltbarem hubraum
FR2661456B1 (fr) * 1990-04-26 1992-08-14 Poclain Hydraulics Sa Mecanisme a fluide sous pression, tel qu'un moteur ou une pompe hydraulique, a plusieurs cylindrees de fonctionnement.
JP3127842B2 (ja) 1996-11-01 2001-01-29 ダイキン工業株式会社 カムモータ装置
US9777573B2 (en) 2012-04-28 2017-10-03 Robert Bosch Gmbh Radial piston engine with brake
FR3038348B1 (fr) * 2015-07-01 2019-08-23 Poclain Hydraulics Industrie Machine hydraulique a pistons radiaux a distribution en harmonique
EP4102051A1 (fr) * 2021-06-07 2022-12-14 Robert Bosch GmbH Machine à pistons multiples comportant au moins trois volumes de déplacement commutables

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