EP3091230A1 - Machine a piston hydrostatique - Google Patents

Machine a piston hydrostatique Download PDF

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Publication number
EP3091230A1
EP3091230A1 EP16164342.4A EP16164342A EP3091230A1 EP 3091230 A1 EP3091230 A1 EP 3091230A1 EP 16164342 A EP16164342 A EP 16164342A EP 3091230 A1 EP3091230 A1 EP 3091230A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
working space
engine according
partial
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.)
Granted
Application number
EP16164342.4A
Other languages
German (de)
English (en)
Other versions
EP3091230B1 (fr
Inventor
Gottfried Hendrix
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
Publication of EP3091230A1 publication Critical patent/EP3091230A1/fr
Application granted granted Critical
Publication of EP3091230B1 publication Critical patent/EP3091230B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—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
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/18—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the effective cross-section of the working surface of the piston

Definitions

  • the invention relates to a hydrostatic piston volume adjustable in its stroke volume according to the preamble of patent claim 1.
  • piston machines are known in which subsets of their cylinders can be completely deactivated. This happens, for example, via valves that are assigned to the cylinders.
  • the cylinders to be deactivated are not connected alternately with the high-pressure side and the low-pressure side of the machine via the valves, but always with one of the two sides-usually with the low pressure side.
  • aspects of the symmetry of the remaining active cylinder must be considered because of a uniform as possible torque introduction at the periphery and the pulsation of the pressure medium.
  • each piston has an inner piston part and an outer piston part, which together define a working space of the associated cylinder.
  • the outer piston part can be hydraulically blocked and thus deactivated.
  • valves are provided for each piston, via which the pressure of a back space of the outer piston part can be changed. This results in a two-stage adjustment of the stroke volume of the piston engine.
  • a disadvantage of such reciprocating engines is that only one (outer) sub-piston can be activated and deactivated while the other (inner) sub-piston always remains active.
  • the object of the invention is to provide a piston engine in which all partial pistons can be activated and deactivated.
  • the claimed hydrostatic piston engine has at least one - preferably more - piston, which is guided in a respective associated cylinder.
  • Each piston has a first partial piston and a second partial piston which is relatively movable relative to the first partial piston.
  • each cylinder has a first working space and a second working space separated therefrom by the piston.
  • Each sub-piston limits a working area with an associated working space.
  • the first working space can be activated and deactivated via a first shut-off valve
  • the second working space can be activated and deactivated via a second shut-off valve.
  • each piston part of the piston can be activated and deactivated independently of the other sub-piston.
  • the inventive Piston engine is particularly suitable for pre-stressed closed circuits as well as in systems with a charge pump.
  • a continuously variable further machine pump or motor
  • the piston engine according to the invention is always operated in the stage that gives maximum efficiency of the transmission.
  • Preferred applications are a direct drive of the crank of a press with creep speed and rapid traverse, an extruder drive with variable speed, a wing-side engine of a wind turbine drive and a winch drive in marine technology.
  • the piston engine according to the invention is a rotationally symmetrical and concentric design of the cylinder and the piston, including its partial pistons.
  • the second partial piston can engage around the first partial piston.
  • the possibilities of variation of the stroke volume of the piston engine according to the invention are expanded if the piston has a third part piston which is relatively movable against the other part piston, and if the cylinder has a third working space which is separated from the other working spaces via the piston.
  • the third limited part piston with a third working surface the working space.
  • the third working space can be activated and deactivated via a third shut-off valve.
  • each of the three pistons of the piston can be activated and deactivated independently of the other piston part. Further such sub-pistons and work spaces are possible and increase the possible variations of the stroke volume of the piston engine according to the invention.
  • each shut-off valve being arranged between a working port of the piston engine which can be used as a feed or a branch to the several comparable work spaces of all cylinders.
  • a shut-off valve all allocated work spaces distributed around the circumference can be activated and deactivated, as a result of which a uniform torque introduction of the partial pistons on the circumference always takes place.
  • this work connection In order to be able to operate the piston machine according to the invention bidirectionally, it requires a further working connection which can be used as an inlet. Then also this work connection further branches are assigned, the number - as well as the number of the first-mentioned branches - that of the work spaces per cylinder corresponds. Each of these further branches - like the first-mentioned branches - connects the comparable working spaces of all cylinders. Respective further shut-off valves are arranged between the further working connection and each further branch, the number of which - like the number of the first-mentioned shut-off valves - corresponds to that of the partial pistons per cylinder. This results in a doubling of the branches and the shut-off valves with respect to the above-described embodiment.
  • the adjustment of the piston engine according to the invention is refined when the first working space facing first working surface of the first part piston has a size that does not correspond to the size of the second working space facing second working surface of the second part piston. Since only the smaller work surface or only the larger work surface or both work surfaces can be activated, there are three levels of adjustment of the stroke volume.
  • all (e.g., three) work surfaces be different in size. This further levels of adjustment of the stroke volume are given.
  • the piston has a piston base body which is movable in the cylinder and which is also movable relative to all partial pistons.
  • the piston main body is arranged substantially on the side facing away from the working surfaces of the partial piston.
  • the piston main body for guiding - similar to a conventional piston - fitting the inner circumference of the cylinder.
  • the piston main body has a total cross-sectional area corresponding to the sum of all work surfaces.
  • the piston main body can have a contact surface for each partial piston, via which the partial piston in the activated state transfers the force of the pressure medium in the working space from the working surface via the contact surface to the piston main body.
  • a rolling element or a roller may be mounted on the piston main body and roll over cams.
  • the KobengrundSuper has a mechanical coupling to the invention Kobenmaschine.
  • each contact surface opens a connected to a housing interior or a tank discharge channel.
  • This allows a relative movement of the piston main body relative to the associated deactivated partial piston, since pressure medium or air can flow into an enlarging intermediate space between the piston main body and the partial piston.
  • the first sub-piston may be used in sections to his leadership in a recess of the piston body.
  • the recess is preferably - like the entire piston with its sub-piston - rotationally symmetrical.
  • the second partial piston engages around the first partial piston, and if the third partial piston engages around the piston main body.
  • the first partial piston can be circular-cylindrical, while the second partial piston and the third partial piston are annular.
  • a check valve can be arranged simply in terms of device technology.
  • these check valves are arranged between the branch and each working space.
  • each working space may be provided a switching valve.
  • a switching valve When operating the piston engine always in one direction extends downstream of each cylinder another switching valve.
  • a bidirectionally operable Piston engine With a bidirectionally operable Piston engine is depending on the operating direction serves one of two different channels as an inlet and is arranged upstream, so that per working space in each of the two channels, a switching valve is needed.
  • Control slots may also be provided upstream and downstream of the work spaces in a control plate or manifold plate.
  • FIG. 1 shows a cylinder 1 with a guided therein piston 2, on which a rolling element 4 is mounted.
  • This arrangement is provided several times and evenly distributed on the circumference of a (not shown) rotor of the first embodiment of the radial piston machine according to the invention.
  • the pistons 2 are supported on the respective rolling elements 4 at a arranged on the outer circumference of the radial piston machine stroke curve 6, wherein at the lifting cam 6, a plurality of cams 8 are evenly distributed.
  • the first embodiment of the radial piston engine according to the invention is used as a pump. It has a low-pressure leading inlet-side working port 10 and a high-pressure leading downstream additional working port 12.
  • the radial piston pump is connected in a closed circuit with a hydrostatic motor 14. Since the delivery volume of the first embodiment of the radial piston pump according to the invention can be adjusted in three stages, the motor 14 can be adjusted in three stages in the case of a constant motor at a constant input speed of the radial piston pump. If the motor 14 is an adjusting motor, can be achieved by the three stage, an optimization of the efficiency of the transmission.
  • the three-stage adjustment of the delivery volume of the radial piston pump according to the first embodiment is realized in that the piston 2 is designed as a stepped piston and the cylinder 1 as a stepped cylinder. More specifically, both have a central concentric tapered section. As a result, a middle first working space A1 and an annular second working space A2 are formed in the cylinder 1.
  • the first working space A1 is delimited by a first working surface A1, which is formed on a first part piston K1.
  • the second working space R2 is bounded by an annular second working surface A2, which is formed on a second part piston K2.
  • the first part piston K1 is circular cylindrical and peg-like.
  • the second part piston K2 is annular and surrounds the first part piston K1.
  • a piston base body 16 of the piston 2 is guided in the cylinder 1, at the outer (in FIG. 1 lower) end portion of the rolling elements 4 is mounted and at its inner (in FIG. 1 Upper) end portion on the one hand, the first part piston K1 is inserted into a concentric recess 18 and on the other hand, the second part piston K2 can be brought into contact with the front side.
  • the recess 18 of the piston body 16 has a first contact surface 20 for the first part piston K1 and on its side facing away from the rolling element 4 end face a second contact surface 22 for the second part piston K2.
  • shut-off valve 32, 34 is provided in each channel 24, 26 between the working connection 10 and the branch 28, 30.
  • Each shut-off valve 32, 34 is formed as a 2/2-way valve, which is shut off in a by a spring-biased home position, and that in a by an electric Actuator open switching position the associated branch 28, 30 connects to the working port 10.
  • the first branch 28 branches off to the first working spaces R1 of all the cylinders 1, while the second branch 28, 30 branches off to the second working spaces R2 of all the cylinders 1. For reasons of clarity, only three cylinders 1 were assumed.
  • a branched relief channel 42 is provided, which extends in the interior of the piston main body 16, and which connects a housing interior of the radial piston pump with the two contact surfaces 20, 22.
  • FIG. 2 shows the arrangement FIG. 1 , wherein the radial piston pump is set to a reduced delivery volume.
  • the radial piston pump is set to a reduced delivery volume.
  • the second shut-off valve 34 was closed by its spring. This leaves the second sub-piston K2 always in the in FIG. 2 shown position, while the first sub-piston K1 perform together with the piston main bodies 16, the lifting movement.
  • Check valve 40 is provided. More specifically, between each branch 28, 30, 38 and the respective working space R1, R2, a check valve 40 is provided, the (in this embodiment, three) check valves 40, between the drain side further channel 36 and the deactivated second working spaces R2 of all cylinders. 1 are arranged, are always closed in this operating condition, as in the other channel 36 always high pressure prevails, while in the second working spaces R2 always low pressure prevails. All check valves 40, which are assigned to the first work spaces R1, open and close cyclically in this operating state.
  • FIG. 3 shows the arrangement Figures 1 and 2 , wherein the radial piston pump is set to a reduced delivery volume.
  • the radial piston pump is set to a reduced delivery volume.
  • the first shut-off valve 32 was closed by its spring.
  • the first part piston K1 always remain in the in FIG. 2 shown position, while the second sub-piston K2 perform together with the piston main bodies 16, the lifting movement.
  • check valves 40 which are arranged between the drain-side further channel 36 and the deactivated first working spaces R1 of all cylinders 1, are always closed in this operating condition, as in the other channel 36 always high pressure prevails, while in the first working spaces R1 always low pressure prevails. All check valves 40, which are assigned to the second work spaces R2, open and close cyclically in this operating state.
  • FIG. 3 the delivery volume is in operation according to FIG. 3 greater than the delivery volume during operation according to FIG. 2 .
  • the show FIGS. 1 to 3 the three different stages of the delivery volume of the first embodiment of the radial piston pump according to the invention.
  • FIGS. 4 to 6 show in a respective common representation a second and a third embodiment of the radial piston engine according to the invention, which is also operated as a radial piston pump.
  • the illustrated operating states or stages, the cylinder 1, the piston 2, the rolling elements 4, the channels 24, 26, 36 with the branches 28, 30, 38 and the two shut-off valves 32, 34 correspond to those of the first embodiment according to the FIGS. 1 to 3 , Also supplied by the radial piston pump hydrostatic motor 14 corresponds to the previous embodiment.
  • the first embodiment according to the FIGS. 1 to 3 is the cyclic or alternating connection of the working spaces R1, R2 in synchronism with the edges of the cam 8 of the lifting cam 6 according to the second embodiment via respective inlet-side switching valves 44 and a common downstream additional switching valve 46 or according to the third embodiment via a slot control with a control mirror A, B and a distributor plate 48 possible.
  • FIGS. 4 to 6 these two embodiments are shown together.
  • FIG. 7 shows a part of a fourth and a fifth embodiment of the radial piston machine according to the invention. It can be operated bidirectionally with maximum flexibility.
  • the cylinder 1, the piston 2, the rolling element 4, the lift curve 6, and the connection of the working port 10 via the two channels 24, 26 with the cylinder 1 and the common representation of the switching valves 44 with the control mirror A, B and the distributor plate 48th correspond to the second and third embodiments according to FIG. 4
  • FIGS. 8 to 13 each show in a longitudinal section a cylinder 101 with a piston 102 according to a sixth embodiment of the radial piston machine according to the invention, which offers further stages of its stroke volume.
  • the piston main body 116 has an additional outermost circumferential third contact surface 122 for an annular third partial piston K3, which defines with its peripheral third working surface A3 a third working space R3 of the cylinder 101. While the second partial piston - as in the previous embodiments - abuts the outer periphery of the first partial piston K1, the third partial piston K3 engages around the piston main body 116th
  • FIG. 8 shows an operating state in which the first and the second working space R1, R2 are activated, while the third working space R3 is deactivated.
  • FIG. 9 shows an operating state in which the first and the third working space R1, R3 are activated, while the second working space R2 is deactivated.
  • FIG. 10 shows an operating state in which the second and the third working space R2, R3 are activated, while the first working space R1 is deactivated.
  • FIG. 11 shows an operating state in which only the first working space R1 is activated.
  • FIG. 12 shows an operating state in which only the second working space R2 is activated.
  • FIG. 13 shows an operating state in which only the third working space R3 is activated.
  • FIGS. 14 and 15 each show in a longitudinal section the cylinder 101 with the piston 102 according to the sixth embodiment of the FIGS. 8 to 13 ,
  • the discharge channel 142 of this embodiment has a branch to the three abutment surfaces 20, 22, 122, so that at each deactivated or deactivated partial piston K1, K2, K3 pressure medium from the housing interior can be sucked into the intermediate space formed between the affected piston part K1, K2, K3 and the piston body 116.
  • FIG. 14 additionally shows the circuit diagram of the cylinder 101 of a bidirectionally operable radial piston machine.
  • Each working space R1, R2, R3 are assigned, on the one hand, a switching valve 44 and, on the other hand, a further switching valve 46, both of which are switched as a function of the momentarily traveled edge of the cams 8 of the lifting cam 6.
  • FIG. 15 additionally shows the circuit diagram of the cylinder 101 of a radial piston machine, which is to be operated only in one direction.
  • a common further switching valve for the three working spaces R1, R2, R3 of the cylinder 101 is emitted from the outlet side.
  • a slot control with a control mirror A, B and a distributor plate 148 may also be provided.
  • a hydrostatic piston engine with a plurality of stepped piston, which are guided in a respective associated cylinder.
  • Each stepped piston has a first partial piston and on the outer circumference at least one further partial piston which can be moved relative to the first partial piston.
  • Each cylinder has a first working space and at least one of them separated by the stepped piston further working space.
  • Each sub-piston limits a working area with an associated working space.
  • the first working space can be switched on and off via one or two first switching valves, and each further working space can be switched on and off via one or two further switching valves.
  • each partial piston of the stepped piston be activated and deactivated independently of the other sub-piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Valve Device For Special Equipments (AREA)
EP16164342.4A 2015-04-23 2016-04-08 Machine a piston hydrostatique Active EP3091230B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015207440.4A DE102015207440A1 (de) 2015-04-23 2015-04-23 Hydrostatische Kolbenmaschine

Publications (2)

Publication Number Publication Date
EP3091230A1 true EP3091230A1 (fr) 2016-11-09
EP3091230B1 EP3091230B1 (fr) 2021-06-09

Family

ID=55794855

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16164342.4A Active EP3091230B1 (fr) 2015-04-23 2016-04-08 Machine a piston hydrostatique

Country Status (3)

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EP (1) EP3091230B1 (fr)
CN (1) CN106065859B (fr)
DE (1) DE102015207440A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11821500B2 (en) 2017-05-23 2023-11-21 New Leaf Management Ltd. Method and system for harnessing wind energy using a tethered airfoil

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1163145B (de) * 1962-11-15 1964-02-13 Muenchner Motorzubehoer G M B Einrichtung zum Hubveraendern einer Kolbenpumpe
DE1278249B (de) * 1966-11-11 1968-09-19 Schiess Defries Hebezeug Und K Hydraulische Zweistufenhandkolbenpumpe
DE19613080C1 (de) * 1996-04-02 1997-01-23 Waldemar Reimann Pumpe für Flüssigkeiten
EP0927305B1 (fr) * 1997-07-19 2003-01-15 Gustav Klauke GmbH Pompe a pistons
DE102006052775A1 (de) * 2006-07-19 2008-01-24 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102009035893A1 (de) 2009-08-03 2011-02-10 Robert Bosch Gmbh Hydromaschine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10266944A (ja) * 1997-03-21 1998-10-06 Robert Bosch Gmbh ピストンポンプ
NZ526361A (en) * 2003-05-30 2006-02-24 Fisher & Paykel Appliances Ltd Compressor improvements
DE102004027849A1 (de) * 2004-06-08 2006-01-05 Bosch Rexroth Aktiengesellschaft Antriebseinheit
DE102009055228A1 (de) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Kolbenpumpe für eine hydraulische Fahrzeugbremsanlage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1163145B (de) * 1962-11-15 1964-02-13 Muenchner Motorzubehoer G M B Einrichtung zum Hubveraendern einer Kolbenpumpe
DE1278249B (de) * 1966-11-11 1968-09-19 Schiess Defries Hebezeug Und K Hydraulische Zweistufenhandkolbenpumpe
DE19613080C1 (de) * 1996-04-02 1997-01-23 Waldemar Reimann Pumpe für Flüssigkeiten
EP0927305B1 (fr) * 1997-07-19 2003-01-15 Gustav Klauke GmbH Pompe a pistons
DE102006052775A1 (de) * 2006-07-19 2008-01-24 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102009035893A1 (de) 2009-08-03 2011-02-10 Robert Bosch Gmbh Hydromaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11821500B2 (en) 2017-05-23 2023-11-21 New Leaf Management Ltd. Method and system for harnessing wind energy using a tethered airfoil

Also Published As

Publication number Publication date
CN106065859B (zh) 2020-08-11
CN106065859A (zh) 2016-11-02
DE102015207440A1 (de) 2016-10-27
EP3091230B1 (fr) 2021-06-09

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