EP1523622A1 - Piston engine comprising a pulsation-reducing device - Google Patents
Piston engine comprising a pulsation-reducing deviceInfo
- Publication number
- EP1523622A1 EP1523622A1 EP03740448A EP03740448A EP1523622A1 EP 1523622 A1 EP1523622 A1 EP 1523622A1 EP 03740448 A EP03740448 A EP 03740448A EP 03740448 A EP03740448 A EP 03740448A EP 1523622 A1 EP1523622 A1 EP 1523622A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- line
- pressure compensation
- piston machine
- compensation line
- 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
Links
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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
-
- 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
- F04B1/20—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 rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
-
- 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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
Definitions
- the invention relates to a piston machine with a device for reducing flow pulsations.
- the design causes the pressure to pulsate due to the non-uniform delivery of the pressure medium used, which spreads through the line system.
- a device for reducing the pulsation in which a pressure compensation line opens in the reversing area of the control level, which is connected to the high-pressure control kidney via a controlled throttle.
- the controlled throttle consists of a piston, which has a control edge, the equilibrium position of the piston being set by a compression spring and in the opposite direction by a pressure force, the pressure force being generated by the pressure prevailing in the high-pressure control kidney.
- a disadvantage of the piston machine described above is that the flow pulsations, which occur only in a reduced manner, but cannot be completely avoided, are transmitted to the control piston, and the control piston can in turn be excited to oscillate. This has a direct influence on the effectiveness of the pressure compensation, which should be made possible by the variable throttle.
- Another disadvantage is that due to the movement of the control piston, which is inevitable due to the pulsation of the pressure in the high-pressure control kidney, considerable wear occurs on the pulsation reducing device. It is an object of the invention to provide a piston machine with pulsation reduction, which is simple and inexpensive to implement and which requires no additional components and no additional installation space.
- the piston machine according to the invention has the advantage that to generate a pulsation reduction, only a pressure compensation line has to be provided, which is arranged between a working line and an opening arranged in a reversing area of a control mirror.
- a pressure compensation line all that needs to be taken into account is that the opening in the working line must be provided at a point which enables the pressure wave progressing in the working line to be picked up in phase. This tapping in the correct phase makes it possible, on the one hand, to achieve a pressure increase in a cylinder space in a piston engine operated as a pump.
- FIG. 1 shows a schematic illustration of an axial piston machine according to the prior art
- FIG. 2 shows a plan view of a control mirror of an axial piston machine operated as a pump
- FIG. 3 shows a plan view of a control mirror of a piston engine operated as a motor
- FIG. 4 shows a plan view of the control mirror of the axial piston machine from FIG. 1 at a later point in time
- FIG. 5 shows a plan view of the control mirror of the axial piston machine from FIG. 3 to a later one
- Fig. 6 is a plan view of a control mirror of
- FIG. 7 shows a top view of a control mirror of an axial piston machine from FIG. 3 with an additional pressure accumulator.
- FIG. 1 shows a section through an axial piston machine 1 known per se.
- a cylinder drum 2 is arranged in the interior of a housing (not shown) of the axial piston machine 1, the cylinder drum 2 being rotatably mounted with respect to a central axis 12.
- Cylinder openings 3, 4 are provided in the cylinder drum 2. see, the cylinder openings 3, 4 are arranged parallel to the central axis 12 and are evenly distributed over the circumference.
- Pistons 5, 6 are arranged in the cylinder bores 3, 4 and are displaceably mounted in the cylinder openings 3, 4.
- the cylinder bores 3, 4 each have a cylinder opening 7 at an end face of the cylinder drum 2,
- control kidneys 9, 10 are arranged in a control mirror 11, which is connected to the housing of the axial piston machine 1 in a rotationally fixed manner.
- the control kidneys 9, 10, which extend along a segment of a circle, are each connected to a working line, not shown in FIG. 1.
- the pistons 5, 6 each have an approximately spherical extension 13, 14, the spherical geometry of which corresponds to a recess 15, 16 of a slide shoe 17, 18, respectively.
- the sliding shoes 17, 18 are supported on a swivel disk 25.
- both the spherical extensions 14, 13 and the slide shoes 17, 18 each have a pressure oil bore 21, 22 or 23, 24.
- the cylinder drum 2 For operation as an axial piston pump, the cylinder drum 2 is rotated about its central axis 12, the pistons 5, 6 arranged in the cylinder drum 2 being one due to the inclination of the swivel plate 25 with respect to the central axis 12 Carry out a lifting movement, wherein they are connected to a low-pressure control kidney during a suction-lifting movement, whereas they are connected to a high-pressure control kidney during a high-pressure lifting movement.
- FIG. 2 shows a top view of a control mirror 11 of an axial piston pump, the direction of rotation of the cylinder drum 2 being indicated by an arrow.
- the cylinder drum 2 has nine cylinder bores distributed uniformly over its circumference, the cylinder openings of which are shown in broken lines in FIG. 2 and identified by the reference numbers 35.1 to 35.9.
- a high-pressure control kidney 9 as the first control kidney and a suction control kidney 10 as the second control kidney are arranged in the control mirror 11.
- An area is provided between the control kidney 9 and the control kidney 10, in which the cylinder openings 35.1 to 35.9 have no contact with either one or the other control kidney 9, 10. These areas are identified as reversing area 30 or reversing area 31.
- an opening is arranged which forms a first end 32 of a pressure compensation line 33.
- the pressure compensation line 33 has a second end 34 which opens into a working line 27.
- the axial piston machine 1 shown in FIG. 2 sucks pressure medium from a tank volume 29 via a working line 28 and, as indicated by the arrow, conveys it into the working line 27.
- non-uniformities in the flow rate occur during operation of an axial piston machine 1. These non-uniformities in the flow rate result in a pressure pulsation, as is shown schematically in the working line 27.
- Starting from the High-pressure control kidney 9 progresses a pressure wave along the working line 27.
- a length L of the working line 27 between the high-pressure control kidney 9 and the second end 34 of the pressure compensation line 33 is dimensioned such that the progressive pressure wave in the working line 27 at the moment when the second end 34 of the pressure compensation line 33 has a maximum to which the first end 32 in the reversing area 30 comes into contact with a further cylinder opening.
- the cylinder opening 35.6 is next in register with the opening at the first end 32 of the pressure compensation line 33.
- the second end 34 of the pressure compensation line 33 a pressure maximum in the working line 27, so a pressure compensation takes place in which the pressure in the cylinder bore, which is connected to the cylinder opening 35.6, is increased via the pressure compensation line 33.
- the amplitude of the pressure wave advancing in the working line 27 is reduced in the further course. A reduction in pressure pulsation is thus achieved.
- a pressure maximum in the working line 27 arises whenever a cylinder opening 35.1 to 35.9 encloses a certain angle with the central axis of the working line 27, which is repeated cyclically in accordance with the number of pistons per revolution. Accordingly, at the time shown, the pressure maximum in the working line 27 has advanced from the side of the high-pressure control kidney 9 by approximately one wavelength ⁇ .
- a connection channel 39 also opens into the reversing area 31, the second end of which opens into the control kidney 10.
- FIG. 3 shows a corresponding device for an axial piston machine 2, which is operated as a hydraulic motor.
- a high pressure which is generated, for example, by the axial piston machine shown in FIG. 2, is fed to the hydraulic motor via the working line 28.
- the direction of rotation is counterclockwise.
- the reversing area 31 is swept through the cylinder openings 35.1 to 35.9, the high pressure generated by the filling on the high pressure side in the cylinder bore is partially released into the working line 27 via the pressure compensation line 33.
- the second end 34 of the pressure compensation line 33 is connected to the working line 27 so that at the time when the cylinder opening 35.1 comes into contact with the opening at the first end 32 of the pressure compensation line 33, a pressure minimum at the second end 34 of the pressure compensation line 33 prevails.
- a pilot control notch 40 is formed for a slow pressure build-up in the direction of rotation in front of the control kidney 10.
- FIG. 4 shows the axial piston machine 2 from FIG. 2 again for a later point in time.
- the pressure wave, which propagates in the working line 27, has progressed by% ⁇ in accordance with the angle of rotation of the cylinder drum 2, and accordingly there is a pressure maximum at the end of the working line 27, which is oriented toward the high-pressure control kidney, which by the Cylinder opening 35.8 belonging piston is caused.
- This pressure maximum which arises at the beginning of the working line 27 moves at the speed of sound along the working line 27, whereby it must have reached the second end 34 of the pressure compensation line 33 at the point in time at which the cylinder opening 35.5 following in the direction of rotation coincides with the opening on the first End 32 of the pressure compensation line 33 has reached.
- the remaining angle ⁇ which the cylinder with the cylinder opening 35.2 must make up to the opening at the first end 32 of the pressure compensation line 33, must be taken as a basis.
- the minimum distance between the orifice at the second end 34 of the pressure compensation line and the outlet control kidney 9 of the axial piston machine 1 is therefore determined from the quotient of the remaining angle ⁇ and the intermediate angle ⁇ between two successive cylinder openings 35.2 and 35.3, in contrast because of the tap of the pressure minimum a shift of ⁇ / 2 must be taken into account in the case described above for a pump.
- FIGS. 6 and 7 show two further exemplary embodiments for pulsation reductions according to the invention, a storage element 38 being provided in each case in addition to the pulsation reduction already carried out by tapping a pressure fluctuation in the working line 27 in the correct phase.
- a storage element 38 being provided in each case in addition to the pulsation reduction already carried out by tapping a pressure fluctuation in the working line 27 in the correct phase.
- a defined cross-sectional area can alternatively be provided at the junction of the pressure compensation line 33 in the working line 27 at the second end 34.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10232983A DE10232983A1 (en) | 2002-07-19 | 2002-07-19 | Piston machine with pulsation |
DE10232983 | 2002-07-19 | ||
PCT/EP2003/007422 WO2004009996A1 (en) | 2002-07-19 | 2003-07-09 | Piston engine comprising a pulsation-reducing device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1523622A1 true EP1523622A1 (en) | 2005-04-20 |
EP1523622B1 EP1523622B1 (en) | 2007-09-12 |
Family
ID=30010244
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03740448A Expired - Fee Related EP1523622B1 (en) | 2002-07-19 | 2003-07-09 | Piston engine comprising a pulsation-reducing device |
Country Status (4)
Country | Link |
---|---|
US (1) | US7585158B2 (en) |
EP (1) | EP1523622B1 (en) |
DE (2) | DE10232983A1 (en) |
WO (1) | WO2004009996A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009037994A1 (en) * | 2007-09-19 | 2009-03-26 | Komatsu Ltd. | Hydraulic pump-motor and method of preventing pulsation of hydraulic pump-motor |
DE102008017253A1 (en) | 2008-04-04 | 2009-10-08 | Robert Bosch Gmbh | Medium pulsation damping device i.e. freely pivotable screw propeller, for use in hydraulic pressurizing medium line in piston pump, has hub with which propeller is supported on axis, where device is designed as rotary mounting unit |
US20120275935A1 (en) * | 2011-04-28 | 2012-11-01 | Hamilton Sundstrand Corporation | Inlet Plenum with Shock Wave Suppression |
DE102014109066A1 (en) | 2014-06-27 | 2015-12-31 | Claas Industrietechnik Gmbh | transmission assembly |
JP7390151B2 (en) | 2019-10-03 | 2023-12-01 | 株式会社小松製作所 | hydraulic pump motor |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2920278C2 (en) * | 1979-05-18 | 1984-01-12 | Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal | Soundproofing device |
SE507637C2 (en) * | 1991-09-06 | 1998-06-29 | Parker Hannifin Ab | Method and apparatus for damping flow pulsations in hydrostatic displacement hydraulic machines and apparatus for carrying out the method |
US5507151A (en) * | 1995-02-16 | 1996-04-16 | American Standard Inc. | Noise reduction in screw compressor-based refrigeration systems |
US5555726A (en) * | 1995-03-31 | 1996-09-17 | Caterpillar Inc. | Attenuation of fluid borne noise from hydraulic piston pumps |
BR9600527A (en) * | 1996-02-01 | 1997-12-30 | Brasil Compressores Sa | Discharge arrangement for airtight compressor |
DE19706114C9 (en) * | 1997-02-17 | 2014-02-06 | Linde Hydraulics Gmbh & Co. Kg | Device for pulsation reduction on a hydrostatic displacement unit |
IL120609A0 (en) * | 1997-04-06 | 1997-08-14 | Nordip Ltd | Hydraulic axial piston pumps |
US6112514A (en) * | 1997-11-05 | 2000-09-05 | Virginia Tech Intellectual Properties, Inc. | Fan noise reduction from turbofan engines using adaptive Herschel-Quincke tubes |
EP1013928A3 (en) * | 1998-12-22 | 2000-11-08 | Parker Hannifin GmbH | Swash plate axial piston pump with pulsation damping means |
DE10034857A1 (en) * | 2000-07-18 | 2002-01-31 | Liebherr Machines Bulle S A | Hydrostatic axial piston machine |
TW587125B (en) * | 2000-07-28 | 2004-05-11 | Sanyo Electric Co | Reciprocating compressor |
JP2002070728A (en) * | 2000-09-04 | 2002-03-08 | Calsonic Kansei Corp | Pulsation reducing structure for swash plate compressor |
US6364055B1 (en) * | 2000-09-26 | 2002-04-02 | Alan H. Purdy | Acoustically non-resonant pipe |
US6558137B2 (en) * | 2000-12-01 | 2003-05-06 | Tecumseh Products Company | Reciprocating piston compressor having improved noise attenuation |
-
2002
- 2002-07-19 DE DE10232983A patent/DE10232983A1/en not_active Withdrawn
-
2003
- 2003-07-09 WO PCT/EP2003/007422 patent/WO2004009996A1/en active IP Right Grant
- 2003-07-09 EP EP03740448A patent/EP1523622B1/en not_active Expired - Fee Related
- 2003-07-09 DE DE50308180T patent/DE50308180D1/en not_active Expired - Lifetime
- 2003-07-09 US US10/521,992 patent/US7585158B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2004009996A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2004009996A1 (en) | 2004-01-29 |
US20060096558A1 (en) | 2006-05-11 |
US7585158B2 (en) | 2009-09-08 |
EP1523622B1 (en) | 2007-09-12 |
DE50308180D1 (en) | 2007-10-25 |
DE10232983A1 (en) | 2004-02-05 |
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