EP3749857B1 - Axialkolbenpumpe in schrägscheibenbauart - Google Patents

Axialkolbenpumpe in schrägscheibenbauart Download PDF

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Publication number
EP3749857B1
EP3749857B1 EP19715863.7A EP19715863A EP3749857B1 EP 3749857 B1 EP3749857 B1 EP 3749857B1 EP 19715863 A EP19715863 A EP 19715863A EP 3749857 B1 EP3749857 B1 EP 3749857B1
Authority
EP
European Patent Office
Prior art keywords
piston
actuating
cylinder
pump according
axial
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
EP19715863.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3749857A1 (de
Inventor
Manuel KRONPASS
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.)
Hydac Drive Center GmbH
Original Assignee
Hydac Drive Center 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 Hydac Drive Center GmbH filed Critical Hydac Drive Center GmbH
Publication of EP3749857A1 publication Critical patent/EP3749857A1/de
Application granted granted Critical
Publication of EP3749857B1 publication Critical patent/EP3749857B1/de
Active legal-status Critical Current
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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
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0686—Control by changing the inclination of the swash plate
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/143—Sealing provided on the piston
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating

Definitions

  • the invention relates to an axial piston pump of swash plate design, in particular for hydraulic systems, having the features in the preamble of claim 1.
  • Swash plate type axial piston pumps are state of the art. They are widely used for the supply of pressure medium to consumers such as working cylinders, hydraulic motors and the like.
  • Axial piston pumps of the type mentioned at the outset, in which the inclination of the swash plate relative to the axis of rotation can be adjusted, are characterized by a better energy balance during operation compared to axial piston pumps that are also known with a fixed swash plate.
  • An axial piston pump of the type mentioned is in the document WO 2014/187512 A1 disclosed.
  • the DE 10 2013 008 681 A1 discloses an axial piston pump of swash plate design, in particular for hydraulic systems, with a cylinder drum that can be driven in a pump housing to rotate about an axis of rotation, in which pistons are arranged so as to be axially movable, which are supported at least indirectly on a swash plate with their actuating end that is accessible outside of the cylinder drum to adjust the stroke of the pistons and thus the fluid system pressure generated by them to the desired angle of inclination relative to the axis of rotation by means of an adjusting device which has at least one pivoting lever which can be deflected and reset in at least one direction by means of an adjusting drive and which in at least one hydraulically actuable actuating cylinder each has an actuating piston which acts at one end on an articulation point of the pivoting lever, the at least one actuating piston having a guide at its end remote from the articulation point surface which is in contact with an associated
  • the object of the invention is to provide an axial piston pump whose adjustment device for setting the position of the swash plate is characterized by a high level of operational reliability with a comparatively simple structure. According to the invention, this object is achieved by an axial piston pump that has the features of patent claim 1 in its entirety. According to the characterizing part of patent claim 1 it is provided that a second compensating means is formed between the second actuating cylinder and its piston rod with a guide zone of the piston of the second actuating cylinder forming the crowned guide surface.
  • the actuating drive can be implemented with only a single articulation point between the pivoting lever and the actuating piston.
  • a ball joint is formed between the piston and piston rod of the actuating piston in the known solution mentioned. Thanks to the presence of the compensating means, this ball joint is omitted in the invention, so that the actuating piston can be formed in one piece with its piston rod by a rotary part. In addition to the simplification and reduction in production costs achieved as a result, the frictional forces and hysteresis are also reduced as a result of the omission of the ball joint located in the piston.
  • the compensating means can be formed at least partially from a crowned outer contour of at least one of the guide surfaces and/or a resilient sealing arrangement at the free end of at least one respective actuating piston and/or a compression spring arrangement and/or a lubricant supply.
  • the arrangement can be such that one actuating piston is connected to a system pressure side with its free end and the other actuating piston is connected to a control pressure side with its free end, which are part of the actuating device for the adjustment device.
  • the lubricant supply can have a longitudinal channel through one of the actuating pistons, which is preferably assigned to the system pressure side, and a further channel in the pivot point of the pivoting lever.
  • a throttle on the free end face of the actuating piston can form the inlet of the longitudinal channel.
  • the respective actuating piston has, adjacent to its end face, a sealing zone formed by at least one piston ring and adjoining this a guiding zone which forms a convex guiding surface which forms the compensating means by abutting against the guiding surface of the actuating cylinder a section of reduced diameter adjoins the guide zone, which forms the transition to the piston rod of the actuating piston.
  • the articulation point is formed by a ball joint with a ball head formed at the free end of the pivoting lever and a ball socket on the respective actuating piston, the spring arrangement of the ball head and respective ball socket being non-positive keeps in contact with each other.
  • the entire actuator drive can be designed without play.
  • the arrangement can advantageously be made in such a way that the spring arrangement simultaneously prestresses the swash plate into the pivoting position corresponding to the maximum pump delivery. Due to this double function of the spring arrangement, the actuating cylinder does not have to be designed as a double-acting cylinder for generating actuating movements in both directions, but a single-acting actuating cylinder can be provided, which only performs an actuating movement from the pivoting position for maximum pump delivery to a lower delivery volume, up to towards zero funding.
  • the spring arrangement can have a compression spring, which preloads the piston rod of the second actuating piston for the movement that corresponds to the extension of the actuating piston of the second actuating cylinder and the retraction of the actuating piston of the first actuating cylinder and thus the pivoting of the pivoting lever from the direction parallel to the axis in the direction corresponds to the position of the maximum pump delivery.
  • the arrangement can advantageously be such that the first actuating cylinder is acted upon by a control pressure for setting the pump delivery and the second actuating cylinder is acted upon by the prevailing system pressure.
  • the adjustment device is set to maximum delivery by the force of the compression spring.
  • the maximum delivery setting is retained until the actuating force generated by the control pressure in the first actuating cylinder exceeds the piston force generated by the system pressure in the second actuating cylinder plus the spring force, after which the control pressure dependent, the swash plate is swiveled back to a lower delivery rate.
  • the piston area of the piston of the first actuating cylinder that can be acted upon by the control pressure is preferably selected to be larger than the piston area of the piston of the second actuating cylinder that can be acted upon by the system pressure.
  • a pump housing is denoted by 1 in which a cylinder drum 3 can be rotated about an axis of rotation 7 by means of a drive shaft 5 .
  • axially movable pistons 9 located in the cylinder drum 3 are supported on the sliding surface 13 of a swash plate 15 via sliding shoes 11 located at their upper ends.
  • the swash plate 15 is about this pivot axis between the in 1 and 4 shown, swiveled settings, which correspond to the maximum flow rate of the pump, and the in 2 , 3 and 5 Settings shown pivoted to zero funding, in which case the plane of the sliding surface 13, based on the vertical course of the axis of rotation 7, is in the horizontal, so that no stroke of the piston 9 occurs when the cylinder drum 3 rotates.
  • the adjusting device 21 has a pivoted lever 23 which is fastened to the swash plate 15 and extends to the side of the swash plate 15 and the cylinder drum 3 .
  • the pivoting lever 23 is attached to the housing 1 by means of a pivot pin 19 (see Fig. 2 ) pivoted.
  • the pivoting lever 23 has a pivot point 29 which acts on the actuators of the adjustment device 21 in order to rotate the pivoting lever 23 in the plane of the drawing 1 and 3 to 5 to move and thus to pivot the swash plate 15 about its pivot axis.
  • the adjusting device 21 has how Figures 3 to 5 show a first actuating cylinder 31 with a cylinder axis 32 defining a cylinder sleeve 33 in which an actuating piston 35 is guided.
  • the piston 35 is formed by a rotating part that is integral with its piston rod 37 and has a ball socket 39 at its free end, which forms a ball joint when it rests against the ball head 29 of the pivoting lever 23 forming the pivot point.
  • the adjusting device 21 has a second actuating cylinder 43 with a cylinder bushing 45 opposite the first actuating cylinder 31 and lying thereon on the same cylinder axis 32 .
  • a second actuating piston 47 is guided, which, like the first actuating piston 35, is formed together with its piston rod 49 by a one-piece rotary part.
  • the second actuating piston 47 has a ball socket 51 at the free end of its piston rod 49, which forms a second ball joint when it rests on the ball head 29 of the pivoting lever 23.
  • the pressure-loaded piston surface 53 of the first piston 35 is larger than the pressure-loaded piston surface 55 of the second actuating piston 47 a compression spring 59 is clamped, which moves the adjusting device 21 into the in 4 shown, the maximum pump delivery corresponding setting biases and also keeps the ball joints formed on the ball head 29 of the pivot lever 23 without play.
  • a compensating means is provided in the invention, which is provided for this purpose in the prior art , additional ball joint located in the respective actuating piston.
  • the compensating means is provided by guide surfaces on the respective actuating piston 35, 47, which is designed in one piece with its piston rod 37 or 49, and by a guide surface on the associated actuating cylinder 31, 43, more precisely, by its cylinder bushing 33 or 45 , educated.
  • a special outer contour of the respective actuating piston 35, 47 is provided as a guide surface, which forms part of the compensating means.
  • the relevant shape is with reference to the Figures 6 to 8 explained, which contain separate representations of the second actuating piston 47 integral with its piston rod 49 . That in these figures, and particularly in 8 , For the smaller actuating piston 47 shown circumferential profile corresponds in full to the circumferential profile of the larger actuating piston 35.
  • FIGS. 6 and 7 show the actuating piston 47 with the compression spring 59 pre-assembled on it, which is supported on the one hand on the fixed spring plate 57 of the piston rod 49 and on the other end on a spring plate which can be displaced on the circular-cylindrical outer surface 61 of the piston rod 49 and which consists of two ring halves 63 and 65 composite spring plate is.
  • relaxed state of the compression spring 59 is the divided spring plate 63, 65 at a stage 67 of the piston rod 49.
  • a sealing zone 69 is formed from a piston ring pack 70 consisting of three identically shaped piston rings 71, one of which is in Figures 9 and 10 is shown in more detail.
  • a guide zone 73 On the side facing away from the piston surface 55 closes (see Fig. 8 ) on the piston rings 71 a guide zone 73.
  • This is formed from a peripheral section 75, which forms the respective piston-side guide surface and has a slight convex curvature, which is selected in such a way that the piston 47 is guided in the respective cylinder liner 33, 45, which forms the cylinder-side guide surface, even if there is a slight axial deviation.
  • Section 75 is in turn adjoined by a section 77 ( 8 ) which forms the transition to the peripheral sections of the piston rod 49, which have a further reduced outside diameter.
  • FIGS. 9 and 10 show the construction of the piston rings 71.
  • the 10 is the in 9 Y-designated open area of the respective piston ring 71 shown in more detail. As shown, this area is toothed in such a way that the piston ring 71 is elastically flexible because there are free spaces 79 in the transition area of its ring ends 80, within which the two ring ends 80 can move towards one another, as indicated by directional arrows 81, while they are on a Separation point 83 slide together, which forms a sealing surface.
  • a continuous lubricant bore 85 is formed in the piston rod 49 in the piston 47, which can be subjected to the system pressure 51 leads and continues from there via a bore 89 in the ball head 29 to the ball socket 39 of the larger piston 35.
  • the pressure chamber 91 of the actuating cylinder 31 ( 3 and 5 ) can be acted upon by the control pressure that actuates the adjusting device 21, while the pressure chamber 93 of the actuating cylinder 43 ( 4 ) can be subjected to the system pressure.
  • the 4 shows the adjustment to maximum flow rate with no control pressure in the pressure chamber 91 of the larger actuating piston 35. Due to the system pressure acting in the pressure chamber 93 of the smaller actuating piston 47 and the force of the compression spring 59, which is supported on the cylinder liner 45 via the divided spring plate 63, 65, the pistons 35 and 47 are shifted to the right in the drawing and the pivoted lever 23 in 4 shown position swung out.
  • a corresponding control pressure is supplied to the pressure chamber 91 of the actuating cylinder 31 .
  • the pistons 35, 47 move to the left in the drawing, and the delivery rate can be reduced to zero delivery rate is that in 3 and 5 is shown with the split spring plate 63, 65 having slid on the cylindrical portion 61 of the piston rod 49 and moved away from the step 67 with the compression spring 59 being compressed. Due to the action of the compression spring 59, the adjustment device is set to the maximum delivery rate even when the pump is at a standstill and there is therefore no system pressure 4 is shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
EP19715863.7A 2018-04-19 2019-03-29 Axialkolbenpumpe in schrägscheibenbauart Active EP3749857B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018003207.9A DE102018003207A1 (de) 2018-04-19 2018-04-19 Axialkolbenpumpe in Schrägscheibenbauart
PCT/EP2019/057982 WO2019201574A1 (de) 2018-04-19 2019-03-29 Axialkolbenpumpe in schrägscheibenbauart

Publications (2)

Publication Number Publication Date
EP3749857A1 EP3749857A1 (de) 2020-12-16
EP3749857B1 true EP3749857B1 (de) 2023-03-08

Family

ID=66049189

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19715863.7A Active EP3749857B1 (de) 2018-04-19 2019-03-29 Axialkolbenpumpe in schrägscheibenbauart

Country Status (8)

Country Link
US (1) US11725639B2 (ja)
EP (1) EP3749857B1 (ja)
JP (1) JP7167182B2 (ja)
CN (1) CN111989485A (ja)
AU (1) AU2019256414A1 (ja)
CA (1) CA3096965C (ja)
DE (1) DE102018003207A1 (ja)
WO (1) WO2019201574A1 (ja)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1534766A (en) * 1923-01-15 1925-04-21 Ottis R Briney Sealing means for pistons and the like
US3174762A (en) * 1962-01-29 1965-03-23 Sealed Power Corp Piston and fire ring construction
US3817660A (en) * 1971-06-25 1974-06-18 Ford Motor Co Air conditioner compressor
US4334832A (en) * 1980-03-06 1982-06-15 The Bendix Corporation Constant output fluid pump
DE3232363A1 (de) * 1981-09-09 1983-03-24 Linde Ag, 6200 Wiesbaden Einstellbare schraegscheiben-axialkolbenmaschine mit gleitgelagertem wiegenkoerper
DE3327351A1 (de) * 1983-07-29 1985-02-07 Robert Bosch Gmbh, 7000 Stuttgart Verstelleinrichtung fuer eine axialkolbenmaschine
DE3626619A1 (de) * 1986-08-06 1988-02-18 Hydromatik Gmbh Hydropumpe oder -motor verstellbaren verdraengungsvolumens
DE10006460B4 (de) * 2000-02-14 2010-06-24 Linde Material Handling Gmbh Nabenantrieb
DE102012218971A1 (de) * 2012-10-18 2014-04-24 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102013008681A1 (de) * 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Axialkolbenpumpe in Schrägscheibenbauart
EP2999885B1 (de) 2013-05-22 2017-12-06 Hydac Drive Center GmbH Axialkolbenpumpe in schrägscheibenbauart
JP6363900B2 (ja) * 2014-07-22 2018-07-25 ナブテスコ株式会社 可変容量型油圧装置
JP2016183662A (ja) 2015-03-27 2016-10-20 株式会社日立産機システム 圧縮機及びピストンリング

Also Published As

Publication number Publication date
CN111989485A (zh) 2020-11-24
DE102018003207A1 (de) 2019-10-24
JP2021520470A (ja) 2021-08-19
EP3749857A1 (de) 2020-12-16
CA3096965A1 (en) 2019-10-24
AU2019256414A1 (en) 2020-10-08
CA3096965C (en) 2024-06-04
WO2019201574A1 (de) 2019-10-24
US11725639B2 (en) 2023-08-15
JP7167182B2 (ja) 2022-11-08
US20210115909A1 (en) 2021-04-22

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