EP1039127A2 - Machine axiale à pistons - Google Patents

Machine axiale à pistons Download PDF

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Publication number
EP1039127A2
EP1039127A2 EP00104963A EP00104963A EP1039127A2 EP 1039127 A2 EP1039127 A2 EP 1039127A2 EP 00104963 A EP00104963 A EP 00104963A EP 00104963 A EP00104963 A EP 00104963A EP 1039127 A2 EP1039127 A2 EP 1039127A2
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston machine
swash plate
machine according
spring
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
EP00104963A
Other languages
German (de)
English (en)
Other versions
EP1039127A3 (fr
EP1039127B1 (fr
Inventor
Ralf Dr. Lemmen
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1039127A2 publication Critical patent/EP1039127A2/fr
Publication of EP1039127A3 publication Critical patent/EP1039127A3/fr
Application granted granted Critical
Publication of EP1039127B1 publication Critical patent/EP1039127B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • An axial piston machine of this type is in the DE 196 45 580 C1.
  • this known Axial piston machine is used to adjust the Throughput volume an adjustment device with one at the Swivel device attacking swashplate or swashplate provided with which the swashplate or swashplate optionally can be swung back and forth and depending on Swivel direction, the swivel angle and the throughput volume can be enlarged and reduced.
  • the swivel device exerts a torque on the swashplate or swashplate that counteracts the torque that the resulting and effective against the swashplate or swashplate Piston force generated.
  • This known axial piston machine does not only exist a large construction and manufacturing effort because one in both Effective swivel device is to be provided, but also a relatively large control effort, around the swash plate z. b. when reaching a maximum Pressure or a maximum output by driving the To pivot the swivel device back.
  • the invention has for its object a Axial piston machine of the type specified above to design that the construction and manufacturing costs, the Control effort and effort are reduced.
  • the axial piston machine In the axial piston machine according to the invention there is a Spring element provided, the one on the inclined or Swashplate generates second torque that that of the resulting piston force on the oblique or Swashplate opposed first torque applied is.
  • the inventive configuration is particularly suitable for Power limitation of the axial piston machine, the Axial piston machine is designed so that it Equilibrium state of the torques about their maximum Delivers power. This will overload the Axial piston machine avoided automatically.
  • Axial piston machine 1 is the axial piston machine according to the invention only partially shown.
  • the example shown Axial piston machine 1 is in a so-called Swashplate design, and it includes one Cylinder block 2, in which several, on a pitch circle evenly distributed, approximately axial Cylinder bores 3 are provided.
  • pistons 4 are arranged to be longitudinally movable.
  • the cylinder bores 3 are connected by connecting channels 5 kidney-shaped control openings 6a, 6b in a control disk 7 connected, which is shown only in part Housing 8 is arranged stationary.
  • the cylinder block 2 is on a drive shaft, not shown, around his Longitudinal central axis rotatably mounted in the housing 8 so that the Cylinder bores 3 cyclically with one on the associated one Control opening 6a connected, not shown Low pressure line and one at the associated Control port 6b connected, also not high pressure line shown are connected.
  • the pistons 4 are facing away from the control disk 7 Articulated ends supported on a swash plate 9; in the present embodiment by means of sliding shoes 11, which on a flat sliding surface 12 of the swash plate 9th apply and each with a ball joint connection 13 the piston 4, which is preferably designed as a hollow piston are connected.
  • the working spaces of the pistons 4 and their Piston recesses 14 are through axial connecting channels 15 in the piston 4 and corresponding axial Connection channels 16 in the shoes 11 for hydrostatic relief with on the contact surfaces of the Sliding shoes 11 provided pressure pockets 17 connected.
  • At 18 is a known retraction device referred to the sliding shoes 11 in permanent contact the sliding surface 12 of the swash plate 9 holds.
  • the retraction device 18 by one of the sliding shoes 11 in a manner known per se engaging perforated disc 19 formed with a central spherical segment-shaped cap 21 on a spherical segment-shaped saddle 22, z.
  • B. a ring on the Drive shaft, not shown, pivotable on all sides is stored. It can be a drive shaft that the end wall 8a of the housing 8 in a round hole 8b enforced and therein z. B. stored by means of a roller bearing and is sealed.
  • the swash plate 9 is transverse to one Longitudinal central axis 23 of the axial piston machine 1 extending Swivel axis 24 in an only indicated Swivel bearing 25, for.
  • B. means on both sides of the Swash plate 9 arranged cylindrical pivot pin, between a swivel position of a minimum swivel angle W, in which the between the sliding surface 12 and the Longitudinal central axis 23 included angles z.
  • B. approximately Is zero, and a swivel position of the maximum swivel angle W1 pivoted.
  • the pivot axis is 24 with respect to the longitudinal central axis 23 of the cylinder block 2 .mu.m the dimension eK is offset transversely.
  • the resulting piston force Kr is the swash plate 9 applied with a torque M1 that the Minimum swash plate 9 in its swivel position Swing angle W tries to swivel.
  • one is resiliently effective pivoting device 26 provided that the swash plate 9 with a torque M2 applied, which is opposite to the torque M1.
  • the effective element of the swiveling device 26 is one Spring 27, in particular a helical spring, here one Compression spring, which is supported on the housing 8 and with it elastic spring force acts on the swash plate 9.
  • the spring 27 on the End wall 8a of the housing 8 supported being preferably between the end wall 8a and the swash plate 9 can be arranged and preferably in one Recess 28, 29 in the end wall 8a and / or in the Swashplate 9 is arranged with play.
  • the radial effective distance of the adjusting device 26 from the Swivel axis 24 is designated by egg and in Embodiment larger than the offset dimension eK.
  • a swivel stop 31, 32 provided, each by an adjusting device is preferably adjustable to a certain amount of Throughput volume in the maximum and minimum To be able to adjust the swivel end position.
  • the adjustable swivel stops are an exemplary embodiment 31, 32 formed by adjusting screws 33 to both Sides of the longitudinal central axis 23 each in one Threaded bore 34 are screwed into the end wall 8a, by a screw-engaging element 35, e.g. B.
  • one Screw head or a screw slot are rotatable and by a securing element, e.g. B. a lock nut 36, can be secured against unintentional loosening.
  • a securing element e.g. B. a lock nut 36
  • this is the piston 4 opposite back 37 of the swash plate 9 wedge-shaped shaped, the two wedge surfaces 37a, 37b one include an obtuse angle towards the Cylinder block 2 is open, the wedge surfaces 37a, 37b so are arranged that the one wedge surface 37a Swashplate 9 in its minimum pivot position is located and the other wedge surface 37b on Swivel stop 31, the swash plate 9 in their maximum swivel position.
  • the apex 38 can on the one hand in the pivot axis 24 and on the other hand on the Inside 8c of the end wall 8a.
  • the swivel stops 31, 32 form, namely in that the swash plate 9 with their preferably flat wedge surfaces 37a, 37b each on the Fit inside 8c.
  • Torque M1 increasingly outweighs torque M2, whereby the swash plate 9 towards its minimum Swivel position is pivoted until it is an equilibrium of the torques M1, M2 is established. If the Working pressure exceeds the value p2, the remains Swash plate 9 due to its abutment on the swivel stop 32, so that the throughput volume W also if necessary increasing working pressure p is no longer reduced, but remains constant.
  • the maximum power of the axial piston machine is in FIG. 3 as a dash-dotted, hyperbolic curved line N shown.
  • the course of the performance characteristic N is located between the minimum and maximum working pressure p1, p2 in the vicinity of the inclined in Fig. 3 Section of the assertion volume characteristic curve V.
  • the axial piston machine is not overloaded can be achieved by changing the characteristic curve by means of a corresponding Swiveling back below the maximum performance characteristic N is located.
  • the maximum performance characteristic N can be exceeded by pressure cut off by a Pressure relief valve at limit pressure p3 can be prevented.
  • the design described above enables a passive pressure-dependent throughput volume adjustment and adjustment, that works in pump mode and in motor mode. This is achieved in that a pressure-dependent and by respective equilibrium of the torques M1 and M2 predetermined adjustment and setting of the swash plate 9 in the area between two pivot end positions, namely passive against the elastic abutment, here the spring 27, takes place.
  • the adjustment is principally for a reduction of the swivel angle of the Swashplate 9 designed with increasing working pressure.
  • the passive pressure-dependent adjustment of the swash plate 9 also for one The swivel angle increases with increasing working pressure to train.
  • the Point of application of the resulting piston force Kr and Point of attack of the elastic abutment or Back swing device 26 mirror image of the swing axis 24 to move, d. H. to the side on which the resulting piston force Kr the swash plate 9 in their Swivel end position of maximum swivel angle W1 is applied.
  • this results in dashed lines Throughput volume characteristic curve V1 shown in FIG. 3.
  • the elasticity of the elastic Abutment or the reset device 26, namely the Force the spring 27 is adjustable.
  • the present exemplary embodiment serves a purpose Adjustment device 39 with which the bias of the spring 27th can be adjusted. It is about a Adjustment screw 41 with a rotary handle element, e.g. B. a cross slot which is an adjustable limit for the Spring 27 forms and in the present embodiment in the recess 28 projects into the end wall 8a from the outside, being in the bottom of the recess 28 penetrating threaded hole 42 and screwed through Securing element is secured, in particular by a screwed onto the outside of the adjusting screw 41 Lock nut 43.
  • a correspondingly effective one Damping element 44 can each on the swash plate 9 or be arranged on the end wall 8a.
  • Fig. 1 that is Damping element 44 integrated in the swash plate 9. It is by a damping cylinder 45 in the form of a axial cylinder bore 46 is formed in which a piston 47th sealed is slidably mounted.
  • the damping cylinder 45 is designed as a blind bore on the wedge surface 37a of the swash plate 9 opens out.
  • the damping piston 47 is also in the damping cylinder 42 arranged return spring 48 in its extension direction and against a stationary counterpart, here against the front wall 8a, preferably against the free end of the adjusting screw 33, biased.
  • the working chamber of the damping cylinder 45 is with a check valve 49 in an inlet channel 51 the surrounding the swash plate 9 and the cylinder block 2 Housing interior 52 connected, the z. B. as a leakage fluid collecting space serves and accordingly with a fluid low Pressure, especially hydraulic oil, is filled.
  • the Working chamber of the damping cylinder 45 is over a Throttle element 53 additionally with the housing interior 52 connected.
  • the throttle element 53 is shown in FIG Embodiment as a relatively small bore Cross section formed. The inlet channel 51 and that Check valve 49 are thus parallel to that Throttle element 53 arranged.
  • Cylinder bore 46 and the damping piston 47 so long dimensioned that the damping piston 47 relatively far can protrude from the cylinder bore 46 and permanently on associated pivot stop 31, 32 can rest. At this Design results in a damping effect on the entire swivel range. Then the power of Include return spring 48 in the torques M1, M2, if this restoring force is relatively large. Because it for an extension movement of the damping piston 47 in each case this spring force can only require a low spring force be neglected if it is small.
  • Fig. 2 is an example of a damping element 44 in the End wall 8a arranged integrated to clarify that the damping elements 44 both on the swash plate 9 and can also be arranged on the end wall 8a. It can an adjusting screw 33 opposite in the Swashplate 9 may be arranged. With this configuration is the adjusting screw 33 or the associated one Adjustment device only accessible from the inside and therefore in front arranged against unauthorized access. This also applies to the adjusting device 39 for adjusting the spring force.
  • the damping element can of course also be structurally combined with the spring 27 and z. B. in the recess 29th be arranged.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP00104963A 1999-03-19 2000-03-08 Machine axiale à pistons Expired - Lifetime EP1039127B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19912509 1999-03-19
DE19912509A DE19912509C2 (de) 1999-03-19 1999-03-19 Axialkolbenmaschine

Publications (3)

Publication Number Publication Date
EP1039127A2 true EP1039127A2 (fr) 2000-09-27
EP1039127A3 EP1039127A3 (fr) 2001-02-28
EP1039127B1 EP1039127B1 (fr) 2005-08-17

Family

ID=7901703

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00104963A Expired - Lifetime EP1039127B1 (fr) 1999-03-19 2000-03-08 Machine axiale à pistons

Country Status (2)

Country Link
EP (1) EP1039127B1 (fr)
DE (2) DE19912509C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103790795A (zh) * 2012-10-31 2014-05-14 罗伯特·博世有限公司 用于流体静力的活塞机的调整设备以及具有这种调整设备的流体静力的活塞机
EP3171023A4 (fr) * 2014-07-16 2017-08-16 Kabushiki Kaisha Toyota Jidoshokki Pompe à piston à capacité variable
CN108361165A (zh) * 2018-04-09 2018-08-03 李涌权 容量可调型流体泵

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1521884A (en) * 1923-02-14 1925-01-06 Jr Henry B Higgins Pump or motor
US2935951A (en) * 1953-01-29 1960-05-10 Daimler Benz Ag Pump means for hydraulic servo systems
US3282225A (en) * 1965-06-04 1966-11-01 Sunstrand Corp Pump swashplate control
US4945817A (en) * 1989-10-24 1990-08-07 General Motors Corporation Axial piston device
JPH04284180A (ja) * 1991-03-11 1992-10-08 Toyota Autom Loom Works Ltd 可変容量ピストンポンプ
DE19645580C1 (de) * 1996-11-05 1998-04-02 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit Dämpfungselement für die Schräg- oder Taumelscheibe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103790795A (zh) * 2012-10-31 2014-05-14 罗伯特·博世有限公司 用于流体静力的活塞机的调整设备以及具有这种调整设备的流体静力的活塞机
CN103790795B (zh) * 2012-10-31 2017-11-21 罗伯特·博世有限公司 用于流体静力的活塞机的调整设备以及具有这种调整设备的流体静力的活塞机
EP3171023A4 (fr) * 2014-07-16 2017-08-16 Kabushiki Kaisha Toyota Jidoshokki Pompe à piston à capacité variable
CN108361165A (zh) * 2018-04-09 2018-08-03 李涌权 容量可调型流体泵

Also Published As

Publication number Publication date
EP1039127A3 (fr) 2001-02-28
EP1039127B1 (fr) 2005-08-17
DE50010945D1 (de) 2005-09-22
DE19912509A1 (de) 2000-09-28
DE19912509C2 (de) 2002-11-07

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