EP1068450B1 - Adjustable face plate for hydraulic pump or motor - Google Patents

Adjustable face plate for hydraulic pump or motor Download PDF

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Publication number
EP1068450B1
EP1068450B1 EP99913745A EP99913745A EP1068450B1 EP 1068450 B1 EP1068450 B1 EP 1068450B1 EP 99913745 A EP99913745 A EP 99913745A EP 99913745 A EP99913745 A EP 99913745A EP 1068450 B1 EP1068450 B1 EP 1068450B1
Authority
EP
European Patent Office
Prior art keywords
rotor
face plate
rotation
port
ports
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.)
Expired - Lifetime
Application number
EP99913745A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1068450A1 (en
Inventor
Peter Augustinus Johannes Achten
Zhao Fu
Francis J. Raab
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.)
Noax BV
Original Assignee
Noax BV
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
Priority claimed from US09/056,271 external-priority patent/US6038958A/en
Priority claimed from NL1009607A external-priority patent/NL1009607C2/nl
Application filed by Noax BV filed Critical Noax BV
Publication of EP1068450A1 publication Critical patent/EP1068450A1/en
Application granted granted Critical
Publication of EP1068450B1 publication Critical patent/EP1068450B1/en
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
    • F04B1/20—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
    • 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
    • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate

Definitions

  • the invention relates to a hydraulic device as described in the preamble of claim 1.
  • a hydraulic device as described in the preamble of claim 1.
  • Such a device is known, inter alia, from WO 9731165 or from NL 1008256 - which is not a prior publication - of the same applicant, both of which relate to a hydraulic pressure transformer.
  • the disadvantage of the known device is that in the known device energy loss occurs due to high fluid speeds, with the result that the efficiency of the device is low. It has been found that a considerable part of the loss occurs during the closing of the inlet to or outlet from the fluid chamber. In the hydraulic device the inlet to or outlet from the fluid chamber is closed or opened gradually while the volume of the fluid chamber is changing.
  • the object of the invention is to avoid the above disadvantage, and to that end the known device is designed as claimed in the characterizing clause of claim 1. In this way the high flow velocity occurs only during a small rotor rotation, with the result that the losses are limited.
  • the invention also relates to a hydraulic device designed as claimed in claim 2.
  • the edges of the rotor port and the face plate port are formed by the line of intersection of a straight surface and the boundary surface. Such an edge can be simple in design and sharp, so that small cracks are avoided. This ensures that fewer losses occur.
  • the device is designed as claimed in claim 3.
  • the hydraulic device is designed as claimed in claim 4.
  • FIGS 1 and 2 show a hydraulic pressure transformer 1, the operation of which corresponds to that described in WO 9731185 .
  • the hydraulic pressure transformer 1 has a rotor housing 4 containing bearings 2 in which a rotary shaft 3 can rotate. Attached to the rotary shaft 3 are plungers 5, which can slide in the fluid chambers 7 of a rotor 6. The rotor 6 can rotate freely about its axis of rotation in the rotor housing 4.
  • a face plate housing 10, in which a face plate 8 can rotate, is fixed on the rotor housing 4.
  • the face plate 8 can be rotated by means of an adjusting shaft 9.
  • the face plate housing 10 is provided with a first line connection 11, a second line connection 12 and a third line connection (not shown).
  • the line connections are connected to the fluid chambers 7 by means of channels, which channels run through the face plate housing 10, the face plate 7 and the rotor 6.
  • the rotor 6 and the face plate 8 are pressed against each other in a sealing manner in a boundary surface 13 by the oil pressure in the fluid chambers 7.
  • Each face plate port 14 is provided in the face plate 8 (see Figure 2a), with three walls 15 between them.
  • Each face plate port 14 according to the prior art has an inner radius 17, an outer radius 16 and a circular side edge 18.
  • the rotor 6 is provided with seven rotor ports 19, each of which is in communication with a fluid chamber 7.
  • the fluid chamber 7 goes into communication with a face plate port 14, is sealed off by a wall 15, and subsequently goes into communication with the next face plate port 14.
  • the shutting off of a fluid chamber 7 by means of a wall 15 of a face plate 8 is commonly applied in a corresponding manner in the case of the known hydraulic plunger pumps and plunger motors.
  • the fluid chamber 7 is shut off when the speed of change of the fluid chamber volume is great.
  • said chamber according to the invention must be closed quickly.
  • Figure 4 shows how in this embodiment the face plate 6 and the rotor 8 are situated in relation to each other in the position in which a rotor port 19 is just not yet covered fully by the wall 15.
  • a side edge 21 of the rotor port 19 at the left-hand side coincides with a side edge 20 of the face plate port 14.
  • the wall 15 is a distance 'a' broader than the rotor port 19, so that no short-circuiting can occur between the pressure in the one face plate port 14 and the other.
  • the distance 'a' is more or less constant over the entire breadth, viewed in the directions of rotation of the rotor, so that when the rotor port 19 rotates to the right, the right-hand, adapted side edge 21 over the entire common breadth 'b' will simultaneously pass the left-hand side edge of the rotor port 14, with the result that the aperture is opened simultaneously over the entire common breadth 'b'.
  • the side edge 20 of the face plate port 14 and the side edge 21 of the rotor port 19 lie in a plane parallel to the axis of rotation of the rotor. This means that the holes on the inside can be worked accurately using simple means, while the boundary surface 13 can also be worked accurately in the known manner. In this way a sharp edge of the ports can be obtained, which increases the accuracy of the simultaneous closing over the entire breadth, thereby making loss reduction possible.
  • FIG. 5a and 5b A second embodiment is shown in Figures 5a and 5b.
  • the rotor has twelve fluid chambers 7 and rotor ports 19.
  • the common breadth 'b' has remained the same and, owing to the fact that the rotor ports 19 have become narrower, the common breadth 'b' is greater than the breadth of the rotor port in the direction of rotation.
  • the flow velocity during closure is reduced by this, because the common breadth has remained the same and the volume of the fluid chamber 7 has been reduced because there are now more fluid chambers 7.
  • Figure 6 shows a third embodiment, in which the shape of the face plate ports 14 has been adapted to the round shape of the rotor ports 19.
  • round rotor ports 19 are simple to make (for example, by drilling and/or honing), while the face plate ports 14 are always a special shape which can be made in a special way (for example by spark erosion).
  • Figure 7 shows a fourth embodiment, in which the rotor port is formed in such a way that the greatest breadth, viewed in the direction of rotation, is situated near the axis of rotation.
  • the oil flow to the fluid chamber 7 is directed largely towards the outside diameter of the rotor 6, with the result that cavitation is less likely to occur.
  • curve I indicates how the efficiency of the hydraulic pressure transformers designed according to the above mentioned exemplary embodiments depends on the speed of rotation of the rotor. It can be seen here that at low speeds the efficiency is high, but that at high speeds the efficiency falls sharply. It is obvious here that the speed of the volume changes in the fluid chambers 7 when they are shut off by the walls 15 is important. By making the walls narrower, as a result of which a fluid chamber 7 is in communication with two face plate ports 14 through a small rotation angle of the rotor 6, for example through 1 to 3 degrees, it is ensured that no great pressure build-up occurs in the fluid chamber 7. The efficiency of the hydraulic pressure transformer is consequently slightly lower at low speeds, but it remains more or less constant over the entire speed range. This is indicated by curve II in Figure 8. Since the efficiency is now higher at high speed of rotation, the total loss is greatly reduced.
  • Figure 9 shows the first exemplary embodiment according to figures 3 and 4, in which the wall 15 between the face plate ports 14 has been made narrower. Viewed in the direction of rotation, the face plate port 19 is a distance 'u' greater than the wall 15 over the entire common breadth 'b'. This means that, through the overlapping of the face plate port 19 over the wall 15, a fluid chamber 7 is in communication with at least one aperture 'u' with a face plate port, so that volume changes during rotation of the rotor 6 do not cause a great pressure build-up in the fluid chamber 7, and high, loss-producing flow velocities are consequently avoided.
  • Figure 10 shows the adapted third exemplary embodiment according to Figure 6 in a corresponding manner
  • Figure 11 shows the adapted fourth exemplary embodiment according to Figure 7.
  • the exemplary embodiments discussed above are based on the known pressure transformer which is designed with plungers 5 and a rotary shaft 3. Likewise in the case of hydraulic devices which are designed differently such as, for example, where the volume of the fluid chambers 7 changes by a movement along a cam disk, the same problems can occur if the fluid chambers 7 are shut off while the volume is changing. The solutions described above can then be used in a comparable manner.
  • the fluid chambers are shut off by valves formed by a face plate with ports.
  • the valves are designed differently and the control of the valves is by different mechanical means, for example with a cam disk. It is also possible for the valves to be operated electrically. In this situation the invention can also be designed accordingly, in which case the valves must be rapid-acting and the time of opening and closing of the valves is possibly selected in such a way that the fluid chambers are never fully shut off, but are in communication with two line connections over a limited rotation of the rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exposure And Positioning Against Photoresist Photosensitive Materials (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
EP99913745A 1998-04-07 1999-04-06 Adjustable face plate for hydraulic pump or motor Expired - Lifetime EP1068450B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US56271 1998-04-07
US09/056,271 US6038958A (en) 1998-04-07 1998-04-07 Porting for hydraulic pressure transformer
NL1009607 1998-07-10
NL1009607A NL1009607C2 (nl) 1998-07-10 1998-07-10 Hydraulische inrichting.
PCT/NL1999/000198 WO1999051881A1 (en) 1998-04-07 1999-04-06 Adjustable face plate for hydraulic pump or motor

Publications (2)

Publication Number Publication Date
EP1068450A1 EP1068450A1 (en) 2001-01-17
EP1068450B1 true EP1068450B1 (en) 2003-09-17

Family

ID=26642840

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99913745A Expired - Lifetime EP1068450B1 (en) 1998-04-07 1999-04-06 Adjustable face plate for hydraulic pump or motor

Country Status (4)

Country Link
EP (1) EP1068450B1 (ja)
JP (1) JP2002510773A (ja)
DE (1) DE69911386T2 (ja)
WO (1) WO1999051881A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014207158A1 (de) 2013-12-12 2015-06-18 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1013996C2 (nl) 1999-12-30 2001-07-03 Innas Free Piston Bv Vrijezuiger aggregaat voor opwekken van hydraulische energie.
CN102562690B (zh) * 2012-02-07 2014-10-15 北京理工大学 一种小流量脉动液压变压器
DE112014004909T5 (de) 2014-10-31 2016-07-07 Komatsu Ltd. Hydraulikpumpe/-Motor
CN105673587B (zh) * 2016-03-24 2017-08-15 太原科技大学 采用组合式配流盘的液压变压器
DE102018202716A1 (de) * 2018-02-22 2019-08-22 Mahle International Gmbh Axialkolbenmaschine mit einem verdrehbaren Steuerscheibensitz

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1068075A (en) * 1963-09-19 1967-05-10 Lely Nv C Van Der Improvements in or relating to hydraulic pumps
DE1278840B (de) * 1967-02-16 1968-09-26 August Monath Dr Ing Kolbentrieb einer Axialkolbenpumpe
DE3820632A1 (de) * 1988-06-10 1989-12-14 Tuczek Franz Kolbenverdichter
NL1002430C2 (nl) * 1996-02-23 1997-08-26 Innas Free Piston Ifp Bv Inrichting voor het opwekken, gebruiken of transformeren van hydraulische energie.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014207158A1 (de) 2013-12-12 2015-06-18 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
US10094365B2 (en) 2013-12-12 2018-10-09 Robert Bosch Gmbh Hydrostatic axial piston machine

Also Published As

Publication number Publication date
WO1999051881A1 (en) 1999-10-14
DE69911386D1 (de) 2003-10-23
JP2002510773A (ja) 2002-04-09
DE69911386T2 (de) 2004-07-01
EP1068450A1 (en) 2001-01-17

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