EP1206640A1 - Axialkolbentriebwerk mit einem stufenlos verstellbaren kolbenhub - Google Patents
Axialkolbentriebwerk mit einem stufenlos verstellbaren kolbenhubInfo
- Publication number
- EP1206640A1 EP1206640A1 EP00965884A EP00965884A EP1206640A1 EP 1206640 A1 EP1206640 A1 EP 1206640A1 EP 00965884 A EP00965884 A EP 00965884A EP 00965884 A EP00965884 A EP 00965884A EP 1206640 A1 EP1206640 A1 EP 1206640A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- crank chamber
- axial
- swash plate
- actuating unit
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
-
- 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
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
Definitions
- the invention is based on an axial piston engine with an infinitely adjustable piston stroke according to the preamble of claim 1.
- An air conditioning system of a motor vehicle essentially has a refrigerant compressor, a first heat exchanger, the so-called evaporator, a second heat exchanger, an expansion element and pipes which connect the components to one another.
- the task of the refrigerant compressor is to suck a refrigerant from the evaporator, in which the refrigerant evaporates while absorbing heat, and to compress it to a higher pressure.
- the refrigerant can then give off the heat at a higher temperature level and is throttled in the expansion element to a pressure level of the evaporator.
- the performance of the refrigerant compressor can be made infinitely variable via the piston stroke via a drive speed and particularly energetically favorably in axial piston engines.
- Known axial piston engines or axial piston compressors for motor vehicle air conditioning systems have a drive shaft driven by a pulley.
- a swash plate is rotatably and tiltably mounted on the drive shaft via a joint.
- the swash plate drives at least one piston which is movable in a cylinder.
- each piston is connected to the swash plate via two articulated stems, specifically with a joint on the tread of the swash plate facing the piston and on the tread facing away from the piston.
- the joint stems run with their flat surfaces on the running surfaces of the swash plate at full circumferential speed with superimposed radial movement, which results in an elliptical raceway.
- the articulated stones lie in shaped spherical bearings of the pistons, in which there is a comparatively small relative movement during operation.
- the swash plate can be connected to the pistons by means of a swash plate instead of articulated stones.
- the swash plate is secured against rotation to the drive shaft either on a housing or via piston rods.
- a bearing between the swash plate and the swash plate takes up the entire relative movement. Because of the rotating swashplate, the swashplate only performs a wobble movement.
- the piston stroke and thus the performance of the axial piston compressor is set via the degree of the tilt angle of the swash plate.
- the tilt angle of the swashplate is usually limited to a minimum and a maximum value by two stops.
- one or two guide pins are required to guide the tilting movement in a defined manner and to avoid jamming.
- the tilt limits or the stops can be integrated in the guide pins.
- the swash plate is additionally axially displaceably mounted against a prestressed Druckfe ⁇ er.
- the swashplate is generally limited by the m axial direction.
- the axial piston engine according to the invention has a drive shaft with a swash plate mounted thereon in a crank chamber and slidable in the axial direction.
- a tilting angle and an axial position of the swash plate can be set via a control device.
- the swash plate is connected to at least one piston which can be moved in a cylinder.
- the control device have an actuating unit separate from the piston. With a control unit separate from the piston, a control range that is independent of the operating points can be created. An actuating force can only be introduced in the direction of the possible adjustment movement of the swash plate, as a result of which jamming and increased wear can be avoided.
- the axial piston engine can be operated with a low pressure in the crank chamber.
- a leakage flow of refrigerant from the crankcase through shaft seals to the outside is roughly proportional to the crankcase pressure.
- an elaborate sealing of the crankcase can be avoided and a low leakage can be achieved.
- This is particularly advantageous in the case of refrigerants with high absolute pressures, in which high pressures in the crankcase are generally required for regulation via a gas pressure difference on the piston.
- the solubility of the refrigerant of an air conditioning system in a lubricant of the piston is also low, whereby a high viscosity can be maintained.
- the viscosity has a positive effect that heating of the lubricant by a gas heated by the high-pressure side of the piston can be avoided with a separate actuating unit.
- a high viscosity low friction can be achieved between highly loaded sliding pairs on the swash plate and between the pistons and the cylinders, which contributes to a long service life and high reliability.
- a control unit separated from the piston no specific pressure in the crank chamber is required for regulation, as a result of which coolant can be fed into the cylinder through the crank chamber from an evaporator.
- the crankcase can thereby be cooled, an additional suction chamber on the top of the piston can be avoided and installation space can be saved.
- a mostly large volume of the crankcase can be used to dampen gas pulsations.
- the actuating unit can be driven electrically, pneumatically or advantageously hydraulically. With hydraulic fluid, an advantageous vibration damping can be achieved and a particularly vibration-insensitive axial column engine can be created.
- the hydraulic actuating unit can be supplied with pressure oil from a hydraulic unit that is independent of the required medium of the piston, for example advantageously from a hydraulic unit that is already present in a motor vehicle. Additional components can be saved and a large control range independent of the operating points of the axial piston engine can be achieved. Furthermore, no pressure build-up or start-up is required for the control, for example due to a minimum tilt angle of 2 °. A load-free start-up of the axial piston engine is made possible and starting an internal combustion engine driving the axial piston engine, for example, is made easier.
- the oil separator With an oil separator downstream of the cylinder, good heat transfer in the heat exchangers can be ensured and a high efficiency of an air conditioning system can be achieved. Furthermore, the oil separator can be used particularly inexpensively to supply the hydraulic actuating unit with pressure oil.
- the pressure oil from the oil separator is depending on pressure. If a high actuating force is required, there is a high pressure in the oil separator; if a small actuating force is required, there is a low pressure.
- the hydraulic actuating unit to the crank chamber via a drain, whereby the oil separator and the actuating unit can be used particularly advantageously to convey the lubricant back into the crank chamber.
- an inflow from the oil separator to the actuating unit and / or the outflow from the actuating unit to the crank chamber can be regulated. If only the outflow or the inflow is designed to be controllable, the unregulated connection can be formed by an inexpensive throttle point.
- an oil level control unit be arranged in the oil separator and / or in the crank chamber, which unit is located when the oil level in the oil separator is exceeded and / or falls below an oil level in the crankcase connects the oil separator to the crankcase via a channel.
- crankcase It is also possible to always connect the oil separator to the crank chamber via a channel and a throttle point, or to match the oil separator and the oil quantity so that the oil separator overflows before there is a lack of oil or a lack of lubricant in the crank chamber.
- the overflowing oil can then be pumped into the crankcase, for example together with a coolant from an air conditioning system. With a controlled inflow and outflow, a sufficient amount of lubricant can always be ensured in the crankcase.
- the Schragsche oe can be made tiltable and axially displaceable with various constructions which appear suitable to the person skilled in the art.
- the swash plate can be mounted on a Z-shaft with a tilted bearing bore and a rotational movement of the bearing plate can be superimposed with a lifting movement, etc.
- the invention proposes that the swash plate be mounted on a joint head which is axially displaceable via an actuating piston of the actuating unit, and that the swash plate is connected to a component fixed in the axial direction via a decentral joint.
- a structurally simple and inexpensive adjustment mechanism can be achieved in which the tilt angle and the axial position of the swash plate have a desired relationship.
- the top dead center of the piston in the cylinder bore can become obsolete and damage space and energy losses can be avoided, as a result of which the axial piston engine can be used particularly advantageously as an earner in an air conditioning system.
- the compressor can be designed as a pure swash plate compressor or as a swash plate compressor.
- the solution according to the invention can be applied to gears, etc.
- the actuating piston and the joint head are advantageously made in one piece, which means that additional components, assembly effort and costs can be saved.
- the actuator can be partially or completely co-rotating with the drive shaft or non-rotatably arranged in a housing.
- the actuation unit can be on the side facing away from the piston Swashplate or from the side facing the piston act on the swashplate.
- FIG. 1 shows an axial piston engine with maximum piston stroke in section
- FIG. 2 shows an axial piston engine with minimum piston stroke in section
- FIG. 3 shows a detail of a variant according to FIG. 1 and
- FIG. 4 shows a schematic diagram of a hydraulic control.
- FIG. 1 shows an axial piston engine for an air conditioning system of a motor vehicle, which works as a compressor.
- the axial piston engine has a drive shaft 10 on which a swash plate 16 is mounted in a crank chamber 14.
- the swash plate 16 is driven via hemispherical ⁇ * j * e gear Steering system 56 connected to pistons 26, 28 guided in cylinders 22, 24.
- each piston 26, 28 is connected to the swash plate 16 via two articulation members 56, in each case via an articulated block 56 with a tread 58 facing the piston 26, 28 and with a tread 58 facing away from the piston 26, 28 , 60.
- the articulated stones 56 run with their flat surfaces on the running surfaces 58, 60 of the swash plate 16 at full circumferential speed with superimposed radial movement, which results in an elliptical path.
- the articulated stones 56 lie with their arched
- the swash plate is connected in a rotationally fixed manner to the drive shaft 10 via an articulated head 48 of an articulated sleeve 64.
- the inclined disk 16 can be tilted with a control device 18 on the joint head 48 and displaced in the axial direction with the joint sleeve 64.
- the control device 18 has a hydraulic actuating unit 30 which is separate from the pistons 26, 28.
- the actuating unit 30 has an actuating piston 4 formed in one piece with the joint sleeve 64 and the joint head 48.
- the actuating piston 44 is guided in a cylinder formed by an actuating housing 54.
- the actuating housing 54 is fixed radially on the drive shaft 10 by means of a positive engagement (not shown in more detail) and axially by means of a clamping ring 76. Stigt.
- the drive shaft 10 is axially the direction facing away from the cylinders 22, 24 via the adjusting housing 54, the axial bearing 80 and via a running disk 82 on a cover 78 and the direction of the cylinders 22, 24 via an axial slide bearing 84 on a housing 86 of the Axial piston engine trimmed. Furthermore, the drive shaft 10 is mounted in the cover 78 and in the housing 86 via two radial bearings 88, 90.
- the actuating piston 44 encloses the pressure chamber 74 sealed with the cylinder em via three services 68, 70, 72.
- Swash plate 16 is connected in one piece to the connecting element 66 and a decentralized joint 52 with the actuating pin 54.
- the actuating piston 44 merges together with the joint sleeve 64, the joint head 48 and the swash plate 16 m in the direction of the cylinders 22, 24 against a prestressed compression spring 92 (FIG. 2).
- the compression spring 92 st drenfest connected to the drive shaft 10 and sicn sicn from a clamping ring 94 in the direction used by the actuating piston 44 from.
- the ⁇ ecentral joint 52 which is formed by a bolt 98 fastened to the connecting element 66 and guided in an elongated hole 96, results in a tilting moment on the swash plate 16 due to the lifting movement of the swash plate 16
- Swashplate 16 is overlaid by a tilting movement guided by bolt 98 in slot 96, so that in each case top dead center 100 of pistons 26, 28 m of cylinders 22, 24 is retained.
- the volume of the pressure chamber 74 is preferably small.
- the actuating unit 30 or the actuating piston 44 is actuated by an oil separator 34 ** connected downstream of the cylinders 22, 24 an Axialoonrung 102, 104, 106 in the housing 86, in the slide bearing 84 and m of the drive shaft 10 and via a radial bore 108 of the drive shaft 10 supplied with pressure oil (Fig. 1, 2 and 4).
- the pressure oil is advantageously fed axially in the center of the drive shaft 10. In this area, the relative movement between the drive shaft 10 and the slide bearing 84 is advantageously small.
- the slide bearing 84 can also be used as a seal. If there is still no oil pressure in the oil separator 34 when starting, the compression spring 92 sets a maximum tilt angle em, which ensures pressure build-up.
- the Swiftmneit 30 is connected to the oil separator 34 via an inlet 38 and to the crank chamber 14 via an outlet 36.
- the inflow 38 and the outflow 36 can each be controlled via valve 110, 112. If a higher actuating force is required, valve 110 opens. 01 flows into actuating unit 30 at a high pressure level and acts on actuating piston 44. Valve 112 remains closed. If a lower actuating force is required, the valve 112 opens, whereby the 01 flows out of the actuating unit 30 and a lower force is available at the actuating unit 30.
- the swash plate 16 is moved via the compression spring 92 in the direction of the maximum tilt angle.
- the valve 110 is closed.
- FIG. 3 shows a section of a variant of an axial piston engine with a control device 20. Components that are essentially the same are fundamentally numbered with the same reference numerals. With regard to the function and components not shown, reference can be made to the exemplary embodiment in FIGS. 1 and 2.
- the control device 20 has a steep unit 32 with an actuating piston 46, which is arranged in a non-rotatable manner in an annular recess 122 of a housing 114 of the axial piston engine, as a result of which an additional actuating housing can be saved.
- the actuating piston 46 is loaded in the direction of the swash plate 16 by a first compression spring 136, is sealed with respect to the housing 114 by two seals 116, 118 and acts on the swash plate 16 in via a joint sleeve 120 and a joint head 50 which is embodied integrally with the joint sleeve 120 axial direction counter to a second prestressed, stronger compression spring 124.
- the compression spring 124 is supported on a shoulder 126 of a drive shaft 12 in the direction facing away from the actuating piston 46.
- the swash plate 16 is supported via a decentral articulation in the axial direction, not shown, so that a tilting moment on the swash plate 16 arises as a result of the lifting movement of the swash plate 16.
- the actuating piston 46 and the articulated sleeve 120 are connected via axial bearings 128 acting on both sides, the actuating piston 46 forming inner treads, the articulated sleeve 120 and fastening element 130 forming outer treads.
- a defined axial play in the axial bearing 128 can be set with the fastening element 130, which is connected to the joint sleeve 120 via a thread 132.
- the actuating unit 32 or the actuating piston 46 is supplied with pressure oil by an oil separator 34 via an axial bore 134, like the actuating inlet 30 (cf. corresponding to FIG. 4).
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19939131 | 1999-08-18 | ||
DE19939131A DE19939131A1 (de) | 1999-08-18 | 1999-08-18 | Axialkolbentriebwerk mit einem stufenlos verstellbaren Kolbenhub |
PCT/EP2000/008084 WO2001012989A1 (de) | 1999-08-18 | 2000-08-18 | Axialkolbentriebwerk mit einem stufenlos verstellbaren kolbenhub |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1206640A1 true EP1206640A1 (de) | 2002-05-22 |
EP1206640B1 EP1206640B1 (de) | 2003-11-12 |
Family
ID=7918769
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00965884A Expired - Lifetime EP1206640B1 (de) | 1999-08-18 | 2000-08-18 | Axialkolbentriebwerk mit einem stufenlos verstellbaren kolbenhub |
Country Status (6)
Country | Link |
---|---|
US (1) | US6957604B1 (de) |
EP (1) | EP1206640B1 (de) |
JP (1) | JP2003507627A (de) |
AU (1) | AU7647700A (de) |
DE (2) | DE19939131A1 (de) |
WO (1) | WO2001012989A1 (de) |
Families Citing this family (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7331271B2 (en) * | 2001-02-08 | 2008-02-19 | R. Sanderson Management, Inc. | Variable stroke/clearance mechanism |
US7841849B2 (en) * | 2005-11-04 | 2010-11-30 | University Of Southern California | Dry material transport and extrusion |
BRPI0416975B1 (pt) * | 2003-11-28 | 2014-12-23 | Textilma Ag | Dispositivo de controle de fio para uma máquina têxtil, especialmente para um dispositivo de formação de cala |
US7438029B2 (en) * | 2004-03-18 | 2008-10-21 | R. Sanderson Management, Inc. | Piston waveform shaping |
US20050238501A1 (en) * | 2004-04-26 | 2005-10-27 | Brailovskiy Aleksandr M | Revolving yoke load-sensitive displacement-varying mechanism for axial piston hydraulic pump |
BRPI0511592A (pt) * | 2004-05-26 | 2008-01-02 | Sanderson R Man Inc | mecanismo de curso e folga variáveis |
US8308470B2 (en) * | 2005-11-04 | 2012-11-13 | University Of Southern California | Extrusion of cementitious material with different curing rates |
EP2623782B1 (de) * | 2006-11-02 | 2014-12-24 | University Of Southern California | Mess- und Pumpvorrichtungen |
JP5519193B2 (ja) * | 2009-06-05 | 2014-06-11 | サンデン株式会社 | 可変容量圧縮機 |
KR101739212B1 (ko) * | 2012-11-05 | 2017-05-23 | 가부시키가이샤 도요다 지도숏키 | 용량 가변형 사판식 압축기 |
CN105102815B (zh) * | 2013-03-27 | 2017-04-05 | 株式会社丰田自动织机 | 容量可变型斜板式压缩机 |
JP5949805B2 (ja) * | 2014-02-25 | 2016-07-13 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6115258B2 (ja) * | 2013-03-29 | 2017-04-19 | 株式会社豊田自動織機 | 両頭ピストン型斜板式圧縮機 |
WO2014157209A1 (ja) * | 2013-03-29 | 2014-10-02 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6032228B2 (ja) * | 2014-03-04 | 2016-11-24 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
CN105051368B (zh) * | 2013-03-29 | 2017-03-08 | 株式会社丰田自动织机 | 可变容量型斜板式压缩机 |
JP6060925B2 (ja) * | 2014-03-10 | 2017-01-18 | 株式会社豊田自動織機 | 可変容量型斜板式圧縮機 |
DE112014001734T5 (de) * | 2013-03-29 | 2015-12-17 | Kabushiki Kaisha Toyota Jidoshokki | Taumelscheibenverdichter mit variabler Verdrängung |
KR101889628B1 (ko) * | 2013-09-11 | 2018-08-17 | 가부시키가이샤 도요다 지도숏키 | 용량 가변형 사판식 압축기 |
JP6094456B2 (ja) | 2013-10-31 | 2017-03-15 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6146263B2 (ja) * | 2013-11-06 | 2017-06-14 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6123665B2 (ja) * | 2013-12-16 | 2017-05-10 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6217474B2 (ja) * | 2014-03-14 | 2017-10-25 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6194830B2 (ja) * | 2014-03-24 | 2017-09-13 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6191527B2 (ja) * | 2014-03-28 | 2017-09-06 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6194837B2 (ja) | 2014-03-28 | 2017-09-13 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6287483B2 (ja) * | 2014-03-28 | 2018-03-07 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6194836B2 (ja) | 2014-03-28 | 2017-09-13 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6179438B2 (ja) * | 2014-03-28 | 2017-08-16 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP6179439B2 (ja) | 2014-03-28 | 2017-08-16 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP2016102419A (ja) * | 2014-11-27 | 2016-06-02 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JP2016102418A (ja) * | 2014-11-27 | 2016-06-02 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
JPWO2016140106A1 (ja) * | 2015-03-04 | 2017-11-30 | 株式会社豊田自動織機 | 可変容量型斜板式圧縮機 |
WO2019005619A1 (en) | 2017-06-27 | 2019-01-03 | TSC Manufacturing and Supply, LLC | VARIABLE STROKE PUMP |
US10670003B1 (en) * | 2019-10-24 | 2020-06-02 | CW Holdings Ltd. | Tilt linkage for variable stroke pump |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE866115C (de) * | 1943-07-06 | 1953-02-05 | Gaston Robert Bouchard | Kolbenmaschine mit Taumelscheibe, insbesondere Brennkraftkolbenmaschine |
US2964234A (en) * | 1954-05-13 | 1960-12-13 | Houdaille Industries Inc | Constant clearance volume compressor |
DE1755912C3 (de) * | 1968-07-09 | 1974-02-14 | Hans Dipl.-Ing. 7502 Malsch Molly | Leistungsverzweigtes hydrostatisches Fahrzeuggetriebe |
US3552886A (en) * | 1968-11-13 | 1971-01-05 | Mitchell Co John E | Compressor unit with self-contained drive means |
US3712759A (en) * | 1971-01-04 | 1973-01-23 | Mitchell J Co | Lubricating system for multiple piston compressor units and driven parts thereof |
US3861829A (en) * | 1973-04-04 | 1975-01-21 | Borg Warner | Variable capacity wobble plate compressor |
NL7500731A (nl) * | 1975-01-22 | 1976-07-26 | Philips Nv | Heetgaszuigermotor. |
US4073603A (en) * | 1976-02-06 | 1978-02-14 | Borg-Warner Corporation | Variable displacement compressor |
US4037993A (en) * | 1976-04-23 | 1977-07-26 | Borg-Warner Corporation | Control system for variable displacement compressor |
DE2633618A1 (de) * | 1976-07-27 | 1978-02-02 | Josef Jobelius | Stufenlosregelbares drehmoment erzeugende kolbenkraftmaschine |
US4105370A (en) * | 1977-05-19 | 1978-08-08 | General Motors Corporation | Variable displacement compressor with three-piece housing |
US4178135A (en) * | 1977-12-16 | 1979-12-11 | Borg-Warner Corporation | Variable capacity compressor |
US4236875A (en) * | 1979-10-04 | 1980-12-02 | General Motors Corporation | Pressure operated hydraulic control valve |
US4475871A (en) * | 1982-08-02 | 1984-10-09 | Borg-Warner Corporation | Variable displacement compressor |
JPH01182581A (ja) * | 1988-01-14 | 1989-07-20 | Honda Motor Co Ltd | 容量可変式圧縮機の制御装置 |
JPH0264275A (ja) * | 1988-05-25 | 1990-03-05 | Nippon Soken Inc | 可変容量式斜板型圧縮機 |
JPH05126029A (ja) * | 1991-10-31 | 1993-05-21 | Toyota Autom Loom Works Ltd | 可変容量ピストンポンプ |
US5226349A (en) * | 1992-07-15 | 1993-07-13 | Eaton Corporation | Variable displacement hydrostatic pump and improved gain control thereof |
DE19749727C2 (de) * | 1997-11-11 | 2001-03-08 | Obrist Engineering Gmbh Lusten | Hubkolbenmaschine mit Schwenkscheibengetriebe |
-
1999
- 1999-08-18 DE DE19939131A patent/DE19939131A1/de not_active Withdrawn
-
2000
- 2000-08-18 DE DE50004444T patent/DE50004444D1/de not_active Expired - Lifetime
- 2000-08-18 JP JP2001517056A patent/JP2003507627A/ja active Pending
- 2000-08-18 AU AU76477/00A patent/AU7647700A/en not_active Abandoned
- 2000-08-18 US US10/049,690 patent/US6957604B1/en not_active Expired - Fee Related
- 2000-08-18 EP EP00965884A patent/EP1206640B1/de not_active Expired - Lifetime
- 2000-08-18 WO PCT/EP2000/008084 patent/WO2001012989A1/de active Search and Examination
Non-Patent Citations (1)
Title |
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See references of WO0112989A1 * |
Also Published As
Publication number | Publication date |
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EP1206640B1 (de) | 2003-11-12 |
DE50004444D1 (de) | 2003-12-18 |
WO2001012989A1 (de) | 2001-02-22 |
AU7647700A (en) | 2001-03-13 |
US6957604B1 (en) | 2005-10-25 |
DE19939131A1 (de) | 2001-03-08 |
JP2003507627A (ja) | 2003-02-25 |
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