EP0739450B1 - Dichtungsanordnung an einer kolben-zylinder-einheit - Google Patents

Dichtungsanordnung an einer kolben-zylinder-einheit Download PDF

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Publication number
EP0739450B1
EP0739450B1 EP95935791A EP95935791A EP0739450B1 EP 0739450 B1 EP0739450 B1 EP 0739450B1 EP 95935791 A EP95935791 A EP 95935791A EP 95935791 A EP95935791 A EP 95935791A EP 0739450 B1 EP0739450 B1 EP 0739450B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
central axis
guides
housing
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
EP95935791A
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German (de)
English (en)
French (fr)
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EP0739450A1 (de
Inventor
Anton Steiger
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Cleanergy AB
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Steiger Anton
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Filing date
Publication date
Application filed by Steiger Anton filed Critical Steiger Anton
Publication of EP0739450A1 publication Critical patent/EP0739450A1/de
Application granted granted Critical
Publication of EP0739450B1 publication Critical patent/EP0739450B1/de
Anticipated expiration legal-status Critical
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    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids

Definitions

  • the invention relates to a sealing arrangement on a piston-cylinder unit, with one in a cylinder with one Cylinder liner longitudinally movable in the direction of a central axis Piston, with a piston skirt and a non-contact Gap seal between cylinder liner and piston skirt for sealing a liquid under pressure or gaseous medium, the piston-cylinder unit is installed in a housing.
  • Sealing arrangements of this type take place in a known manner Use with compressors, servo motors, volumetric flasks or Stirling free-piston engines, which are equipped with a gaseous, or in the case of servomotors or volumetric pistons also interact with liquid medium. Special problems now occur wherever the piston-cylinder unit both sliding friction-free and lubricant-free to be operated. For example, with oxygen compressors, or compressors for the food industry the case.
  • Known compressors of this type have a piston-cylinder unit, in which the Seal between piston and cylinder by means of a labyrinth seal is formed. The piston must be in the cylinder as centrally as possible to avoid touching the piston skirt to avoid on the cylinder wall and corresponding To prevent damage or seizure.
  • the guidance of the piston according to the invention ensures precise guidance of the translatory movements of the piston along the central axis of the cylinder and prevents deviating Movements perpendicular to this central axis.
  • connection of the cylinder to the machine housing is also done via a conical centering, or over several elastic brackets. At least three brackets are attached to the housing, whereby elastic tongues, over a lateral surface of a housing part of the cylinder, the radial positioning and thus centering of the cylinder determine.
  • elastic Tongues When the cylinder is not assembled and housing define holding surfaces on the elastic Tongues have an inner diameter which is smaller than the outer diameter of the lateral surface on the housing part of the Cylinders.
  • the different Components have the same possible thermal Strains at the same temperatures, the linear Thermal expansion coefficient at least by a factor of 4 should be smaller than that of unalloyed steel, or Iron. This ensures that in the event of temperature differences practically no additional between piston and cylinder Changes in the sealing gap occur.
  • this embodiment also has the other one Advantage that pistons and cylinders are practical at the beginning a Passitz can be assembled and by appropriate Shrink the component from sintered graphite, or with the Nickel graphite layer, i.e. the piston skirt or the cylinder liner, ground in, and the sealing gap by running in is trained. This possibility can be used if minimal sealing gaps are required, and the correspondingly high costs for breaking in and subsequent removal of the abrasion can be accepted.
  • sintered graphite or coatings of nickel graphite other materials can also be used which have the same thermal properties and have the same emergency running properties. The mentioned However, materials prove to be particularly suitable.
  • each of the two spaced guides several plate-shaped spring elements.
  • the proposed one Arrangement of the guides with the spring elements provides the Advantage that the piston, which oscillating linear movements centered exactly on its central axis and to be led.
  • the guides have no parts move against each other and subject to sliding wear are.
  • the piston is guided through the two guides and centered that it is non-contact with the cylinder can perform a purely axial relative movement. This e.g. in a lubricant-free oxygen processor, or at a lubricant-free piston of a Stirling free-piston engine.
  • the spring elements of the individual guides are in arranged on a plane which is approximately perpendicular to the central axis of the oscillating moving machine element stands.
  • the main spring parts are on this level, which are plate-shaped. This arrangement of Main spring parts allows a calculation of the movement and Spring data in a known manner, so that the movements of the machine element can be determined exactly.
  • the outer area of the long main spring parts are shorter auxiliary spring parts arranged, at right angles to the main spring parts, so that these auxiliary spring parts approximately parallel to Central axis run.
  • the connection of the auxiliary spring parts with the main spring parts via an additional connecting element, which with appropriate fasteners for the fixed connection of the ends of the main and auxiliary spring parts Is provided.
  • each spring element from several individual spring parts allows adaptation to different Requirements and brings the significant advantage with the fact that no parts of the spring elements during manufacture deformed, for example, must be bent.
  • the plate-like design of the individual spring element parts allows precise processing to the desired at any time Dimensions, e.g. by grinding too.
  • the main and the Auxiliary spring parts are normally flat plates.
  • each guide expediently arranged centrally symmetrically, so that from the central axis in the plane of the guide four, extend six or more spring element parts radially outwards. Odd numbers of spring element parts in the plane the tour is possible, each expediently includes Spring element, however, a main spring part, which itself extends symmetrically on both sides of the central axis. Thereby, that between the spring elements, which lie in one plane, the same angles are included, results the advantage that the machine element on the central axis is centered exactly symmetrically.
  • the dimensions of the long main spring parts and the short ones Auxiliary spring parts are chosen in a known manner so that the rigidity of the two guides that guide the piston, across the central axis at least by the factor 100 is larger than in the direction of the central axis.
  • Depends on the desired precision in the area of the sealing gap and the lateral forces that occur are guides with a Stiffness ratio of 500 and more used.
  • the rigidity or the movement paths by adapting the individual spring element parts can be changed.
  • the stiffness ratio leaves not only by changing the dimensions, for example of the plate-shaped spring parts change, but also in that at least two auxiliary spring parts or main spring parts spaced parallel to each other, or the auxiliary as well as the main spring part so formed are. If you do not want to change the spring constant, so in a tour in two at a distance from each other arranged levels two groups of plate-shaped spring elements be arranged. This leads to an increase in Load capacity of the corresponding guide with approximately the same Stiffness ratio. With all these different Arrangements and embodiments can always the same basic elements of main spring parts, auxiliary spring parts and fasteners are used so that the Calculation bases are simplified, and so is manufacturing the individual parts is made considerably easier.
  • the main spring part of the individual spring elements formed in one or two parts can be. If the guide is arranged at the end of an axis, it can be advantageous to make the main spring parts in one piece train, since they then with the help of a central connecting element can be connected to the axis. Becomes however, the guide somewhere in the axis area of the machine element arranged, it is often useful to the main spring parts run in two parts, and then against the central axis directed inner ends of the main spring parts by appropriate fastening devices with the axis connect to.
  • the Seal arrangement according to the invention can be formed Guide the pistons in a cylinder so precisely that a lubricant-free one Operation is enabled, and yet sealing gaps between piston and cylinder of minimal dimensions become possible.
  • the piston is guided exactly along the central axis, and disturbing movement deviations are avoided.
  • the piston or the piston rod a free piston engine, e.g. a Stirling engine without Use lubricant in the cylinder, namely the working and displacement pistons. Pollution of the pressure medium due to abrasion or lubricant residues completely avoided.
  • the inventive Sealing arrangement requires no lubricant and provides also make sure that there is no abrasion in the area during operation of the sealing gap arises.
  • the compressor 1 shows a longitudinal section through a compressor 1, only the upper part is shown, but the lower part is centrally symmetrical is the same.
  • the compressor 1 has an electric drive in a housing 5, which consists of a fixed magnetic coil 10 and a longitudinally movable Anchor 11 exists.
  • the armature 11 is with a piston rod 6 connected, the piston rod 6 and armature 11 the Have common central axis 2 and in the direction of this Central axis 2 are translationally movable.
  • the piston rod 6 is supported on two guides 8 and 9 and exactly centered guided, these two guides 8 and 9 with Are spaced from each other.
  • a piston 7 At the front end 16 of the Piston rod 6 is a piston 7 with a piston skirt 13 attached.
  • This piston 7 is from a cylinder liner 4 surround which is part of a cylinder 3.
  • the cylinder 3 is in turn connected to the housing 5 and forms part of the same.
  • the cylinder 3 includes one Working space 18 for the pressure medium and has in a known Show intake valves 19 and exhaust valves 20.
  • Between the piston skirt 13 and the cylinder liner 4 is a gap seal 12 formed, the piston 7 without contact is guided in the cylinder liner 4.
  • This configuration A non-contact gap seal is achieved by the inventive Design and arrangement of the two guides 8, 9 enables. In the example shown, it is for example possible with a piston diameter of 45 mm Form a gap width of 0.01 mm on the gap seal.
  • the piston 7 is assembled from several parts.
  • the piston rod 6 has a plate-shaped flange 21, which forms the holder for the cylindrical piston jacket 13.
  • a second plate-shaped flange 22 interacts with the other end of the piston jacket 13 and is connected to the front end 16 of the piston rod 6 via an elastic clamping element 23 and a clamping nut 24.
  • the two plate-shaped flanges 21, 22 have conical edge regions 25 and 25 '.
  • the two end faces of the piston skirt 13 are also conical.
  • the conical edge region 25 of the plate-shaped flange 21 centers and guides the piston jacket 13 exactly centrally to the central axis 2.
  • the elastic clamping element 23 generates a constant clamping force in the direction of the central axis 2 and ensures that even with length changes due to temperature changes, the piston jacket 13 is always exactly centered between the two plate-shaped flanges 21, 22 is clamped.
  • the elastic clamping element 23 consists of a plate spring.
  • the piston skirt 13 is made of sintered graphite in the example shown, and the clamping between the two conical edge regions 25 and 25 'of the plate-shaped flanges 21, 22 ensures a permanent pressure preload and secure mounting for the sintered body 13.
  • the for the piston skirt 13 and the cylinder liner 4 materials used have a linear thermal expansion coefficient, which is at least four times smaller than that of unalloyed steel, the latter being 11.1x10 -6 per degree Kelvin.
  • a high-alloy nickel steel with eg 36% nickel can have a linear expansion coefficient of 0.9x10 -6 per degree Kelvin.
  • the cylinder liner 4 is elastic on the one hand Clamping element 26 and fastening element 27, and on the other hand supported by a conical centering 28 in the cylinder 3 and centered.
  • the elastic tensioning element 26 also exists from a disc spring, but can also from others known elastic elements can be formed.
  • the cylinder liner In case of Changes in length of the cylinder liner 4 due to temperature differences the cylinder liner is always in the direction of the central axis pressed against the conical centering 28. Thereby it is also ensured on the cylinder liner that this is always free of play and no deviations occur with respect to the central axis 2.
  • a conical centering 29 is formed.
  • the connection between cylinder 3 and housing 5 does not take place Connection elements 30 shown in the area of the conical Centering 29. Since the conical centering 29 both the housing 5, as well as the cylinder 3, from the same Material, there are no thermal ones Axial movements to be expected.
  • the conical centers between the individual components of the cylinder 3 and Pistons 7 ensure that the individual components are accurate be assembled and formed centrally to the central axis 2 thus the prerequisites for training the desired minimal gap at the gap seal 12.
  • the first guide is 8 arranged in the immediate vicinity of the piston 7 and the second Guide 9 at the rear end 17 of the piston rod 6.
  • This Guides 8, 9 are aligned on two levels 32, 33, which are approximately at right angles to the central axis 2.
  • Each of the two guides 8, 9 consists of several spring elements 34, which can best be seen from FIG. 3.
  • This Spring elements 34 each consist of a two-part long Main spring part 35 and two short auxiliary spring parts 36, which at the outer ends 37 of the main spring part 35 rigidly attached and connected to the housing 5.
  • the Auxiliary spring parts 36 are approximately at right angles to the main spring part 35 arranged and thus run approximately parallel to Central axis 2.
  • the rigid connection between the outer Ends 37 of the main spring part 35 and the auxiliary spring parts 36 is produced by means of connecting elements 38.
  • the spring elements 34 are on the one hand via the auxiliary spring parts 36 and Fasteners 39 fixed to the housing 5, and on the other hand via the main spring parts 35, and the flanges 40 and Clamping elements 41 with the oscillating piston rod 6 and the piston 7 firmly connected.
  • the two guides 8, 9 are exactly the same, but as shown in Fig. 1 is recognizable, arranged mirror-inverted.
  • the leadership and Centering the piston 7 is so precise that between the piston 7 and the cylinder liner 4 only a very thin one Gap 12 is necessary. This can seal the piston chamber 18 take place through a contactless gap seal 12, and no seals are necessary and available, which are abraded or worn by relative movements would.
  • each guide 8, 9 formed spring system is designed so that the Stiffness in the direction of the planes 32, 33 at least around the Factor 100 is greater than its stiffness in the direction the central axis 2.
  • the rigidity across the central axis 2 is approx. 200 times higher than in the direction of the central axis 2.
  • spring parts made of hardened spring steel with a thickness of 1.18 mm.
  • the main spring parts 35 have a length of approx. 13 cm and the auxiliary spring parts a length of approx. 2.2 cm. This enables a piston stroke of 20 mm.
  • the piston diameter is 45 mm and the oscillation frequency is 50 Vibrations per second.
  • Fig. 2 shows another embodiment of the piston 7, the remaining parts of the compressor 1 are configured identically, as in Fig. 1.
  • cylinder 3 is again a cylinder liner 4 used, which is made of a high-nickel steel, manufactured in the example shown of the type 36% Ni-Alloy is.
  • the centering and clamping of the cylinder liner 4 in Cylinder 3 also takes place here via the conical centering 28, and the elastic clamping element 26, and the fastening elements 27.
  • the piston 7 also consists of several Divide.
  • a piston skirt 44 is between one of the Piston rod 6 outgoing plate-shaped flange 42 and clamped a second plate-shaped flange 43.
  • the Tension is achieved by the elastic tensioning element 23 in the Form a plate spring, and the clamping nut 24 is generated.
  • the piston skirt 44 consists of high nickel steel.
  • On the outer surface 45 of this piston skirt 44 is a coating 46 made of suitable nickel graphite angry, e.g. in the composition of 15-25% by weight graphite and 75-85% nickel.
  • This coating 46 forms the interface of the gap seal 12 the cylinder liner 4.
  • the conical edge areas 47 and 47 ' point at both ends of the cylindrical piston skirt 44 here an inclination, which in relation to the piston skirt 44 causes a tension. This is because of the chosen one Material steel permissible and advantageous.
  • the dimensions of the piston skirt 13, or 44 and the cylinder liner 4 from the beginning chosen so that when assembling the components in the areas the gap seal 12 forms the smallest possible gap becomes.
  • the diameter of the piston skirt 44 and the Select cylinder liner 4 in which a very uniform circular cross-section is requested, and at the same time the thickness the gap of the gap seal 12 should be absolutely minimal, it is possible to the diameter of the piston skirt 44 and the Select cylinder liner 4 so that almost a Passitz or a relatively strict sliding fit arises.
  • the sintered graphite material of the piston jacket can shrink 13, or the coating 46 rubbed against the piston skirt 44 and thereby creates a very narrow gap seal 12 will.
  • FIG. 3 shows a guide 8, 9 as shown in FIG. 1 or 2 is used as a partial view in the direction of the central axis 2. It can be seen that in each of the levels 32 or 33 two spring elements 34 are arranged, between the Spring elements 34, seen in the circumferential direction, are the same Angles are included. Each of the spring elements 34 is made thereby from two main spring parts 35, two auxiliary spring parts 36 and two connecting elements 38. The connecting elements 38 turned ends of the short auxiliary spring parts 36 are fasteners 39 on the housing 5 of the compressor 1 rigidly attached.
  • the piston rod 6, which is moved axially oscillating has a flange 40 on, and a clamping element 41, which for connection the inner ends 53 of the main spring parts 35 with the flange 40 serves.
  • the short auxiliary spring parts 36 are made of flat, rectangular plates formed.
  • the main spring parts 35 are trapezoidal and wider towards the outer end 37 than at the inner end 53.
  • the shape of the spring parts 35, 36 is in a known manner by the desired spring characteristics certainly.
  • Ribs 55 are arranged on the flange 40, which stop surfaces 56 for the inner ends 53 of the Form main spring parts 35. Through these ribs 55 and the corresponding stop surfaces 56, and the corresponding Shape of the inner ends 53 of the main spring parts 35, their position relative to the piston rod 6 is precisely determined. In this position, the inner ends 53 of the Main spring parts 35 with the help of the clamping element 41 and Screws 58 clamped and held.
  • Fig. 4 shows a guide 50, which in principle the arrangements 1 and 2 corresponds. However, it is on each guide 50 two spaced apart Levels 51, 52 are present, in each of which spring elements 34 are arranged are. The two levels 51, 52 run parallel to each other and approximately at right angles to the central axis 2 the piston rod 6. As described and shown for Fig. 3 there are two in each of the levels 51, 52 Spring elements 34 are arranged, in which between the spring elements 34, seen in the circumferential direction, the same angle are included.
  • the flange 40 and Clamping element 41 are two centering plates on piston rod 6 here 54 and a spacer 57 arranged.
  • the centering plates 54 have the ribs 55 with the stop faces 56 on.
  • the inner ends 53 of the pair arranged spring parts 35 are between a centering plate 54 and the flange 40, or the clamping element 41 clamped.
  • the clamping force is generated by means of the screws 58.
  • This arrangement of a guide shown in Fig. 4 50 with two spring levels 51, 52 can be larger longitudinal and Take up lateral forces. However, it leaves the same Movements to, such as that shown and described in Fig. 1 simple execution. Freedom in particular the linearly oscillating movement of the piston rod 6 and the associated piston 7 in the direction of arrows 31 guaranteed.
  • the two-part main spring parts 35 is particular useful where on the central axis 2 before and 50 further machine elements arranged behind the guide which are a plug-in of continuous one-piece Do not allow spring elements 34 on the piston rod 6. in the but also the production of the main spring parts 35 facilitated because they have smaller dimensions, and if necessary, individual parts of a spring element 34 can be replaced are. But it is quite possible and in the sense of the invention, e.g. in plane 33 in Fig. 1, one-piece Use main spring parts 35. These have a central Bore on and can be pushed onto the piston rod 6 and then clamped.
  • each spring element 34 shows a further embodiment of an inventive one Guide for a sealing arrangement shown in each spring element 34 both the main spring parts 35, as well as the auxiliary spring parts 36 in pairs in parallel and are arranged at a distance from each other.
  • the connection of the inner ends 53 of the main spring parts 35 with the flange 40 the piston rod 6 takes place in the same way as for FIG. 3, or 4 described.
  • the ends of the auxiliary spring parts 36 are designed accordingly and has contact surfaces for the paired arrangement of the parallel springs.
  • For connecting the auxiliary spring parts 36 with the housing 5 are corresponding fastening and Clamping elements 60 available.
  • the organization of the leadership with parallel springs 35 leads to one in both longitudinal directions of movement symmetrical spring characteristic with accordingly more favorable voltage curve.
  • the one shown in Fig. 1 simple spring points because of the bending and force relationships in the clamping areas for the forward or Backward movement of the machine element is not the same Spring characteristic. In relation to the zero point the positive and negative characteristics of the single spring not symmetrical.
  • each of the levels 32, 33, or 51, 52 it turns out to be useful in each of the levels 32, 33, or 51, 52 to arrange at least two spring elements 34, which are centrally symmetrical to the central axis 2 and their orientation axes, seen in the circumferential direction, Cross at an angle of 90 °.
  • the spring elements can also be at an angle of 60 ° or 45 ° to each other. Accordingly then in the area of the oscillating piston 7 and Housing 5 more attachment and positioning points provided.
  • the housing part 61 of the cylinder 3 has a cylindrical Shell surface 62, which is exactly centric to the central axis 2 is formed. At least 5 are on the housing three, in the example shown four elastic mounts 65 arranged. These four brackets 65 are radial each 90 ° offset and fastening parts 67 and known fasteners 68, e.g. Screws, attached to the housing 5. Each bracket 65 has an elastic tongue 69 on the free end of a holding surface 64 is arranged. To the Holding surface 64 closes an outwardly diverging surface oblique guide surface 63.
  • the housing 5 is in the further a stop surface 66 is arranged, which in a radial plane to the central axis 2 and the support and mounting surface forms for the housing part 61 of the cylinder 3.
  • the holding surfaces 64 of the marked brackets 65 Before assembling the cylinder 3 with the housing 5 machined the holding surfaces 64 of the marked brackets 65 so that they limit an inside diameter which is smaller than the outer diameter of the outer surface 63 am Housing part 61. If the housing part 61 of the cylinder 3 in Pushed in the direction of the central axis 2 between the brackets 65, the tongues 69 are elastically deformed, and between the outer surface 62 on the cylinder 3 and the holding surfaces 64 on the brackets 65 becomes a backlash-free fit educated.
  • the outer surface 62 on an annular collar, or in a groove on the opposite the housing 5 facing end face 70 of the housing part 61 to arrange.
  • the outer surface 62 is then an outer surface or designed as an inner surface.
  • the brackets 65 are then arranged accordingly in the interior of the housing 5, and the holding surfaces 64 on the elastic tongues 69 are then dependent on the orientation of the lateral surface 61 directed inwards or outwards.
  • the elastic tongues 69 holding surfaces 64 arranged on the outside have, which in a collar or a groove on the housing part 61 engage, the initial diameter is not in assembled condition larger than the diameter of the Shell surface 62 on the housing part 61 of the cylinder 3. Die play-free leadership is, as described above, at guaranteed each embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP95935791A 1994-11-14 1995-11-09 Dichtungsanordnung an einer kolben-zylinder-einheit Expired - Lifetime EP0739450B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH339294 1994-11-14
CH3392/94 1994-11-14
PCT/CH1995/000259 WO1996015368A1 (de) 1994-11-14 1995-11-09 Dichtungsanordnung an einer kolben-zylinder-einheit

Publications (2)

Publication Number Publication Date
EP0739450A1 EP0739450A1 (de) 1996-10-30
EP0739450B1 true EP0739450B1 (de) 1998-06-03

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95935791A Expired - Lifetime EP0739450B1 (de) 1994-11-14 1995-11-09 Dichtungsanordnung an einer kolben-zylinder-einheit

Country Status (10)

Country Link
US (1) US5826491A (ja)
EP (1) EP0739450B1 (ja)
JP (1) JP3512192B2 (ja)
CN (1) CN1071845C (ja)
AT (1) ATE166949T1 (ja)
CA (1) CA2181169A1 (ja)
DE (1) DE59502408D1 (ja)
DK (1) DK0739450T3 (ja)
ES (1) ES2118631T3 (ja)
WO (1) WO1996015368A1 (ja)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1019858C2 (nl) * 2002-01-29 2003-09-08 Thales Nederland Bv De onderhavige uitvinding heeft in het algemeen betrekking op cryogene koelers en in het bijzonder op de werkwijze voor de assemblage van de compressor van cryogene koelers en op middelen voor het in positie houden van de zuiger die in dergelijke cryogene koelers wordt gebruikt.
US8490414B2 (en) * 2007-05-16 2013-07-23 Raytheon Company Cryocooler with moving piston and moving cylinder
US9856866B2 (en) 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles
CN103635662B (zh) * 2011-07-21 2016-06-22 马勒国际有限公司 凸轮轴及相应的制造方法
JP6082310B2 (ja) * 2013-04-26 2017-02-15 株式会社神戸製鋼所 往復動圧縮機
CN203770066U (zh) * 2013-06-28 2014-08-13 Lg电子株式会社 线性压缩机
JP6570359B2 (ja) * 2015-07-24 2019-09-04 三輪精機株式会社 エアコンプレッサ
US10422329B2 (en) 2017-08-14 2019-09-24 Raytheon Company Push-pull compressor having ultra-high efficiency for cryocoolers or other systems

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US166592A (en) * 1875-08-10 Improvement in pistons for steam-engines
US2888879A (en) * 1953-09-30 1959-06-02 Union Carbide Corp Immersion pump for liquefied gases
US2856249A (en) * 1955-01-11 1958-10-14 Maquinaria Petrolifera S A High-pressure pump liner and packing
DE1133856B (de) * 1958-05-19 1962-07-26 Carl Lott Kolben fuer Luftkompressoren
US3261598A (en) * 1964-07-02 1966-07-19 Fairchild Hiller Corp Spring mechanism
US3727900A (en) * 1971-03-09 1973-04-17 Fema Corp Adjustable non-linear spring and spring suspension system
US4044655A (en) * 1975-10-01 1977-08-30 Kennametal Inc. High pressure plunger and method of manufacture
SE408324B (sv) * 1976-10-15 1979-06-05 Sandvik Ab Kolv foretredesvis for hogtryckskompressorer
EP0028144A1 (en) * 1979-10-29 1981-05-06 Gordon Davey Support system for a reciprocating compressor piston
DE3315556C1 (de) * 1983-04-29 1984-11-29 Goetze Ag, 5093 Burscheid Verschleissfeste Beschichtung
US5318412A (en) * 1992-04-03 1994-06-07 General Electric Company Flexible suspension for an oil free linear motor compressor

Also Published As

Publication number Publication date
DE59502408D1 (de) 1998-07-09
US5826491A (en) 1998-10-27
ATE166949T1 (de) 1998-06-15
DK0739450T3 (da) 1999-02-01
EP0739450A1 (de) 1996-10-30
CA2181169A1 (en) 1996-05-23
JPH09507894A (ja) 1997-08-12
AU691351B2 (en) 1998-05-14
JP3512192B2 (ja) 2004-03-29
AU3769295A (en) 1996-06-06
WO1996015368A1 (de) 1996-05-23
ES2118631T3 (es) 1998-09-16
CN1138890A (zh) 1996-12-25
CN1071845C (zh) 2001-09-26

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