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
  • 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 a piston which is longitudinally movable in a cylinder with a cylinder liner in the direction of a central axis, with a piston jacket and a non-contact gap seal between the cylinder liner and piston jacket for sealing a pressurized liquid or gaseous medium, the piston-cylinder unit being installed in a housing.
• Sealing arrangements of this type are used in a known manner in compressors, servomotors, volumetric pistons or Stirling free-piston engines, which interact with a gaseous medium or, in the case of servomotors or volumetric pistons, under certain circumstances also liquid medium.
• Known compressors of this type have a piston-cylinder unit, in which the seal between the piston and the cylinder is formed by a labyrinth seal. The piston in the cylinder must be guided as centrally as possible in order to avoid touching the piston jacket on the cylinder wall and to prevent corresponding damage or seizing.
• the piston In order to meet these guide conditions, the piston is provided with a piston rod which is supported and guided in a crosshead.
• This crosshead is in turn known Driven by a rotating crankshaft via a crank rod. That way . generates the necessary oscillating movements of the piston, the desired guidance of the piston in the cylinder being ensured by the crosshead.
• Corresponding compressors are described in the specialist book “Piston Compressor” by KH kuttner, Springer Ver ⁇ lag 1991, pages 236 and the following.
• a disadvantage of this embodiment is that no very narrow gaps can be provided between the piston skirt and the cylinder wall, but rather a relatively large amount of play is necessary.
• 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.
• This has the advantage that there is a minimal sealing gap between the piston skirt and the cylinder wall. can be set, and thus the need for the arrangement of labyrinth seals is eliminated. There is also no risk that the cross-section of the sealing gap assumes a crescent-shaped shape, thereby reducing the sealability of the sealing arrangement.
• Conical centering on the components of the piston and of the cylinder results in the advantage that these parts are aligned exactly on the same axis and are held in this position. This ensures that the piston and the cylinder do not touch at any point during the course of the movement, and that the annular gap remains constant during the entire operating time.
• the cylinder is also connected to the machine housing via a conical centering or via a plurality of elastic holders. At least three brackets are fastened to the housing, elastic tongues, via a lateral surface of a housing part of the cylinder, determining the radial positioning and thus centering of the cylinder.
• holding surfaces on the elastic tongues define an inner diameter which is smaller than the outer diameter of the outer surface on the housing part of the cylinder.
• the lateral surface on which the elastic holders rest can be designed as an outer surface or as an inner surface, and the holding surfaces on the holders are correspondingly directed inwards or outwards.
• Another advantage of the arrangement is that the components of the piston and the cylinder, namely the piston skirt and the cylinder liner, which form the boundary surfaces of the gap of the gap seal, consist of a material which has a very low thermal expansion coefficient. efficient.
• Such materials are known per se, and in the present case high-nickel steel or sintered graphite or coal are selected.
• the various components have the same possible thermal expansions at the same temperatures, the linear thermal expansion coefficient being at least 4 times smaller than that of unalloyed steel or iron. This ensures that there are practically no additional changes in the sealing gap when there are temperature differences between the piston and cylinder.
• this embodiment also has the further advantage that pistons and cylinders are practically assembled at the beginning with a Passitz and the component made of sintered graphite or with the nickel graphite layer, i.e. the piston jacket or the cylinder liner, is ground in by appropriate running-in, and the Sealing gap is formed by running in.
• This option can be used if the smallest possible sealing gaps are desired and the correspondingly high costs for running in and then removing the abrasion can be accepted.
• sintered graphite or coatings of nickel graphite other materials can be used which have the same thermal properties and the same emergency running properties. However, the materials mentioned prove to be particularly suitable.
• the individual components are assembled using elastic tensioning elements, which in Act in the direction of the axis of the conical centerings or the central axis.
• the interaction of the conical centerings and the clamping forces results in the advantage that even with temperature differences between the components in the radial direction there is no additional play, since the components in the conical guides always remain pressed together in the axial direction. This ensures compliance with the concentricity between the piston and cylinder.
• each of the two spaced-apart guides consists of several plate-shaped spring elements.
• the proposed arrangement of the guides with the spring elements has the advantage that the piston, which carries out oscillating linear movements, is centered and guided precisely on its central axis.
• the guides have no parts that move against each other and are subject to sliding wear.
• the piston is guided and centered by the two guides so that it can perform a purely axial relative movement without contact with the cylinder. This can be done, for example, in a lubricant-free oxygen processor or on a lubricant-free piston in a Stirling free-piston engine.
• the spring elements of the individual guides are arranged in a plane which is approximately at right angles to the central axis of the oscillating machine element stands.
• the main spring parts which are plate-shaped, are located in this plane. This arrangement of the main spring parts allows the movement and spring data to be calculated in a known manner, so that the movements of the machine element can also be precisely determined.
• Shorter auxiliary spring parts are arranged in the outer region of the long main spring parts, at right angles to the main spring parts, so that these auxiliary spring parts run approximately parallel to the central axis.
• the auxiliary spring parts are connected to the main spring parts via an additional connecting element, which is equipped with corresponding fastening means for the fixed connection of the ends of the main and auxiliary spring parts.
• this additional connecting element between each auxiliary spring part and the associated main spring part results in the advantage that the spring element is rigid in the angled area and the deformations of the spring elements only take place in the plate-shaped areas.
• the individual auxiliary spring parts and main spring parts, as well as the connecting elements can be manufactured very precisely in accordance with the technical specifications so that they have the desired values during installation, both with regard to dimensional accuracy and strength values. This exact correspondence with specified masses and strength values can be achieved with conventional manufacturing methods, since the spring parts and the connecting elements have simple shapes.
• the individual components can also be easily checked and parts that deviate from the standard data can be easily eliminated.
• each spring element from several individual spring parts enables adaptation to different requirements and has the considerable advantage that no parts of the spring elements have to be deformed, for example bent, during manufacture.
• the plate-like design of the individual spring element parts allows precise machining to the desired dimensions at any time, for example by grinding.
• the main and auxiliary spring parts are normally flat plates.
• the plate-shaped spring elements of each guide are expediently arranged centrally symmetrically, so that four, six or more spring element parts extend radially outward from the central axis in the plane of the guide. Odd numbers of spring element parts in the plane of the guide are possible, but expediently each spring element comprises a main spring part which extends symmetrically on both sides of the central axis. The fact that angles of equal size are included between the spring elements lying in one plane results in the advantage that the machine element is centered exactly symmetrically on the central axis.
• the dimensions of the long main spring parts and the short auxiliary spring parts are selected in a known manner so that the stiffness of the two guides, which guide the piston, is at least 100 times greater in the direction of the central axis than transverse to the central axis.
• guides with a rigidity ratio of 500 and more are used.
• the force absorption, the rigidity or the movement paths can be changed by adapting the individual spring element parts.
• the stiffness ratio can be changed, for example, not only by changing the dimensions of the plate-shaped spring parts, but also by arranging at least two auxiliary spring parts or main spring parts at a distance parallel to one another, or by designing the auxiliary and main spring parts in this way. If no change in the spring constant is desired, two groups of plate-shaped spring elements can be arranged in a guide in two planes spaced apart from one another. This leads to an increase in the load-bearing capacity of the corresponding guide with an approximately constant stiffness ratio. With all of these Different arrangements and embodiments can always use the same basic elements of main spring parts, auxiliary spring parts and connecting elements, so that the calculation bases are simplified and the manufacture of the individual parts is also made considerably easier.
• the main spring part of the individual spring elements can be formed in one or two parts. If the guide is arranged at the end of an axle, it can be advantageous to form the main spring parts in one piece, since they can then be connected to the axle with the aid of a central connecting element. However, if the guide is arranged somewhere in the axis area of the machine element, it is often expedient to design the main spring parts in two parts and then to connect the inner ends of the main spring parts directed against the central axis to the axis by means of appropriate fastening devices.
• pistons can be guided in a cylinder so precisely that lubricant-free operation is possible, and sealing gaps between the piston and cylinder of minimal dimensions are nevertheless possible.
• two identical guides which are arranged at a distance from each other, the piston is guided exactly along the central axis and disturbing movement deviations are avoided.
• This makes it possible, for example, to guide the piston or the piston rod of a free-piston engine, for example a Stirling engine, without the use of lubricant in the cylinder, specifically the working piston as well as the displacement piston. Contamination of the pressure medium by abrasion or lubricant residues is completely avoided.
• the same also applies to versions of oxygen compressors or to compressors with other pressure media which must not be contaminated by lubricants or abrasion.
• the inventive Sealing arrangement requires no lubricant and also ensures that no wear occurs in the area of the sealing gap during operation.
• FIG. 1 shows a longitudinal section through a schematically illustrated compressor, with an electromagnetic drive
• FIG. 2 shows a longitudinal section through the piston-cylinder area of the compressor according to FIG. 1, with a coated piston
• FIG. 3 shows a partial front view of one of the guides for the piston shown in FIGS. 1 and 2
• FIG. 4 shows a section from a guide with double spring elements and two-part main spring parts
• FIG. 5 shows a section from a guide with two-part main spring parts and paired main and auxiliary spring parts
• FIG. 6 shows a section from FIG. 1, with elastic
• FIG. 7 is a view of the arrangement of FIG. 6 in the direction of the central axis, with a partial section through the cylinder and piston.
• the compressor 1 shows a longitudinal section through a compressor 1, only the upper part being shown, but the lower part having the same central symmetry.
• the compressor 1 has an electrical drive in a housing 5, which consists of a fixed magnetic coil 10 and a longitudinally movable armature 11.
• the armature 11 is connected to a piston rod 6, the piston rod 6 and armature 11 having the common central axis 2 and being translationally movable in the direction of this central axis 2.
• the piston rod 6 is supported on two guides 8 and 9 and exactly trisch guided, these two guides 8 and 9 are arranged at a distance from each other.
• a piston 7 is fastened with a piston skirt 13. This piston 7 is surrounded by a cylinder liner 4, 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 comprises a working space 18 for the pressure medium and has inlet valves 19 and outlet valves 20 in a known manner.
• a gap seal 12 is formed between the piston skirt 13 and the cylinder liner 4, the piston 7 being guided in the cylinder liner 4 without contact.
• This configuration of a contact-free gap seal is made possible by the configuration and arrangement of the two guides 8, 9 according to the invention. In the example shown, it is possible, for example, to form a gap width of 0.01 mm on the gap seal with a piston diameter of 45 mm.
• 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 ', respectively.
• 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 the piston jacket 13 is always exactly centered even in the event of changes in length due to temperature changes is clamped between the two plate-shaped flanges 21, 22.
• the elastic tensioning element 23 consists of a plate spring.
• the piston skirt 13 is made of sintered graphite, and the clamping between the two conical edge regions 25 and 25 'of the plate-shaped flanges 21, 22 ensures a permanent one
• the materials used for the piston skirt 13 and the cylinder liner 4 have a linear thermal expansion coefficient which is at least four times smaller than that of unalloyed steel, the latter being 11.1x10 " per degree Kelvin
• a high-alloy nickel steel with, for example, 36% nickel can have a linear expansion coefficient of 0.9 ⁇ 10 0 per degree Kelvin.
• the cylinder liner 4 is elastic on the one hand
• the elastic tensioning element 26 also consists of a plate spring, but can also be formed from other known elastic elements.
• the cylinder liner In the event of changes in length of the cylinder liner 4 as a result of temperature differences, the cylinder liner is always pressed against the conical centering 28 in the direction of the central axis. This also ensures that the cylinder liner is always guided without play and that there are no deviations from the central axis 2.
• a conical centering 29 is also formed on the housing part 61 of the cylinder 3 between the cylinder 3 and the housing 5.
• the connection between cylinder 3 and housing 5 takes place via connecting elements 30 (not shown) in the region of the conical centering 29. Since in the conical centering 29 both the housing 5 and the cylinder 3 consist of the same material, no thermal axial movements are to be expected here.
• the conical centers between the individual components of the cylinder 3 and the piston 7 ensure that the individual components are joined exactly centrally to the central axis 2 and thus form the prerequisites for the formation of the desired minimum gap on the gap seal 12.
• the two guides 8 and 9 center and guide the piston rod 6 or the piston 7 such that the lateral surface 14 of the piston jacket 13 runs without contact and exactly parallel to the cylindrical surface 15 of the cylinder liner 4. This over the entire length of the translatory movements of the piston 7 in the direction of the arrows 31.
• the first guide 8 is arranged in the immediate vicinity of the piston 7 and the second guide 9 at the rear end 17 of the piston rod 6.
• These guides 8, 9 are aligned on two planes 32, 33, which are approximately at right angles to the central axis 2.
• the two planes 32, 33 and thus the two guides 8, 9 are arranged at a distance from one another in the direction of the central axis 2, this distance being determined by the storage conditions and the structural conditions of the compressor.
• Each of the two guides 8, 9 consists of several spring elements 34, which can best be seen from FIG. 3.
• These spring elements 34 each consist of a two-part long main spring part 35 and two short auxiliary spring parts 36, which are rigidly attached to the outer ends 37 of the main spring part 35 and connected to the housing 5.
• the auxiliary spring parts 36 are arranged approximately at right angles to the main spring part 35 and thus run approximately parallel to the 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 fixed to the housing 5 via the auxiliary spring parts 36 and fastening elements 39, and on the other hand via the main spring parts 35 and the flanges 40 and Clamping elements 41 are firmly connected to the oscillating piston rod 6 and the piston 7.
• the two guides 8, 9 are of exactly the same design, but, as can be seen from FIG. 1, are arranged mirror-inverted.
• the guidance and centering of the piston 7 is so precise that only a very thin gap 12 is necessary between the piston 7 and the cylinder liner 4.
• the piston chamber 18 can be sealed by means of a contactless gap seal 12, and no seals are necessary and present which would be abraded or worn by relative movements.
• the spring system formed by the spring elements 34 of each guide 8, 9 is designed in such a way that the rigidity in the direction of the planes 32, 33 is at least 100 times greater than its rigidity in the direction of the central axis 2.
• the rigidity transverse to the central axis 2 is approximately 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 are used.
• the main spring parts 35 have a length of approximately 13 cm and the auxiliary spring parts have a length of approximately 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 design of the piston 7, the remaining parts of the compressor 1 being of the same design as in FIG. 1.
• a cylinder liner 4 which is made of a high-nickel steel, in the example shown in FIG Types 36% Ni-Alloy is made.
• the centering and clamping of the cylinder liner 4 in the 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 likewise consists of several parts.
• a piston skirt 44 is between one of the Piston rod 6 outgoing plate-shaped flange 42 and a second plate-shaped flange 43 clamped.
• the clamping force is generated by the elastic clamping element 23 in the form of a plate spring, and the clamping nut 24.
• the clamping nut 24 is screwed onto the front end 16 of the piston rod 6.
• the piston skirt 44 is made of high nickel steel.
• a coating 46 made of suitable nikraphite is applied, for example in the composition of 15-25% by weight graphite and 75-85% nickel. This coating 46 forms the interface of the gap seal 12 against the cylinder liner 4.
• the conical edge regions 47 and 47 'at both ends of the cylindrical piston jacket 44 have an inclination here, which causes a tension in relation to the piston jacket 44. This is permissible and advantageous because of the steel chosen.
• the dimensions of the piston jacket 13 or 44 and the cylinder liner 4 are selected from the start so that when the components are joined together in the area of the gap seal 12 the smallest possible gap is formed.
• the diameter of the piston jacket 44 and the cylinder liner 4 it is possible for the diameter of the piston jacket 44 and the cylinder liner 4 to be so to choose that almost a Passitz or a relatively strict sliding seat arises.
• the sintered graphite material of the piston jacket 13 or the coating 46 on the piston jacket 44 can be rubbed off by careful running in, and a very narrow gap seal 12 can thereby be produced. It is also possible to exchange the material combinations between the cylinder liner 4 and the piston skirt 13.
• the exact guidance of the piston 7 via the guides 8 and 9, as well as the conical centering of the various components of the piston 7 and the cylinder 3 in any case enable the formation of a very narrow and contact-free gap seal 12, and thus the lubricant-free operation. Since the piston 7 runs in the cylinder bushing 4 without contact during normal operation, there is no abrasion, which also prevents contamination of the pressure medium.
• FIG. 3 shows a guide 8, 9, as used in FIGS. 1 or 2, as a partial view in the direction of the central axis 2. It can be seen that two spring elements 34 are arranged in each of the planes 32 and 33, the same angle being included between the spring elements 34, as seen in the circumferential direction.
• Each of the spring elements 34 consists of two main spring parts 35, two auxiliary spring parts 36 and two connecting elements 38. The ends of the short auxiliary spring parts 36 facing away from the connecting elements 38 are rigidly fastened to the housing 5 of the compressor 1 by means of fastening elements 39 .
• the piston rod 6, which is moved in an axially oscillating manner, has a flange 40 and a clamping element 41, which serves to connect the inner ends 53 of the main spring parts 35 to the flange 40.
• the short auxiliary spring parts 36 are formed from flat, rectangular plates.
• 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 determined in a known manner by the desired spring characteristics.
• Ribs 55 are arranged on the flange 40, which form stop surfaces 56 for the inner ends 53 of the main spring parts 35. Through these ribs 55 and the corresponding stop surfaces 56, as well as 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.
• FIG. 4 shows a guide 50 which corresponds in principle to the arrangements according to FIGS. 1 and 2. However, on each guide 50 there are two planes 51, 52 arranged at a distance from one another, in which each spring element 34 is arranged. The two planes 51, 52 run parallel to one another and approximately at right angles to the central axis 2 of the piston rod 6. As has been described and illustrated for FIG. 3, two spring elements 34 are also arranged in each of the planes 51, 52, at which between the spring elements 34, as seen in the circumferential direction, each include the same angle.
• centering plates 54 and a spacer 57 are arranged on the piston rod 6 here.
• the centering plates 54 have the ribs 55 with the stop surfaces 56.
• the inner ends 53 of the spring parts 35 arranged in pairs are clamped between a centering plate 54 and the flange 40 or the clamping element 41.
• the clamping force is generated by means of the screws 58.
• This arrangement of a guide 50 shown in FIG. 4 with two spring planes 51, 52 can be larger in length and length
• the embodiment of the two-part main spring parts 35 described in accordance with FIGS. 3 and 4 is particularly expedient where further machine elements are arranged on the central axis 2 in front of and behind the guide 50, which insert continuous one-piece spring elements 34 onto the piston rod 6 not allow. Furthermore, the manufacture of the main spring parts 35 is also facilitated, since they have smaller dimensions and, if necessary, individual parts of a spring element 34 can also be replaced. However, it is entirely possible and in the sense of the invention, for example in plane 33 in FIG. 1, to use one-piece main spring parts 35. These have a central Open the hole and can be pushed onto the piston rod 6 and then clamped.
• FIG. 5 shows a further embodiment of a guide according to the invention for a sealing arrangement, wherein in each spring element 34 both the main spring parts 35 and the auxiliary spring parts 36 are arranged in pairs in parallel and at a distance from one another.
• the connection of the inner ends 53 of the main spring parts 35 to the flange 40 of the piston rod 6 takes place in the same way as described for FIGS. 3 and 4.
• the connecting element 38 between the outer ends of the main spring parts 35 and the abutting ends of the auxiliary spring parts 36 is formed accordingly and has contact surfaces for the paired arrangement of the parallel springs.
• Corresponding fastening and tensioning elements 60 are provided for connecting the auxiliary spring parts 36 to the housing 5.
• the design of the guide with parallel springs 35 leads to a spring characteristic that is symmetrical in both longitudinal directions of movement with a correspondingly more favorable stress curve.
• the simple spring shown in FIG. 1 does not have the same spring characteristic because of the bending and force ratios in the clamping areas during the forward or backward movement of the machine element. In relation to the zero point, the positive and negative characteristics of the single spring are not symmetrical.
• each of the planes 32, 33 and 51, 52 at least two spring elements 34 which are designed to be centrally symmetrical with the central axis 2 and whose orientation axes are in the circumferential direction seen, cross at an angle of 90 °. If the construction conditions and the forces occurring require this, the spring elements can, however, also be arranged at an angle of 60 ° or 45 ° to one another. Accordingly, in the area of the oscillating piston 7 and Housing 5 provided more fastening and positioning points.
• the housing part 61 of the cylinder 3 has a cylindrical circumferential surface 62 which is formed exactly in the center of the central axis 2.
• At least three, in the example shown four elastic holders 65 are arranged on the housing 5. These four brackets 65 are offset radially by 90 ° each and are fastened to the housing 5 via fastening parts 67 and known fastening means 68, for example screws.
• Each holder 65 has an elastic tongue 69, on its free end a holding surface 64 is arranged.
• An outwardly diverging oblique guide surface 63 adjoins the holding surface 64.
• a stop surface 66 is also arranged on the housing 5, which lies in a radial plane to the central axis 2 and forms the support and fastening surface for the housing part 61 of the cylinder 3.
• the holding surfaces 64 of the marked holders 65 are machined in such a way that they limit an inner diameter which is smaller than the outer diameter of the outer surface 63 on the housing part 61. If the housing part 61 of the cylinder 3 in Pushed in the direction of the central axis 2 between the holders 65, the tongues 69 are elastically deformed, and a clearance-free fit is formed between the lateral surface 62 on the cylinder 3 and the holding surfaces 64 on the holders 65. The deformation of the elastic tongues 69 on the O 96/15368 PC17CH95 / 00259
• Brackets 65 cause four equal radial forces directed against the central axis 2, which center the housing part 61 and thus the cylinder 3 relative to the central axis 2 without play.
• the housing part 61 of the cylinder 3 bears against the stop surface 66 of the housing 5 and is connected by means of known connecting elements 30, e.g. Screws, with the housing 5 connected.
• This embodiment of the connections between the cylinder 3 and the housing 5 ensures centering and fastening without play, in which the influence of the connecting elements 30 on the centricity of the arrangement is avoided.
• the lateral surface 62 is then designed as an outer surface or as an inner surface.
• the holders 65 are then arranged accordingly in the inner region of the housing 5, and the holding surfaces 64 on the elastic tongues 69 are then directed inwards or outwards depending on the orientation of the lateral surface 61.
• the elastic tongues 69 have holding surfaces 64 arranged on the outside, which engage in a collar or a groove on the housing part 61, the initial diameter in the unassembled state is larger than the diameter of the outer surface 62 on the housing part 61 of the cylinder 3. As described above, the play-free guidance is guaranteed in every 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 With Elastic Sealing Lips (AREA)
• Sealing Devices (AREA)
• Cylinder Crankcases Of Internal Combustion Engines (AREA)

Applications Claiming Priority (3)

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• 1995
  • 1995-11-09 AT AT95935791T patent/ATE166949T1/de not_active IP Right Cessation
  • 1995-11-09 ES ES95935791T patent/ES2118631T3/es not_active Expired - Lifetime
  • 1995-11-09 CA CA002181169A patent/CA2181169A1/fr not_active Abandoned
  • 1995-11-09 US US08/669,503 patent/US5826491A/en not_active Expired - Fee Related
  • 1995-11-09 DE DE59502408T patent/DE59502408D1/de not_active Expired - Fee Related
  • 1995-11-09 WO PCT/CH1995/000259 patent/WO1996015368A1/fr active IP Right Grant
  • 1995-11-09 EP EP95935791A patent/EP0739450B1/fr not_active Expired - Lifetime
  • 1995-11-09 CN CN95191211A patent/CN1071845C/zh not_active Expired - Fee Related
  • 1995-11-09 DK DK95935791T patent/DK0739450T3/da active
  • 1995-11-09 JP JP51561496A patent/JP3512192B2/ja not_active Expired - Fee Related

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