Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C9/00—Oscillating-piston machines or engines
  • F01C9/007—Oscillating-piston machines or engines the points of the moving element describing approximately an alternating movement in axial direction with respect to the other element
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C9/00—Oscillating-piston machines or engines
  • F01C9/005—Oscillating-piston machines or engines the piston oscillating in the space, e.g. around a fixed point

Definitions

• the invention relates to a swash plate machine with a hollow spherical working space, which is separated by a partition
• the partition wall reaching as far as a piston carrier and working together with a plate-shaped sealing strip, with a circular one
• Partition works together, and which piston tapers outwards towards the circumference, the end faces of the piston with the opposite and perpendicular to the axis of rotation of the shaft limiting the working space laterally
• the invention relates to the field of swashplate machines for the conveyance of liquid and gaseous Media as a subgroup of the field of working machines, especially swash plate pumps and swash plate compressors.
• Such a swash plate machine has been known from German patent DE 35 42 648 C2.
• the teaching disclosed there relates to a swash plate machine with an annular piston which is arranged in a hollow spherical working space.
• the piston is held in a piston carrier and is set into a wobbling movement by a drive shaft, the piston carrier directly loaded by the shaft being in positive engagement with the piston and imparting the wobbling movement to the latter.
• the partial working spaces located on both sides of the piston which are formed by a partition wall engaged with the piston, work as a high-pressure and low-pressure chamber into which the respective medium flows in and out, depending on the direction of rotation of the drive shaft driving the piston carrier is dissipated.
• the piston guide here consists of a guide pin inserted in a radial slot in the piston, which in its basic form is a circular cylindrical one Column is formed with a slot corresponding to the wall thickness of the partition, in which the partition engages. In accordance with the wobbling movement of the piston caused by the piston carrier set in rotation by the drive shaft, the guide pin slides along the partition.
• the piston has a circular cylindrical guide pin inserted into its radial slot and guided in a guide groove arranged in the partition is which radial slot is angled with Lanken is provided, the opening angle of which is adapted to the pivot stroke of the piston and that the guide pin cooperates with a sealing element arranged in the piston carrier, which is adapted to the opening angle of the radial slot of the piston.
• the rotatable guide pin is supported by an axial bearing in the base of the radial slot. This results in a further reduction in friction, since instead of
• This arrangement is therefore particularly suitable for the operation of the swash plate machine according to the invention as a high-pressure pump or as a compressor.
• the guidance of the radial piston according to the invention proves itself in one Guide groove in the partition wall by means of the rotatable guide pin inserted in the radial slot as being very insensitive to wear even at high drive speeds.
• the partition wall which engages in the radial slot arranged in the piston, guides the guide pin with a certain tolerance on two opposite sides with the
• Guide groove comprises, so that only one side of the two possible contact surfaces, namely the respective inner wall side of the guide groove in the partition, is acted upon by force and the opposite side is relieved. In a further development according to the invention, this results in a very advantageous reduction in wear due to the comparatively low, almost negligible friction.
• the piston has a radial slot with angled side flanks, the opening angle of which is adapted to the pivoting stroke of the piston, and that the slot base and the end face of the in the dividing wall engaging the radial slot are each provided with a coordinated spherical curvature adapted to the radius of the slot base.
• the piston In contrast to the first solution, the piston also has a radial slot but no guide pin. Instead, the radial piston is guided by the side flanks adapted to the pivoting stroke of the piston. In order to reduce the friction that occurs, the common contact surface of the piston and the partition wall End face adapted to each other in the shape. This achieves a very good sealing effect, but only an operation at low speeds is possible with the swash plate machine according to the invention.
• the engagement of the partition wall in the radial slot of the piston has force-acting, tangentially movable sealing rollers arranged in the radial slot, which bear against the partition wall.
• sealing rollers have a double function. On the one hand, as the name indicates, they serve to seal the two pressure chambers from one another. On the other hand, however, they also serve to guide the piston, with only one linear contact surface between the sealing rollers and the piston because of the circular cylindrical roller shape of the sealing rollers. Accordingly, the resulting friction is almost negligible.
• sealing lips can also be provided, which are also rounded, one
• Half-cylinder have corresponding contact surface for the partition and can also be arranged tangentially movable, so that they always nestle against the partition.
• the sealing lip and partition wall should be selected so that a certain lubricating effect and thereby an improved sealing effect occur, for example by using bearing metal for the sealing lips
• the sealing rollers are acted upon by compression springs which press the sealing rollers against the partition.
• the sealing rollers are acted upon by pressure medium from the working space, mechanical springs also being able to be provided if necessary.
• the sealing strip is arranged like a piston ring in a circumferential groove on the piston.
• the sealing strip is expediently made of resilient material and inserted into the circumferential groove in such a way that it always rests against the inner wall of the working space with a sufficiently high contact pressure.
• a further advantageous development of the invention provides that the sealing strip can be pressed against the housing additionally or only exclusively by the working medium, as a result of which the sealing effect is considerably improved without impermissibly high frictional forces attacking.
• Such a measure can, according to the invention, consist in the fact that tangentially movable, force-actuated, roller-shaped parts are arranged in the side surfaces of the radial slot, which serve to guide the cob along the dividing wall engaging therein and at the same time to seal the partial working spaces formed by the piston and the dividing wall from one another serve.
• Compression springs are pressed against the partition and are in constant contact with the partition and ensure a good seal.
• the spring force is dimensioned in such a way that, on the one hand, sufficient pressing force is applied and, on the other hand, no inadmissibly high friction results.
• the compression springs for pressing the sealing rollers are provided together with the application by the pressure medium, in order to ensure in this way that, even in the unpressurized state, for A seal against a minimum pressure is ensured, for example, when the swashplate machine is at a standstill.
• the piston for the swashplate machine has at least in some areas radially extending grooves on at least one end face which are delimited by knife-like webs. This ensures that the contaminants, e.g. Chips and wood pulp in paper production or fish bones in fish processing or fruit or grape residues in wine and must production, cannot get stuck between the piston and the inner wall of the work area and thus impair the pumping machine's pumping action .
• the area of the piston provided with the radial grooves is a circular sector in the piston, the bisector of which extends perpendicular to the axis of the piston slot.
• radial grooves can be arranged on both end faces of the piston, the grooves being arranged on the respective end face of the piston in a sector, one side of which adjoins the piston slot.
• the regions of the piston provided with the grooves are each arranged on the mutually opposite end faces of the piston such that a parting plane of the piston lying along the piston slot axis converts the piston into a first piston half with radial grooves or with radial ones knife-like Web and divided into a second piston half with smooth piston surfaces without grooves and webs.
• the smooth piston area is arranged on the suction side, while the groove area of the piston provided with knife-edge-like webs is arranged on its pressure side. This means that a change in the direction of rotation with a concomitant change of the suction side to the pressure side and vice versa should be avoided, since otherwise there may be leaks during suction due to the spaces between the piston surface and the working space wall caused by the grooves, which lead to the fact that the negative pressure required to convey the medium in question cannot arise.
• the grooves according to the invention are provided only on the bevelled end faces of the piston, which come into contact with the wall of the work area.
• the rest of the piston face is smooth, i.e. without grooves and bars.
• a clear width of 15 mm is preferably provided on the inner circumference as the maximum groove width, ie at the radius at which the beveling of the piston begins.
• the groove depth is in a certain ratio to the groove width and, according to an advantageous embodiment of the invention, is for example 4 mm, corresponding to 40% of the associated groove width.
• the width of the radially arranged grooves is provided in accordance with an angular division of 7.5 ° + 2.5 °. It follows from this that, depending on the respective piston diameter, the inside width of the grooves adapts and, with large piston dimensions, wide grooves also result.
• the grooves have a square profile. This can preferably be a rectangular profile which is flat or curved in the longitudinal direction of the groove. However, it can also be advantageous for the stability of the webs delimiting the grooves that the grooves have a trapezoidal profile with a flat groove base and beveled groove flanks.
• a further advantage can be that the grooves are profiled asymmetrically with respect to their longitudinal axes or that the grooves have a V-profile with a narrow groove base and flanks that are set at the same or different steep angles. It is advantageous if the flanks of each groove on the piston slot side, that is to say the flanks which are in each case closer to the piston slot, are set steeper than the opposite flanks. In this way it can be achieved that when the piston rolls off the wall of the work space, the solid materials are carried along as if by a blade without falling back.
• a particularly preferred embodiment of the invention provides that the angle of attack of the groove flanks on the piston slot side with respect to the groove base is 105 ° to 120 °, preferably 112 °, and that the angle of attack of the opposite groove flanks with respect to the groove base is> 135 ° .
• the knife-like webs delimiting the grooves have a cutting edge-like outer edge and, in comparison, a broader base on the groove base, which reinforce the respective web .
• the knife-like webs In order to reduce the wear of the piston or its piston surfaces provided with the grooves and knives, it has proven to be advantageous for the knife-like webs to be surface-hardened. Instead or, if necessary, additionally, it can be provided that the knife-like webs have a coating with a wear-resistant material.
• a further embodiment provides that the webs are made of hard metal as separate inserts and are inserted in the pistons.
• the piston is made of stainless material, preferably steel
• the groove base receiving the knife-like webs is designed as a separately manufactured piston part which is connected to the piston.
• the knife-edge-like outer edge of each web means that when the piston is successively unrolled on the inner wall of the working space, solid components located between this and the piston are not squeezed as since then, with the result that this may result in leaks in the working spaces ⁇ are produced, but are cut due to the sharp cutting edge of each web and thus comminuted.
• the inner wall of the work space serves as a cutting surface similar to an anvil.
• a further embodiment of the invention which aims to avoid disruptions in the conveyance of media which are mixed with granular impurities, provides that the piston with egg on its piston surfaces, preferably only in the beveled area ⁇ ner soft layer is provided.
• This soft layer can be made of rubber and vulcanized onto the piston blank made of steel.
• a flexible but wear-resistant plastic is provided as a soft layer.
• the soft layer ensures that the granular admixtures such as sand, granulate, gravel or the like cannot lead to leaks during pump operation, since the piston with its sealing surface is always on the working space wall applies and any impurities in between are pressed into the soft layer or removed beforehand as with a spatula.
• FIG. 1 shows a longitudinal section through a swash plate machine according to the invention with an internally guided guide pin
• FIG. 2 is a sectional view according to section line I-I in Fig. 1 (top view of the piston)
• FIG. 3 shows a longitudinal section through the working space with inserted piston and piston guide of the swash plate machine according to the invention
• FIG. 5 shows a piston arrangement with a first sealing segment with an inserted guide pin and lateral slot flanks in an exploded diagram
• FIG. 6 shows a second sealing segment
• FIG. 8 shows a longitudinal section through the working space of the swash plate machine according to FIG. 1 with a new piston with radial grooves
• Fig. 9 is a side view of the new piston
• a swash plate machine 10 according to the invention is shown in longitudinal section, one from a left
• the two housing parts 13, 14 forming the housing 12 are held together in a known manner by means of a screw connection.
• a partition 18 which divides the work space 16 into a high-pressure space 23 and a low-pressure space 24 together with an annular piston 20.
• the piston 20 is held by a piston carrier 26 which is placed on a drive shaft 28.
• the drive shaft 28 is guided laterally to the outside, where it can be acted upon by a motor, not shown here.
• the piston carrier 26 is composed in a known manner from two halves, the parting line of which is set at an angle, that is to say at an angle to the drive shaft 28, so that the piston 20 inserted between the two halves of the piston carrier is also inclined in a known manner Longitudinal axis of the drive shaft 28 is employed.
• the peripheral area of the piston 20, i. H. its area close to the circumference is chamfered in accordance with the maximum swivel position caused during the wobble movement, which on the one hand ensures its full mobility within the working space and enables simplified manufacture compared to the swashplate machine known from the prior art.
• the piston 20 On the side facing the partition 18, the piston 20 has a radial slot 30 into which the partition 18 engages.
• the flanks 32, 33 of the radial slot 30 are, as is apparent from FIG. 2, beveled in accordance with the pivoting stroke of the piston 20.
• a sealing segment 37 In the slot base 34 of the radial slot 30, a sealing segment 37, which is supported by means of an axial bearing, which is designed here as a roller bearing, is arranged, on which a guide pin 38 is attached.
• the guide pin 38 is a circular cylindrical body which is inserted centrally into the slot base 34 and is guided on two sides by a guide groove 40 formed in the end face of the partition wall 18 facing the piston 20.
• the guide pin 38 which is guided in the guide groove 40, serves to pull the piston 20, which is caused to wobble, by the rotating piston carrier 26 prevent him from turning. Instead, the piston, caused by the guiding of the guide pin 38 in the guide groove 40, makes a back and forth movement in which it executes a pivoting movement corresponding to the angular adjustment of the piston carrier 26 with respect to the drive shaft 28, all of which as a wobble movement appears.
• the swivel path or, in other words, the swivel stroke of the piston is matched with regard to the intended use, for example as a high-pressure pump or as a compressor, that is, the higher the drive speed provided for the drive shaft, the higher the swivel or wobble frequency and the smaller the swivel path or swivel stroke, in order to ensure the safe functioning of the swash plate machine 10.
• a sealing strip 21 is inserted in a circumferential groove 22 of the piston 20.
• the sealing strip 21 rests on the inner wall of the working space 16 in a manner similar to a piston ring and thus ensures a good seal of the low-pressure space 23 against the high-pressure space 24 with a comparatively low friction.
• FIG. 2 shows the swash plate machine 10 according to FIG. 1 in a sectional view from above, the cut being made along the section line I-I in FIG. 1.
• the same reference numerals as in FIG. 1 have been used for the same features.
• this view shows the arrangement of the guide groove 40 in the end face of the partition wall 18 facing the piston 20, which surrounds the guide pin on both sides and is idealized only in the respective one Tangent line touched.
• lubrication channels or lubrication bores 54 and ventilation channels or ventilation bores 56 are shown, which serve on the one hand the relatively movable sliding surfaces, e.g. the guide pin 38 and the guide groove 40, as well as bearing points, e.g. to provide the first and second piston bearings 42, 44 in the piston carrier 26 or the axial bearing 36 in the slot base 34, as well as the support bearings 46 for mounting the drive shaft 28, with sufficient lubricant and, at the same time, to prevent an overdosing of lubricant by automatically applying excess lubricant due to negative pressure is sucked out of the swashplate process.
• the relatively movable sliding surfaces e.g. the guide pin 38 and the guide groove 40
• bearing points e.g. to provide the first and second piston bearings 42, 44 in the piston carrier 26 or the axial bearing 36 in the slot base 34, as well as the support bearings 46 for mounting the drive shaft 28, with sufficient lubricant and, at the same time, to prevent an overdosing
• FIG. 4 shows a representation similar to that in FIG. 3, namely a side view of the annular piston 20, which, however, has a different piston guide on the partition wall 18, which is provided specifically for operation at low drive speeds .
• sealing rollers 60 are arranged in the two opposite vertices of the oppositely angled flanks 32, 33, each of which is pressed against the partition 18 by a compression spring (not shown in detail) and / or by the respective working medium.
• baffle plate 50 is installed in an advantageous further development of the invention, which is made of metallic chemical material and leads to a considerable reduction in the mechanical stress on the seals 51 and 52.
• a conventional mechanical seal 52 used here lasts only a short operating time of a few hundred operating hours without any problems due to the mechanical action of the high-pressure jet of the lubricant, i.e. trouble-free.
• the operating costs are significantly increased because of the replacement procurement and the inevitable downtime of the swash plate machine 10 according to the invention.
• baffle plate 50 which surrounds the drive shaft 28 with sufficient play, a significantly increased service life can be achieved, which is important in all respects proves to be advantageous.
• baffle plate or baffle plate 50 prevents an undesirable pumping effect for the lubricant, which inevitably occurs when the fit between the drive shaft 28 and the baffle plate 50 is too tight and promotes lubricant in the sealing area of the shaft bushing of the drive shaft 28 through the housing, which Leakage would favor, but prevented.
• the lubrication of the bearing points 42, 44, 46 by introducing external lubricants Via a lubricant connection 62, for example in the form of a ball valve, to which a lubricant hose with plug-in coupling, not shown here but generally known in the prior art, can be attached.
• a lubricant connection 62 for example in the form of a ball valve, to which a lubricant hose with plug-in coupling, not shown here but generally known in the prior art, can be attached.
• the individual bearing points 42 and 44 in the piston 20 including the guide pins 38 and the support bearings 46 in the housing 12 for supporting the drive shaft 28 are arranged in the drive shaft 28 as a central bore formed as a central bore supplied with the sufficient amount of lubricant.
• the guide groove 40 in the end face of the partition 18 is also included in this lubrication circuit, the lubricant being supplied with sufficient pressure via the lubricant connection 62 and via the ventilation holes already mentioned the low-pressure side can flow off again in order to keep the pressure chamber free of lubricant and thus to avoid undesired enrichment of the compressed air with lubricant, for example oil.
• the lubrication channels 54 act in the opposite direction of rotation of the drive shaft 28 of the swash plate machine 10 as ventilation holes 56 and vice versa, the ventilation holes 56 as lubrication channels 54.
• the lubrication system with the holes 54, 56 cannot ball valves or the like shown in more detail can be designed accordingly.
• FIG. 5 shows a so-called exploded view of a piston arrangement with a first sealing segment 37 for use in a swash plate machine according to FIG. 1 in a longitudinal section or in a side view.
• the sealing segment 37 consists of an insert 39, a radial slot element 31 and the guide pin 38 arranged therein, which is provided for engaging in the guide groove 40 formed in the end wall 18 of the partition 18 on the pressure chamber side and which is by means of a releasable connection, e.g. Thread or screw connection, the radial slot element 31 is connected to the insert 39 and the piston 18.
• This variant of the solution offers the advantage that the above-mentioned frictional wear can be additionally reduced by a suitable material pairing of the materials of the guide pin 38 and the partition wall 18 with the guide groove 40 or the optionally provided lining of its inner wall.
• Another function of the sealing segment 37 is to accommodate the radial slot 30.
• the X-shaped radial slot 30 With the help of the X-shaped radial slot 30 with lateral, at an angle to each other slot flanks 32, 33, in which the partition 18 engages with a tight fit, the pivot angle of the piston 20 and thus is explained, as already explained in relation to FIG. 1 whose swing stroke is limited.
• the pivot angle of the piston 20 With the possibility to improve the required sealing effect and to reduce the frictional wear that occurs by selecting the appropriate material.
• the piston 20 has a radial recess 35 on the side opposite the radial slot 30 or the sealing segment, in which a body 65 with a circular cross section is arranged.
• the radial recess 35 serves to compensate for unbalance of the piston 20, which results from the material removal resulting from the production of the X-shaped radial slot 30, wherein by introducing balancing weights 65 into the radial recess 35, a weight compensation even when using a Radial slot
• FIG. 6 shows a second sealing segment 66 in side view and underneath in top view, as can be used in place of the sealing segment 37 shown in FIG. 5.
• the sealing segment 66 shown here does not have a radial slot element but only an insert 67.
• the pivoting path of the piston 20 is provided by a slot flank 32, 33 in the piston molded radial slot 30 limits.
• the insert 67 is spherically curved on its surface carrying the guide pin 38, the curvature being compatible with the configuration of the corresponding end face of the partition 18.
• the insert 67 has V-shaped indentations on two opposite sides, which the Congruently correspond to X-shaped radial slot 30 in the piston 20.
• FIG. 7 shows a third sealing segment 68 in a side view and underneath in a top view, as can be used instead of the sealing segment 37 or 66 shown in FIG. 5 or in FIG. 6.
• the sealing segment 68 shown here is connected in one piece to the guide pin 38. In its further configuration, it corresponds to the second sealing segment 66, which is shown in FIG. 6. Accordingly, it also has no radial slot element, but a spherically curved surface and V-shaped indentations on two opposite longitudinal sides, which are congruent with the X-shaped radial slot 30 in the piston 20 and thus a fixed one Ensure seat in piston 20.
• the lubrication system provided in the swash plate machine according to the invention which makes use of the different pressures of the pump system, works very cleanly, economically and efficiently due to the suction of excess lubricant caused by negative pressure .
• FIG. 8 shows a sectional view through the swash plate machine 10 according to FIG. 1, which has a new piston 20 in its working space 16.
• the two housing parts 13, 14 forming the housing 12 are held together in a known manner by means of a screw connection, not shown.
• the working space 16 which is spherical, there is a partition 18 which divides the working space 16 together with the annular piston 20 into the high-pressure space 23 located below and into the suction or low-pressure space 24 located above.
• the piston 20 is held by a piston carrier 26 which is placed on a drive shaft 28.
• the drive shaft 28 is guided laterally outwards, where it can be acted upon by a motor (not shown here).
• the piston carrier 26 is also composed here in a known manner, not shown in more detail, from two halves, the parting line of which is set at an angle, that is to say at an angle to the drive shaft 28, so that, in a known manner, that between the two halves of the Piston 20 inserted piston 20 is positioned obliquely to the longitudinal axis of the drive shaft 28.
• the peripheral area of the piston 20, i. H. its circumferential area 33, 34 is chamfered so that its piston surfaces 33, 34 can lie against the inner wall of the working space 16 in accordance with the respective maximum pivoting position caused by the wobble movement, thereby ensuring its full mobility within the working space 16 .
• the piston 20 On the side facing the partition 18, the piston 20 has a radial slot 30 into which the partition 18 engages.
• a guide pin 32 is inserted in the radial slot 30 and absorbs the pivoting forces of the piston 20.
• the guide pin 32 guided in the radial slot 30 serves to prevent the piston 20, which is caused to rotate by the rotating piston carrier 26, from rotating with it. Instead, the piston 20 makes gently through the guidance of the guide pin 32 in the radial slot 30, a back and forth movement in which he executes a pivoting movement corresponding to the angular position of the piston carrier 26 26 with respect to the drive shaft 28, which appears overall as a wobble movement.
• the piston 20 has 72 grooves 76 on its two pressure piston surfaces belonging to the pressure chamber 23 are delimited by knife-like webs 78.
• the knife-like webs 78 have the task of cutting the solid components which get between the piston surface 72 and the inner wall of the working space 16 during the pivoting movement of the piston 20.
• the cavity of the grooves 76 serves in each case to temporarily take up the comminuted residues, as a result of which a certain seal is also achieved until the components comminuted in this way are conveyed onward.
• FIG. 9 shows the piston 20 according to FIG. 8 in a side view, ie with a pressure piston surface 72 provided with grooves 76 and webs 78 and with a smooth suction piston surface 74.
• this view shows the arrangement of the grooves 76 and webs 78 and their radial orientation and their position relative to the radial slot 30, which encompasses the guide pin 32 (not shown here) on both sides.
• the groove width depends on the respective piston diameter and can be specified with an angular pitch of approximately 7.5 ° + 2.5 °.
• FIG. 10 shows a view from two different directions on the end face of the piston 20 with a partial section through a piston surface, from which the longitudinal slot profile of the grooves 76 can be seen.
• the view of the radial slot 30 is reproduced above the division plane shown in dashed lines. Below this, a view swiveled by 90 ° is shown.
• the grooves 76 can accordingly be designed either as continuous grooves with a straight, ie flat, groove base or with a curved groove base (dashed course).
• the latter embodiment variant is, on the one hand, less effective than the flat groove base with regard to the desired cutting action of the webs 78 delimiting the grooves 76; for this, this design has a more favorable service life, which increases its service life.
• the grooves 76 are radially aligned, as are the webs 78 which delimit them, the groove width on the outer circumference depending on the piston diameter being 5 to 10 mm.
• Piston 20 the radially aligned grooves 76 or the groove flanks of the webs 78 delimiting them ensure that the material to be conveyed, in particular the solid components, is automatically carried along when the piston 20 rolls on the wall of the working space 16 and is similar to a pocket ⁇ is held so that the material to be conveyed does not remain behind and does not cause a backflow, but is continuously conveyed onward. In this way it is possible to pump even media that are difficult to convey.
• the thickness of the webs is preferably 1 mm + 0.5 mm, whereby the web cross section can be provided conically with a corresponding processing with a broad base and a narrow outer edge. On the one hand, this improves the cutting effect of the webs 78 and, on the other hand, increases their service life.

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• Engineering & Computer Science (AREA)
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• 1993
  • 1993-12-04 PL PL93308994A patent/PL172811B1/pl unknown
  • 1993-12-04 DE DE59303688T patent/DE59303688D1/de not_active Expired - Fee Related
  • 1993-12-04 DK DK94902680.1T patent/DK0674746T3/da active
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  • 1993-12-04 ES ES94902680T patent/ES2092887T3/es not_active Expired - Lifetime
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• 1995
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  • 1995-06-15 FI FI952948A patent/FI107402B/fi active
• 1996
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• 1997
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