EP0674746B1 - Taumelscheibenmaschine - Google Patents

Taumelscheibenmaschine Download PDF

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Publication number
EP0674746B1
EP0674746B1 EP94902680A EP94902680A EP0674746B1 EP 0674746 B1 EP0674746 B1 EP 0674746B1 EP 94902680 A EP94902680 A EP 94902680A EP 94902680 A EP94902680 A EP 94902680A EP 0674746 B1 EP0674746 B1 EP 0674746B1
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EP
European Patent Office
Prior art keywords
piston
swash plate
plate machine
grooves
groove
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
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EP94902680A
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German (de)
English (en)
French (fr)
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EP0674746A1 (de
Inventor
Fritz Reis
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Hofmann Hofmann Sondgen Pauly Gdbr
Original Assignee
Hofmann Hofmann Sondgen Pauly Gdbr
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Priority claimed from DE19924242449 external-priority patent/DE4242449A1/de
Priority claimed from DE19934334874 external-priority patent/DE4334874A1/de
Application filed by Hofmann Hofmann Sondgen Pauly Gdbr filed Critical Hofmann Hofmann Sondgen Pauly Gdbr
Publication of EP0674746A1 publication Critical patent/EP0674746A1/de
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    • 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 swashplate machine with a hollow spherical working space which is divided by a partition into at least one high-pressure side and one low-pressure side, into which the working medium can be fed through a line system, the partition extending up to a piston carrier and working together with a plate-shaped sealing strip an annular piston adapted to the diameter of the working space, which is connected to the outer space by a mounted shaft which causes the piston to wobble, the piston having at least one radial piston slot extending from the periphery to approximately a piston carrier, in which a guide pin is inserted , which cooperates with the partition, and which piston tapers outwards towards the circumference, the end faces of the piston having opposite Se and laterally delimiting the working space and perpendicular to the axis of rotation of the shaft surfaces are in contact.
  • the invention relates to the field of swashplate machines for the conveyance of liquid and gaseous Media as a sub-group of the field of work machines, especially swash plate pumps and swash plate compressors.
  • Such a swashplate machine has become 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 acted upon by the shaft being in positive engagement with the piston and imparting the wobbling movement to it.
  • the partial working spaces located on both sides of the piston which are formed by a partition wall which is in engagement with the piston, function as a high-pressure and low-pressure chamber into which the respective medium is fed and discharged, depending on the direction of rotation of the drive shaft driving the piston carrier.
  • the piston guide 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, which is guided in a guide groove arranged in the partition, which radial slot is angled Side flanks are provided, the opening angle of which is adapted to the pivoting 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 static friction, only the significantly lower rolling resistance of the rotatable cylindrical guide pin in the guide groove in the end face of the partition facing the working area is opposed to the wobbling movement of the piston. if anything, friction occurs at most as sliding friction and then only in a line along the pressure-side contact line of the circular-cylindrical guide pin on the inner wall of the guide groove that is tangential to it.
  • 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 by means of the rotatable guide pin inserted in the radial slot as very wear-resistant even at high drive speeds.
  • the partition which engages in the radial slot arranged in the piston, includes the guide pin with a certain tolerance on two opposite sides with the guide groove, so that only one side of the two possible contact surfaces, namely the respective one Inner wall side of the guide groove in the partition, is subjected to force and the opposite side is relieved.
  • 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 dividing wall engaging in the radial slot each have a coordinated spherical curvature adapted to the radius of the slot base are provided.
  • 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 which are adapted to the pivoting stroke of the piston. In order to reduce the friction that occurs, the common contact surface between the piston and the partition end face adapted to each other in the form. 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.
  • 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, they also serve to guide the piston, and because of the circular cylindrical roller shape of the sealing rollers, there is only one linear contact surface between the sealing rollers and the piston. Accordingly, the resulting friction is almost negligible.
  • sealing lips can also be provided, which also have a rounded contact surface for the partition, corresponding to a half cylinder, and can also be arranged so as to be tangentially movable, so that they always nestle against the partition.
  • the material pairing of the sealing lip and partition wall can 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
  • 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 optionally provided.
  • 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 lies 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 consist, according to the invention, 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 partition wall engaging therein and at the same time to seal the part work spaces formed by the piston and the partition wall against one another.
  • these guide bodies or sealing rollers are pressed against the partition wall by compression springs and are thus in constant contact with the partition wall and ensure a good seal.
  • the spring force is dimensioned such that sufficient pressure is applied on the one hand and no unacceptably high friction results on the other hand.
  • the compression springs for pressing the sealing rollers are provided together with the action of the pressure medium, in order to ensure in this way that even in the unpressurized state, for For example, when the swashplate machine is stopped, a seal against a minimum pressure is guaranteed.
  • the piston for the swash plate 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 or fish 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 swash plate machine in its pumping action.
  • the area of the piston provided with the radial grooves in the piston is a circular sector, 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 areas of the piston provided with the grooves are each arranged on the mutually opposite end faces of the piston so that a plane of division of the piston lying along the piston slot axis converts the piston into a first piston half with radial grooves or with radially extending 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 the associated 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 gaps between the piston surface and the working space wall caused by the grooves, which lead to the fact that the pumping of the relevant one Medium required vacuum can not 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 relationship 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 °. From this it follows that, depending on the respective piston diameter, the clear width of the grooves adapts and, with large piston dimensions, wide grooves also result. This proves to be advantageous for operation in that large media flows are also usually conveyed with a swash plate machine with a large piston diameter, which often also have large foreign components.
  • 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.
  • 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 the same or different steep slopes. 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 shovel, 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 a wider 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 possibly additionally, it can be provided that the knife-like webs have a coating with a wear-resistant material.
  • Another embodiment provides that the webs are made as separate inserts made of hard metal and inserted into the piston.
  • 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 rolled off on the inner wall of the working space, solid components located between it and the piston are not squeezed as since then, with the result that leaks in the working spaces may be generated as a result, but instead the sharp cutting edge of each bar is cut and thus crushed.
  • the inner wall of the work space serves as a cutting surface similar to an anvil.
  • the previously mentioned problem which can possibly arise when the piston area provided with grooves is used on the suction side, has no relevance for the pressure side, since there are already conveyed solid parts in the piston working space which fill the grooves and thus contribute to the sealing.
  • 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 is provided with a soft layer on its piston surfaces, preferably only on the beveled area.
  • This soft layer can consist of rubber and can be vulcanized onto the piston blank made of steel. Instead, it is also possible that a flexible but wear-resistant plastic is provided as a soft layer instead of rubber.
  • 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 and any dirt in between is pressed into the soft layer or removed beforehand as with a spatula.
  • FIG. 1 shows a swash plate machine 10 according to the invention in longitudinal section, which has a housing 12 formed from a left housing part 13 and a right housing part 14, in which a working space 16 is arranged.
  • the two housing parts 13, 14 forming the housing 12 are held together in a known manner by means of a screw connection.
  • the working space 16 which is spherical, there is a partition 18 which divides the working space 16 together with an annular piston 20 into a high-pressure space 23 and a low-pressure space 24.
  • 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 inclined, 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 to the longitudinal axis of the piston Drive shaft 28 is employed.
  • the peripheral area of the piston 20, i. H. its circumferential area is beveled 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 in which the partition 18 engages.
  • the flanks 32, 33 of the radial slot 30 are, as shown in 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 which is formed in the end face of the partition 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 guidance 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, which overall appears as a wobbling movement.
  • the swivel path or, in other words, the swivel stroke of the piston is coordinated with regard to the intended use, e.g. as a high-pressure pump or as a compressor, i.e. the higher the drive speed provided for the drive shaft, the higher the swivel or wobble frequency and the higher the swivel path or swivel stroke is smaller 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 good sealing of the low-pressure space 23 against the high-pressure space 24 with comparatively little 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 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
  • Reference numbers 58 denote housing screws which serve to connect the two housing parts 13, 14 of the swashplate machine housing 12. They are arranged concentrically around the work space 16, so as to ensure that no leaks or housing misalignment with corresponding adverse consequences for operation can occur.
  • FIG. 4 shows a representation similar to that shown in FIG. 3, namely a side view of the annular piston 20, which, however, has a different piston guide on the dividing wall 18, which is provided specifically for operation at low drive speeds.
  • the guide of the piston 20 is achieved by the flanks 32, 33 of the radial slot 30, which abut the partition wall 18 engaging in the radial slot 30.
  • 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) and / or by the respective working medium.
  • bearing arrangements 42, 44, 46 in the housing 12 and in the piston 20 are possible to lubricate evenly and also to keep a sealing ring 51 provided for sealing the shaft bushing and a stuffing box 53 or an alternative mechanical seal 52 used instead of these two seals virtually without pressure, that is to say to relieve the medium pressure.
  • a vent hole 56 is provided at the lowest point of each relevant seal 50, 51, 52.
  • baffle plate 50 In order to protect the seals 51 or 52 which are provided for sealing the shaft bushing and are directly exposed to the action of the lubricant against mechanical damage by the pressure jet of the lubricant, a so-called baffle plate 50 is built in, which consists of metallic material and forms one leads to significant 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 if the fit between the drive shaft 28 and the baffle plate 50 is too tight and promotes lubricant in the sealing region of the shaft bushing of the drive shaft 28 through the housing, which promotes leakage would, 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 supplied with the sufficient amount of lubricant via a lubricant channel 64 arranged in the drive shaft 28 as a central bore.
  • the guide groove 40 in the end face of the dividing wall 18 is also included in this lubrication circuit, the lubricant being supplied with sufficient pressure via the lubricant connection 62 and being able to flow off again on the low-pressure side via the ventilation holes already mentioned, in order to keep the pressure chamber free of lubricants and thus to avoid undesired enrichment of the compressed air with lubricants, eg oil.
  • the lubrication channels 54 act in the opposite direction of rotation of the drive shaft 28 swash plate machine 10 as vent holes 56 and vice versa the vent holes 56 as lubrication channels 54.
  • the lubrication system with the holes 54, 56 with ball valves or the like, not shown, can be used accordingly be designed constructively.
  • 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 of the partition 18 on the pressure chamber side and which is by means of a releasable connection, e.g. Thread or screw connection that connects the radial slot element 31 with 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 its pivot stroke, as already explained in relation to FIG. 1 limited.
  • 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, whereby by introducing balancing weights 65 into the radial recess 35, weight compensation even when using a radial slot 30 with a different geometry and therefore less material removal is possible.
  • 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 limited by a radial slot 30 provided with slot flanks 32, 33 and molded in the piston .
  • insert 67 is spherically curved on its surface carrying guide pin 38, the curvature being compatible with the configuration of the corresponding end face of partition 18.
  • the insert 67 has V-shaped indentations on two opposite sides, which the X-shaped radial slot 30 in the piston 20 correspond congruently.
  • 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 ensure a firm fit in the 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 through 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, of two halves, the parting line of which is inclined, that is to say at an angle to the drive shaft 28, so that, in a likewise known manner, that between the two halves of the piston carrier 26 inserted piston 20 is set 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 it can rest with its piston surfaces 33, 34 in accordance with the respective maximum swivel position caused by the wobble movement on the inner wall of the working space 16, 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 in which the partition 18 engages.
  • a guide pin 32 is used, which 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 tumble by the rotating piston carrier 26, from rotating with it. Instead, the piston 20 makes by guiding the guide pin 32 in the radial slot 30, a back and forth movement in which it executes a pivoting movement corresponding to the angular adjustment of the piston carrier 26 26 with respect to the drive shaft 28, which appears as a wobble movement overall.
  • the piston 20 has 72 grooves 76 on its two pressure piston surfaces belonging to the pressure chamber 23. which are delimited by knife-like webs 78.
  • the knife-like webs 78 have the task of cutting the solid components that 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.
  • the suction piston surface 74 is left smooth, that is to say without grooves or webs. The reason for this is to build up a sufficient negative pressure in order to draw in the fluid to be conveyed in each case.
  • the profiling of the piston surfaces 74 on the suction side would lead to disturbing leaks which prevent the generation of the required negative pressure.
  • a possible jamming of solid components between the piston surface 74 and the inner wall of the working space 16, in contrast, is less problematic. In any case, the tightness achieved is sufficient to build up the desired negative pressure.
  • FIG. 9 the piston 20 is shown in FIG. 8 in side view, i. H. with a pressure piston surface 72 provided with grooves 76 and webs 78 and with a smooth suction piston surface 74.
  • a pressure piston surface 72 provided with grooves 76 and webs 78 and with a smooth suction piston surface 74.
  • the same reference numbers as in FIG. 8 have been used for the same features.
  • 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 is a view that is pivoted by 90 °.
  • 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 line).
  • 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; but this design has a more favorable service life, which increases its service life.
  • the pumped medium is sucked in on the suction side of the piston 20 and, as a result of the wobbling movement, is conveyed from the suction chamber 24 into the pressure chamber 23, where, if necessary, the knife-like webs 78 crush the solid components of the pumped medium.
  • the grooves 76 are radially aligned, as are the webs 78 which delimit them, the groove width on the outer circumference being 5 to 10 mm, depending on the piston diameter.
  • the radially aligned grooves 76 or the groove flanks of the webs 78 that delimit 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 similarly is kept in a pocket 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, it being possible for the web cross-section to be provided conically with a corresponding machining, 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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  • Portable Nailing Machines And Staplers (AREA)
EP94902680A 1992-12-16 1993-12-04 Taumelscheibenmaschine Expired - Lifetime EP0674746B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19924242449 DE4242449A1 (de) 1992-12-16 1992-12-16 Taumelscheibenmaschine
DE4242449 1992-12-16
DE4334874 1993-10-13
DE19934334874 DE4334874A1 (de) 1993-10-13 1993-10-13 Taumelscheibenmaschine
PCT/EP1993/003415 WO1994013934A1 (de) 1992-12-16 1993-12-04 Taumelscheibenmaschine

Publications (2)

Publication Number Publication Date
EP0674746A1 EP0674746A1 (de) 1995-10-04
EP0674746B1 true EP0674746B1 (de) 1996-09-04

Family

ID=25921383

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94902680A Expired - Lifetime EP0674746B1 (de) 1992-12-16 1993-12-04 Taumelscheibenmaschine

Country Status (17)

Country Link
US (2) US5685702A (enrdf_load_stackoverflow)
EP (1) EP0674746B1 (enrdf_load_stackoverflow)
AT (1) ATE142307T1 (enrdf_load_stackoverflow)
AU (1) AU700197B2 (enrdf_load_stackoverflow)
BG (1) BG61736B1 (enrdf_load_stackoverflow)
CA (1) CA2151397A1 (enrdf_load_stackoverflow)
CZ (1) CZ155695A3 (enrdf_load_stackoverflow)
DE (1) DE59303688D1 (enrdf_load_stackoverflow)
DK (1) DK0674746T3 (enrdf_load_stackoverflow)
ES (1) ES2092887T3 (enrdf_load_stackoverflow)
FI (1) FI107402B (enrdf_load_stackoverflow)
GR (1) GR3020949T3 (enrdf_load_stackoverflow)
HU (1) HU218803B (enrdf_load_stackoverflow)
NO (1) NO307268B1 (enrdf_load_stackoverflow)
PL (1) PL172811B1 (enrdf_load_stackoverflow)
RO (1) RO115660B1 (enrdf_load_stackoverflow)
WO (1) WO1994013934A1 (enrdf_load_stackoverflow)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29614108U1 (de) * 1996-08-16 1997-12-11 Klipstein, Thomas, Dipl.-Ing., 22359 Hamburg Rotationskolbenmaschine bzw. Rotationskolbenpumpe
KR100419142B1 (ko) * 1999-03-18 2004-02-14 김종대 자이로 펌프
ITTO20100716A1 (it) * 2010-08-27 2012-02-28 Captech S R L Macchina a fluido con disco oscillante
ITTO20100714A1 (it) * 2010-08-27 2012-02-28 Captech S R L Macchina a fluido con disco oscillante
US8984871B1 (en) 2010-12-23 2015-03-24 Hydro-Gear Limited Partnership Transmission assembly

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DE2517469A1 (de) * 1975-04-19 1976-10-28 Fritz Reis Pumpe mit scheibenfoermigem kolben fuer fluessige oder gasfoermige medien
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DE4131628A1 (de) * 1991-09-23 1993-03-25 Klein Schanzlin & Becker Ag Taumelscheibenpumpe

Also Published As

Publication number Publication date
HUT73256A (en) 1996-07-29
NO952231D0 (no) 1995-06-06
FI107402B (fi) 2001-07-31
EP0674746A1 (de) 1995-10-04
NO952231L (no) 1995-06-06
NO307268B1 (no) 2000-03-06
FI952948A7 (fi) 1995-06-19
PL308994A1 (en) 1995-09-18
ES2092887T3 (es) 1996-12-01
CA2151397A1 (en) 1994-06-23
AU1474995A (en) 1996-09-19
GR3020949T3 (en) 1996-12-31
FI952948A0 (fi) 1995-06-15
RO115660B1 (ro) 2000-04-28
BG99682A (bg) 1996-01-31
HU9501135D0 (en) 1995-06-28
WO1994013934A1 (de) 1994-06-23
US5897301A (en) 1999-04-27
ATE142307T1 (de) 1996-09-15
DE59303688D1 (de) 1996-10-10
PL172811B1 (pl) 1997-11-28
BG61736B1 (bg) 1998-04-30
US5685702A (en) 1997-11-11
HU218803B (hu) 2000-12-28
DK0674746T3 (enrdf_load_stackoverflow) 1997-02-24
AU700197B2 (en) 1998-12-24
CZ155695A3 (en) 1996-01-17

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