EP0617753B1 - Pompe a piston rotatif - Google Patents

Pompe a piston rotatif Download PDF

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Publication number
EP0617753B1
EP0617753B1 EP92924672A EP92924672A EP0617753B1 EP 0617753 B1 EP0617753 B1 EP 0617753B1 EP 92924672 A EP92924672 A EP 92924672A EP 92924672 A EP92924672 A EP 92924672A EP 0617753 B1 EP0617753 B1 EP 0617753B1
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EP
European Patent Office
Prior art keywords
rotary piston
rotation
inlet
slide
circumferential surface
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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EP92924672A
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German (de)
English (en)
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EP0617753A1 (fr
Inventor
Hans Richard Rappenhöner
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C2/3566—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than one line or surface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/90—Slurry pumps, e.g. concrete

Definitions

  • the present invention relates to a rotary piston pump for conveying flowable or free-flowing, in particular liquid, pasty or granular media, consisting of a pump housing with a cylinder space having a cylindrical inner circumferential surface, into which at least one inlet and at least one outlet open, and from one inside the Cylinder space around a coaxially rotating axis of rotation-driven rotary piston with an outer peripheral surface, the radial distance to the axis of rotation changes over the circumference such that the rotary piston with at least a portion of the outer peripheral surface cooperates sealingly with the inner peripheral surface of the cylinder space and in regions from the inner peripheral surface by one Axis of rotation is spaced radially from the stroke, so that when the rotary piston rotates in the area of the inlet for sucking in the medium to be conveyed, the volume increases beitshunt is formed, which then continues to decrease in volume in the area of the outlet for displacing the medium after continued rotation, the respective working chamber at least during its volume increase or reduction of at least one
  • rotary piston pumps For general-purpose rotary piston pumps, reference is made, for example, to "Lueger, Lexikon dertechnik", DVA-Stuttgart, volume 7 1965, page 218, image 7 and volume 16 1970, pages 243, 244, image 6.
  • Each of these known pumps has an inlet and an outlet directly adjacent to it opposite to the direction of rotation and spaced in the direction of rotation by a circumferential "delivery path".
  • the rotary piston has a cylindrical outer circumference and is connected eccentrically to a shaft coaxial to the cylinder space in such a way that at a point on its outer circumference it touches the inner circumferential surface of the cylinder space in a linear manner, as a result of which working chambers which vary in volume are formed during its rotation.
  • a separating slide is arranged between the inlet and the outlet for the separation between the suction side and the pressure side, which separates the working chamber which enlarges when the rotary piston rotates in the area of the inlet from the working chamber which shrinks in the area of the outlet.
  • the isolating slide is connected to the outer circumference of the rotary piston by a spring pressed and therefore moved back and forth immediately when the piston rotates. This is disadvantageous because there is a high level of friction between the slide valve and the rotary piston combined with a correspondingly high level of wear.
  • a spring must always be tuned in such a way that the natural vibration of the "spring / isolating slide system" is high compared to the rotation frequency. As a rule, this can only be achieved satisfactorily if a strong spring (high spring force) is used, but this disadvantageously increases the friction between the separating slide and the rotary piston.
  • DE-U-69 31 657 describes a rotary pump which has a rotary piston which is polygonal in cross section and which is rotatably mounted in a cylindrical bore in a housing. Each between an outlet pipe and a suction pipe following this in the direction of rotation a slide-like separating element separating these lines from one another is arranged, each of these separating elements being displaceably guided in the piston housing and resting under spring pressure on the circumference of the piston.
  • a spring element is provided which is designed as an annular spring and exerts spring forces directed radially towards the center on the separating members.
  • French publication FR-A-2 464 389 describes a hydraulic machine which can be used both as a pump and as a motor. Here too, gate valves are moved directly by their abutment on cam surfaces of the housing.
  • EP-A-0 065 591 relates to a rotary piston machine of the generic type described at the outset, which can be used in particular as a motor. It is known per se to force the slide via a drive device, for which purpose the rotary piston has lateral guide grooves in which guide elements of the slide are led. However, the sealing problem is particularly addressed in this known machine, for which it is disclosed, among other things, that the separating slide always rests on the piston via sealing strips, and that the slide is even to be pressed against the piston by gas pressure and / or spring pressure .
  • rotary piston machines in particular steam engines
  • a hermetic seal of the respective working chamber is important with regard to a “slide valve drive device”.
  • US-A-892 351 also describes a steam engine with such an abutment element (“sliding abutment”), which is even equipped with an additional seal.
  • the invention has for its object to improve the generic rotary piston pump so that it works on the one hand with little wear and noise and on the other hand not only for the delivery of almost any media, but also for the exact metering of the amount or volume of the medium conveyed is suitable.
  • a metering device is provided for varying the stroke conveying volume of the respective medium conveyed in one of the working chambers.
  • the rotary piston pump is therefore practical to be referred to as a "metering pump”.
  • Flowable or free-flowing media in particular granular, powdery media, can be metered very precisely. This will be discussed in more detail in the following description of the figures.
  • the pump according to the invention is therefore particularly suitable for foodstuffs, such as dairy products in particular, especially since, due to the basic structure, the medium is also conveyed almost without pressure ("entrainment" via the working chambers), so that mechanically sensitive media, such as emulsions, are conveyed very gently ; a mechanical "smashing" of the emulsion (eg milk, cream and the like), as it could occur, for example, in the case of non-generic vane or centrifugal pumps, is advantageously avoided.
  • emulsion eg milk, cream and the like
  • the drive device is designed as a cam drive which, in a preferred embodiment, has at least one cam track (control cam track) which rotates synchronously and coaxially with the rotary piston and is designed as an open groove in the direction of the axis of rotation, in each of which one with the separating slide over a motion transmission link connected cam is guided.
  • the circumferential course of the cam track is precisely adapted to the course of the outer circumferential surface of the rotary piston, so that the separating slide during the rotation of the rotary piston by radial reciprocating movement with its surface facing the piston exactly follows the course of the piston outer circumference.
  • the above-mentioned resonance phenomena are also avoided by the "positive guidance" according to the invention, so that an optimal sealing effect is always maintained in the region of the respective slide valve under all operating conditions (e.g. at any speed).
  • the pump housing there are several, in particular, within the pump housing formed three, evenly distributed over the circumference of the cylinder part pumps each with an inlet and an outlet.
  • an inlet of one of the sub-pumps is arranged at a short distance adjacent to an outlet of the sub-pump which is adjacent (upstream in the direction of rotation) and a separating slide is arranged between the outlet of one sub-pump and the inlet of the other sub-pump. All existing separating slides are then driven by the same drive device, in that a corresponding cam is guided in each case in the same cam track for each separating slide.
  • a rotary piston pump 1 has a pump housing 2 with a cylinder space 4 which has a cylindrical inner peripheral surface 6 (see in particular FIGS. 3 and 5, FIGS. 9 and 10 and FIGS. 14 and 15).
  • the pump housing 2 has at least one inlet 8 and at least one outlet 10, each of which opens into the cylinder space 4 in the region of the inner peripheral surface 6.
  • several, in particular three, sub-pumps 12, 14 and 16, each of which is arranged uniformly distributed over the circumference of the cylinder space 4 are formed within the pump housing 2, each of which Have inlet 8 and an outlet 10 (see in particular Fig.
  • a rotary piston 20 is mounted in a rotationally drivable manner within the cylindrical space 4 via a drive shaft 18 coaxial with the cylindrical space 4 or the inner peripheral surface 6.
  • This rotary piston 20 has an outer circumferential surface 22 designed in such a way that, when it rotates, it interacts in a sealing manner with the inner circumferential surface 6 and in regions between its outer circumferential surface 22 and the inner circumferential surface 6 of the cylinder chamber 4, due to a radial “stroke distance”, respective working chambers 24 are formed, the volume of which increases for the suction of a medium to be conveyed starting from the respective inlet 8 and decreases again with continued rotation to displace the medium in the direction of the respective outlet 10.
  • a separating slide 26 which has an axial length, is arranged between the outlet 10 of one sub-pump 12/14/16 and the adjacent inlet 8 of the sub-pump 14/16/12 closest in the direction of rotation. which essentially corresponds to the axial length (“clear internal width”) of the cylinder space 4, with the exception of a slight play.
  • Each separating slide 26 is mounted in the pump housing 2 so as to be displaceable in an essentially radial direction and acts in a sealing manner with the outer circumferential surface 22 of the rotary piston 20 in order to separate a "suction" working chamber 24 from a "displacing" working chamber 24.
  • each separating slide 26 reciprocates in the radial direction in such a way that its surface 28 facing the rotary piston 20 touches the outer peripheral surface 22 of the rotary piston 20, but preferably via a small, narrow sealing gap (in the Drawings not recognizable) is spaced from the outer peripheral surface 22.
  • each separating slide 26 is driven back and forth in both radial directions by a drive device 30 which is synchronized with the rotary piston 20 in such a way that it has the surface 28 facing the rotary piston 20 the "radial stroke distance curve" which follows when the rotary piston 20 rotates past the separating slide 26, the outer circumferential surface 22.
  • the movement of the separating slide 26 is illustrated in the drawing figures by double arrows 32.
  • the drive device 30 is preferably designed as a cam drive and has for this purpose at least one rotating synchronously and coaxially with the rotary piston 20 than in the direction of the axis of rotation 34 Open groove formed cam track (cam) 36, in which for each separating slide 26 a cam 40 connected to this via a motion transmission member 38 is guided.
  • cam track (cam) 36 in which for each separating slide 26 a cam 40 connected to this via a motion transmission member 38 is guided.
  • each cam 40 is advantageously designed as a cam roller (cam roller) 42 that rotates in the cam track 36 and is rotatably connected to the motion transmission member 38.
  • the cam roller 42 can advantageously be formed by a roller bearing.
  • FIGS. 1 to 7 on the one hand and FIGS. 8 to 11 on the other hand differ primarily in the structural design of the movement transmission element 38. These differences will now be explained in the following.
  • the drive device 30 is arranged in a separate housing chamber 46, which is separated from the cylinder space 4 via a partition 44.
  • This housing chamber 46 practically forms a "gear housing".
  • the drive shaft 18 of the rotary piston 20 extends through an opening of the partition wall 44 and through the housing chamber 46 and is mounted in a housing cover 48 closing the housing chamber 46 on its side facing away from the partition wall 44.
  • On the side of the cylinder space 4 opposite the partition 44, the latter is closed by a further housing cover 50.
  • the drive shaft 18 extends through an opening of the housing cover 50 and a bearing arranged here to the outside and can be connected here to a drive element, not shown.
  • the cylinder chamber 4 is sealed on both sides against the drive shaft 18 by means of a shaft sealing ring 52 in each case.
  • a cam 54 is now arranged and torque-connected to the drive shaft 18 so that it rotates synchronously with the rotary piston 20.
  • the cam plate 54 has the cam track 36 on its side facing the partition 44.
  • each of the cams 40 engaging in the cam track 36 is connected to the associated separating slide 26 via the movement transmission member 38.
  • the motion transmission member 38 consists of a guide tappet 56 connected to the cam 40 and led outwards from the pump housing 2 or the housing chamber 46, and connected to the separating slide 26 and sealed by a seal 58 from the pump housing 2 or the cylinder chamber 4 outwardly guided control plunger 60 and from a connecting part 62 connecting the guide plunger 56 outside the pump housing 2 with the control plunger 60.
  • This connecting part 62 is - as can best be seen in FIGS. 2 and 6 - as Bridge-like driver plate and each rigidly connected to the plungers 56 and 60, in particular screwed.
  • the seal 58 sealing the control tappet 60 is preferred formed as a sealing package from several individual sealing rings.
  • the guide plunger 56 and the control plunger 60 are each guided in a bearing 64 in a direction that is perpendicular to the axis of rotation 34, ie radial, essentially without tilting.
  • Each bearing 64 is preferably designed as a recirculating ball bushing.
  • the plungers 56 and 60 are of course each arranged in the same circumferential area of the pump which is aligned in the axial direction. Due to the "media-tight" separation of cylinder space 4 and "gear housing" (housing chamber 46), this embodiment is suitable for virtually any medium. In this case, in the area of the drive device 30, it is even possible for lubrication to reduce friction without the medium to be conveyed being contaminated.
  • the drive device 30 is arranged together with the rotary piston 20 in the cylinder space 4.
  • the cylinder space 4 is closed on both sides directly by the housing covers 48 and 50; the sealing to the outside again takes place via the shaft sealing rings 52.
  • the rotary piston 20 preferably has a cam track 36 in each of its two end faces, two cams 40 being provided for each slide valve 26, each of which is guided in one of the two cam tracks 36.
  • the motion transmission member 38 expediently consists of two guide slides 66, which are arranged on the opposite end faces of the rotary piston 20 and each connect one of the cams 40 to an end face of the separating slide 26. This can also be seen best in FIG. 8.
  • the guide slides 66 are each in guide recesses of the pump housing, in particular in guide recesses 68 of the housing covers 48 and 50, guided in the radial direction essentially without tilting.
  • This embodiment of the rotary piston pump 1 according to the invention is particularly suitable for conveying "granular” and viscous (highly viscous) media. With media of this type it can namely be ensured that no medium gets into the area of the drive device 30, although this is arranged within the cylinder space 4.
  • the inlets and outlets 8, 10 are arranged in such a way and the rotary piston 20 is designed with respect to the areas of its outer peripheral surface 22 which sealingly cooperate with the inner peripheral surface 6 of the cylinder chamber 4 in such a way that in all positions of the rotary piston 20 within each sub-valve 12, 14, 16 the Inlet 8 is separated from the associated outlet 10.
  • this is achieved according to the invention with the three sub-valves 12, 14, 16, each offset by 120 °, in that the rotary piston 20 has a cross section which corresponds at least approximately to a regular polygon, namely at least one pentagon.
  • the rotary piston 20 is rounded in the region of the corners of its cross section - seen in the circumferential direction - convexly rounded. In these areas, the rotary piston 20 acts in a sealing manner with the inner circumferential surface 6 of the cylinder space 4.
  • the sealing effect can - depending on the medium to be pumped - can be achieved by an axially aligned, linear system or by a small, defined sealing gap.
  • the rotary piston 20 can advantageously also have strip-like radial sealing elements, not shown, which extend in the axial direction and then rest sealingly on the inner circumferential surface 6.
  • the rotary piston 20 is preferably concavely curved in the areas of the side faces of its pentagonal cross section, as seen in the circumferential direction. This contributes to the formation or enlargement of the working chambers 24 and thus also to an increase in the delivery volume of the pump.
  • the convex and concave curvatures of the rotary piston 20 expediently merge into one another.
  • FIGS. 3 and 5 or FIGS. 9 and 10. it is also expedient if the surface 28 of each separating slide 26 facing the rotary piston 20 - again seen in the direction of rotation - is convex.
  • this special configuration ensures that no inlet 8 is connected to the associated outlet 10 in any position of the rotary piston 20. Rather, the inlet is always separated from the outlet via at least one “sealing area” of the rotary piston 20. In each case in one position of the rotary piston 20 there are even two “sealing areas” with a working chamber 24 closed off by them between the inlet 8 and the outlet 10 (see in this respect in FIGS. 3 and 9 each the "lower" working chamber 24).
  • the pump housing 2 is preferably made of stainless steel (e.g. V2A), or of nickel-bronze or plastic.
  • the rotary piston 20 is made of nickel-bronze or plastic.
  • a ceramic material can also be used for housing and / or pistons e.g. a ceramic material can also be used.
  • the rotary piston pump 1 is basically suitable for both directions of rotation (clockwise / counterclockwise rotation); in the case of a direction of rotation reversed to the direction of arrow 70, only the functions of the inlets and outlets 8, 10 would "swap", i.e. each inlet 8 would become the outlet and each outlet 10 would become the inlet, so that the arrows 72 and 74 would also be reversed accordingly.
  • the pump works extremely low in friction and wear, so that even a low drive power is required.
  • the rotary piston 20 is preferably driven at a speed of 16 to 230 l / min (revolutions per minute). A volume of approximately 0.25 l is delivered per revolution.
  • the concrete embodiment with three sub-pumps and "pentagonal" Rotary piston 20 is also particularly advantageous because, when interconnecting all inlets 8 on the one hand and all outlets 10 on the other hand, a very uniform delivery flow is achieved because the pump cycles of the individual sub-pumps differ from one another in time or overlap.
  • this special embodiment also leads to a "shortening" of the transport routes (in the circumferential direction) within the pump 1 according to the invention, ie the medium is only spread over part of the circumference, here in particular less than 120 ° (angular distance between inlet and outlet 8, 19), promoted by the piston 20.
  • the pump according to the invention "treats" the medium much more "gently”.
  • the rotary piston pump 1 initially illustrated in FIGS. 12 to 14 is specially designed as a “metering pump” in particular for granular, powdery media, ie for those substances which consist of individual, more or less large particles and which therefore do not “flow” like liquids. , but are more “flowable”. It is therefore "bulk goods”.
  • the rotary piston pump 1 in this embodiment has only one inlet 8 and also only one outlet 10. In operation, the rotary piston pump 1 is arranged in relation to its position in space so that its axis of rotation 34 runs essentially horizontally.
  • Inlet 8 and outlet 10 are diametrically opposed to one another and at least approximately on the vertical, the inlet 8 pointing upwards as the housing opening during the Outlet 10 is opened vertically downwards.
  • an inlet funnel (not shown here) for receiving and feeding the respective substance, the substance then sliding down into the inlet 8 mainly due to gravity (trickling).
  • the inlet 8 is - seen in the direction of rotation of the rotary piston 20 (see arrow 70 in Fig. 14) - a first slide valve 26, and the outlet 10 is followed by a second slide valve 26, so that the inlet 8 into the cylinder chamber 4 medium is then transported via the working chambers 24 to the outlet 10 (entrained), where it then falls out of the pump 1 essentially due to gravity.
  • the two separating slides 26 correspond - in particular with regard to their "positive drive” via the drive device 30 - to the above explanations, so that reference can be made here.
  • the separating slides 26 do not separate "sub-pumps" here because there is only one pump (one inlet and one outlet) per se.
  • a metering device 80 which serves to vary the "cycle delivery volume" delivered in each of the work chambers 24 in each working cycle, preferably setting the respective cycle delivery volume from zero to one of the maximum volume of the respective one Working chamber 24 corresponding maximum value is possible in particular continuously.
  • the metering device 80 is arranged between the inlet 8 and the outlet 10, for which purpose the inlet 8 in the direction of rotation (arrow 70) of the piston 20 seen, ie on its side opposite the separating slide 26 in the direction of rotation, is limited by a metering slide 82 forming the metering device 80.
  • This metering slide 82 is mounted on a holder 84 in such a way that it can be adjusted relative to the holder 84 in a radial direction relative to the holder 84, preferably via a screw spindle 86 (see the double arrow 87), so that between the outer circumference 22 of the rotary piston 20 and at the end of the metering slide 82 facing this, an inlet gap 88 is formed with a variable clear width measured in the radial direction.
  • the holder 84 carrying the metering slide 82 is driven back and forth in a radial direction — analogous to the separating slide 26 —by the drive device 30 (see FIG. 13), which is illustrated by the corresponding double arrow 32.
  • the holder 84 of the metering slide 82 is connected to a cam 89 which is guided in the cam track 36 already mentioned, so that the metering slide 82 is also driven synchronously with the rotation of the rotary piston 20.
  • the metering slide 82 when set for a reduced delivery volume, projects radially into the cylinder space 4 in some areas, as can also be clearly seen in FIG. 14, but the drive of the holder 84 ensures that the metering slide 82 deviates radially outwards when the sealing areas of the rotary piston 20 each pass the area of the metering slide 82.
  • the working chamber 24 which forms after the inlet 8 when the rotary piston 20 rotates and increases in volume can only fill via the inlet gap 88 formed by the metering slide 82, so that the "degree of filling ", that is, the stroke volume conveyed in one of the working chambers 24 is variable as a result.
  • This described embodiment of the rotary piston pump 1 according to FIGS. 12 to 14 with the metering slide 82 is particularly suitable for granular and powdery media, such as beverage and soup powder, but - at least to a limited extent - also for viscous to pasty media.
  • this version can be used if the metering slide 82 has a "longer" sealing surface, as seen in the direction of rotation of the piston 20, since this would cause the inlet gap 88 as "throttle gap” to increase the flow resistance for the medium.
  • an adjustable ventilation valve 90 is provided for this purpose, it being pointed out that this ventilation valve 90 can in principle also be used without the metering slide 82, so that the ventilation valve 90 itself forms the metering device 80. In the preferred embodiment shown in FIG. 15, however, the metering slide 82 and the ventilation valve 90 are combined with one another.
  • the delivery volume of the medium is metered through the ventilation valve 90 in that part of the medium always flows in the direction of the arrow 94 and part of the air in the direction of the arrow 96 and these parts are conveyed in this way, the "mixing ratio" via the ventilation valve 90 - and if necessary in cooperation with the metering slide 82 - in particular continuously variable.
  • the embodiment with the metering slide 82 also offers the advantageous possibility of counting the particles in the case of granular media which consist of individual particles, such as grains, tablets or the like, ie a specific, defined number of each delivery cycle in each working chamber 24 To transport particles to the outlet 10 so that they can then be packed in the required number of pieces in packaging, for example.
  • the rotary piston 20 preferably has, in its outer circumference 22, receiving recesses (not shown) for one of the particles in each case.
  • the metering slide 82 is then set to an inlet gap 88 in such a way that it only strips off any surplus, that is to say the particles which are not seated in the receiving recesses, and thus does not get into the working chamber 24.
  • uniform "filling" of all receiving recesses of the rotary piston 20 it can be advantageous to set the rotary piston pump 1 according to the invention in vibration during operation.
  • the metering device 80 can also be formed in that the axial length of the working chambers 24 seen in the direction of the axis of rotation 34 and thus also the volume thereof is variable.
  • the rotary piston, the pump housing and the separating slide each consist of at least two telescopically telescopic parts.
  • the metering device 80 thus enables precise metering of the stroke delivery volume in all the possible configurations mentioned.
  • the specific gravity of the medium in question can then be used to easily meter the weight using this volume metering.
  • the metering device 80 that is to say in particular the metering slide 82 and / or the ventilation valve 90, can be equipped with a scale (for volume and / or weight, for example) which is determined empirically, as a result of which the metering is very simple.
  • the medium falling out of the outlet 10 can thus be processed cyclically as a packaging unit, for example, be filled directly into certain packaging.
  • the metering device 80 can also be set automatically by means of an electronic control device, in particular, by merely entering a desired weight or volume as the desired value; the control device then automatically initiates a corresponding setting of the metering device 80, and automatic readjustment can also be carried out by comparing the actual value / setpoint.
  • the drive device driving the isolating slide (s) can in principle be realized by any suitable type of drive, such as a gear / eccentric drive or a servo (motor) drive, in the latter case synchronization with the rotation of the rotary piston via a electronic, programmable logic control can take place.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Steroid Compounds (AREA)

Claims (15)

  1. Pompe à piston rotatif pour la circulation d'agents coulants ou ruisselants, en particulier liquides, pâteux ou granuleux, comprenant un boîtier (2) avec une chambre cylindrique (4) à surface périphérique intérieure cylindrique (6) dans laquelle débouchent au moins une entrée (8) et au moins une sortie (10), ladite pompe comprenant également un piston rotatif (20) pouvant être entraîné en rotation dans la chambre cylindrique (4) autour d'un axe de rotation (34) coaxial à cette demière, la distance radiale par rapport à l'axe de rotation (34) de la surface périphérique extérieur (22) dudit piston variant de manière à ce qu'au moins une région de la surface périphérique extérieure (22) du piston rotatif (20) coopère de manière étanche avec la surface périphérique intérieure (6) de la chambre cylindrique (4), et que certaines régions du piston rotatif soient séparées de la surface périphérique intérieure (6) d'une distance de course, radiale par rapport à l'axe de rotation (34), de manière à ce qu'il se forme, lors de la rotation du piston rotatif (20), dans la région de l'entrée (8) une chambre de travail (24) dont le volume peut augmenter, pour l'aspiration de l'agent à faire circuler, chambre dont le volume diminue ensuite,au cours de la rotation,dans la région de la sortie (10) pour évacuer l'agent, la chambre de travail (24) étant délimitée, au moins pendant son augmentation ou diminution de volume, par au moins un coulisseau de séparation (26) disposé en amont de l'entrée (8) ou en aval de la sortie (10) dans la direction de rotation, ce coulisseau étant déplacé en va et vient dans le boîtier de pompe (2) lorsque le piston rotatif (20) tourne, sensiblement dans la direction radiale par rapport à l'axe de rotation (34), de manière à ce que sa surface (28) en regard du piston rotatif (20) coopère toujours de manière étanche avec la surface périphérique extérieure (22) du piston rotatif (20), le déplacement du coulisseau de séparation (26) étant effectué de force au moyen d'un dispositif d'entraînement (30) synchronisé avec le piston rotatif (20),
    caractérisé en ce qu'un dispositif de dosage (80) est prévu pour faire varier le volume véhiculé cycliquement dans l'une des chambres de travail (24) respectives.
  2. Pompe à piston rotatif selon la revendication 1,
    caractérisée en ce que, grâce au dispositif de dosage (80), il est possible d'effectuer, en particulier sans paliers, une modification du volume de zéro à une valeur maximum correspondant au volume respectif de la chambre de travail (24).
  3. Pompe à piston rotatif selon la revendication 1 ou 2,
    caractérisée en ce que le dispositif de dosage (80) comprend un coulisseau de dosage (82) disposé radialement qui, vu dans la direction de rotation (70), est disposé immédiatement derrière l'entrée (8) et maintenu sur un support (84), de manière à pouvoir être ajusté dans la direction radiale par rapport à ce dernier, en ce que, entre la périphérie extérieure (22) du piston rotatif (20) et le coulisseau de dosage (82), il est formée une fente variable (88) pour l'admission de l'agent, le support (84) et le coulisseau de dosage (82) étant entraînés de force en va et vient par le dispositif (30) dans la direction radiale, en synchronisme avec la rotation du piston rotatif (20).
  4. Pompe à piston rotatif selon l'une des revendications 1 à 3,
    caractérisée en ce que le dispositif de dosage (80) comporte une vanne d'aération réglable (90) par laquelle on peut aspirer un volume variable d'air frais dans la chambre de travail (84) dont le volume s'agrandit en aval de l'entrée (8), le dosage de l'agent étant ainsi effectué par une variation du rapport entre le volume d'agent et le volume d'air aspiré.
  5. Pompe à piston rotatif selon l'une des revendications 1 à 4,
    caractérisée en ce que le piston rotatif (20) présente sur sa périphérie extérieure (22) des évidements d'accueil d'une particule respective de l'agent, composé d'une pluralité de particules identiques, de manière à ce, dans la chambre de travail (24) soit seulement véhiculé un nombre déterminé de particules correspondant aux évidements d'accueil présents dans la région de la chambre de travail (24), les particules en surnombre étant retenues par le coulisseau de dosage (82).
  6. Pompe à piston rotatif selon l'une des revendications 1 à 5,
    caractérisée en ce que le coulisseau de sépration (26) est toujours séparé de la surface périphérique extérieure (22) du piston rotatif (20) par une fente étanche déterminée.
  7. Pompe à piston rotatif selon l'une des revendications 1 à 6,
    caractérisée en ce que le dispositif d'entraînement (30) a la forme d'un entraînement à cames et comprend de préférence au moins une piste à cames (36) toumant en synchronisme et coaxialement avec le piston rotatif (20) et ayant la forme d'une rainure ouverte dans la direction de l'axe de rotation (34), dans laquelle est guidée une came (40), reliée au coulisseau de séparation (26) par un organe de transmission du mouvement (38).
  8. Pompe à piston rotatif selon l'une des revendications 1 à 7,
    caractérisée en ce que le dispositif d'entraînement (30) est disposé dans une chambre de boîtier distincte (46), séparée de la chambre cylindrique (4) par une cloison (44), un disque à came (54) présentant la piste à came (36), relié en particulier directement à l'arbre d'entraînement (18) du piston rotatif (20), étant de préférence disposé dans la chambre de boîtier distincte (46), l'organe de transmission du mouvement (38) qui relie la came (40) coopérant avec la piste (36) au coulisseau de séparation (26), étant formé par un poussoir de guidage (56) relié à la came (40) et sortant du boîtier de pompe (22), par un poussoir de commande (60) relié au coulisseau de séparation (26) et sortant avec étanchéité du boîtier de pompe (2), ainsi que par un élément de liaison (62) reliant le poussoir de guidage (56) au poussoir de commande (60).
  9. Pompe à piston rotatif selon l'une des revendications 1 à 7,
    caractérisée en ce que le dispositif d'entraînement (30) est disposé avec le piston rotatif (20) dans la chambre cylindrique (4), le piston rotatif (20) présentant de préférence sur ses deux surfaces frontales respectivement une piste à came (36), et en ce que pour le/chaque coulisseau de séparation (26), deux cames (40) sont prévues, guidées respectivement dans l'une des deux pistes (36), l'organe de transmission du mouvement (38) étant formé par deux coulisseaux de guidage (66) reliant sur les faces frontales en regard du piston rotatif (20) respectivement l'une des cames (40) à une face frontale du coulisseau de séparation (26).
  10. Pompe à piston rotatif selon l'une des revendications 1 à 9,
    caractérisée en ce que, à l'intérieur du boîtier de pompe (2), plusieurs, en particulier trois, pompes partielles (12, 14, 16) disposées à intervalles égaux sur la périphérie de la chambre cylindrique (4), sont respectivement pourvues d'une entrée (8) et d'une sortie (10), une entrée (8) respectivement de l'une des pompes partielles (12, 14, 16) étant disposée à faible distance d'une sortie (10) de la pompe partielle (16, 12, 14) voisine dans la direction contraire au sens de rotation, l'un des coulisseaux de séparation (26) étant respectivement disposé entre l'entrée (8) de l'une des pompes partielles et la sortie (10) des autres pompes partielles.
  11. Pompe à piston rotatif selon l'une des revendications 1 à 10,
    caractérisée en ce que les entrées et sorties (8, 10) sont disposées de telle manière , et que les régions de la surface périphérique extérieure (22) du piston rotatif (20) qui coopèrent de manière étanche avec la surface périphérique intérieure (6) de la chambre cylindrique (4) sont formées de telle manière que dans toutes les positions du piston rotatif (20), l'entrée (8) soit séparée de la sortie (10) qui lui est associée.
  12. Pompe à piston rotatif selon l'une des revendications 1 à 11,
    caractérisée en ce que le piston rotatif (20) présente une section transversale sensiblement régulièrement polygonale, en particulier régulièrement pentagonale.
  13. Pompe à piston rotatif selon la revendication 12,
    caractérisée en ce que, vues dans la direction périphérique, les régions des angles du polygone du piston rotatif (20) sont arrondies avec une courbure convexe, et que le piston rotatif coopère dans ces régions de manière étanche avec la surface périphérique intérieure (6) de la chambre cylindrique (4), le piston rotatif (20) présentant, dans la région des faces du polygone de préférence une courbure concave vue dans la direction périphérique.
  14. Pompe à piston rotatif selon l'une des revendications 1 à 13,
    caractérisée en ce que la surface (28) en regard du piston rotatif (20) du/de chaque coulisseau de séparation (26) présente une courbure convexe, vue dans la direction de rotation.
  15. Pompe à piston rotatif selon l'une des revendications 1 à 14,
    caractérisée en ce que le piston rotatif (20) présente, dans la/les région(s) coopérant de manière étanche avec la surface périphérique intérieure (6) de la chambre cylindrique (4) respectivement un élément d'étanchéité radiale en forme de barrette, s'étendant dans la direction axiale et appliqué de manière étanche sur la surface périphérique intérieure (6).
EP92924672A 1991-12-20 1992-12-05 Pompe a piston rotatif Expired - Lifetime EP0617753B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE9115838U DE9115838U1 (fr) 1991-12-20 1991-12-20
DE9115838U 1991-12-20
PCT/EP1992/002813 WO1993013296A1 (fr) 1991-12-20 1992-12-05 Pompe a piston rotatif

Publications (2)

Publication Number Publication Date
EP0617753A1 EP0617753A1 (fr) 1994-10-05
EP0617753B1 true EP0617753B1 (fr) 1996-10-16

Family

ID=6874457

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92924672A Expired - Lifetime EP0617753B1 (fr) 1991-12-20 1992-12-05 Pompe a piston rotatif

Country Status (9)

Country Link
US (1) US5580227A (fr)
EP (1) EP0617753B1 (fr)
JP (1) JPH08503756A (fr)
AT (1) ATE144307T1 (fr)
CA (1) CA2126326A1 (fr)
DE (2) DE9115838U1 (fr)
DK (1) DK0617753T3 (fr)
ES (1) ES2096779T3 (fr)
WO (1) WO1993013296A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102006048989A1 (de) * 2006-10-17 2008-04-24 J. Eberspächer GmbH & Co. KG Fördereinrichtung, insbesondere zum Fördern von Brennstoff zu einem Fahrzeugheizgerät

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29614473U1 (de) * 1996-08-21 1997-12-18 Rappenhoener Hans Richard Rotationskolbendosierer
AUPO292496A0 (en) 1996-10-11 1996-11-07 Merlin Corporation Pty Ltd A rotary machine
DE29702384U1 (de) * 1997-02-12 1998-06-10 Rappenhoener Hans Richard Rotationskolbendosierer
FI991461A0 (fi) * 1999-06-28 1999-06-28 Borealis As Menetelmä hiukkasmuodossa olevan aineksen syöttämiseksi
EP1270938A2 (fr) * 2001-06-28 2003-01-02 Esec Trading S.A. Pompe doseuse pour un fluide visqueux
UA119134C2 (uk) * 2012-08-08 2019-05-10 Аарон Фьюстел Роторні пристрої з розширюваними камерами, що мають регульовані проходи для робочого плинного середовища, а також системи, що мають такі пристрої
CN104265632A (zh) * 2014-09-03 2015-01-07 广东美芝制冷设备有限公司 气缸组件和具有其的回转式压缩机、泵
EP3115610B1 (fr) * 2015-07-06 2021-04-14 Goodrich Actuation Systems Limited Pompe hydraulique
CN109779868A (zh) * 2019-02-12 2019-05-21 中国民航大学 多缸星型内腔泵
WO2021021945A1 (fr) * 2019-07-29 2021-02-04 Diversey, Inc. Système de dosage de fluide
GB2596775A (en) * 2020-04-22 2022-01-12 Ishida Europe Ltd An apparatus and method for dispensing flavouring

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US1001533A (en) * 1910-09-26 1911-08-22 Justus R Kinney Rotary pump for use in pumping wood-pulp and similar substances.
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US1261128A (en) * 1916-08-05 1918-04-02 Frank A Higgins Rotary engine.
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US2023608A (en) * 1932-03-22 1935-12-10 Nebel Franz Rotary pump
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US3988083A (en) * 1971-08-28 1976-10-26 Daihatsu Kogyo Company Limited Non-contact vane pump
DE2601347A1 (de) * 1976-01-15 1977-07-28 Wibau Gmbh Pumpe, insbesondere zur foerderung von zementbeton o.dgl.
GB1582494A (en) * 1976-08-19 1981-01-07 Wheeler C Rotary fluid machine
FR2464389A2 (fr) * 1979-09-03 1981-03-06 Stephanois Rech Mec Machine hydraulique a cylindree variable et a cloisons escamotables perfectionnee
EP0065591A1 (fr) * 1981-05-27 1982-12-01 VON INGELHEIM, Peter, Graf Machines à piston rotatif, particulièrement à palettes
JPH0652077B2 (ja) * 1986-05-12 1994-07-06 株式会社日本自動車部品総合研究所 ロ−リングピストン型回転式流体機械

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Publication number Priority date Publication date Assignee Title
DE102006048989A1 (de) * 2006-10-17 2008-04-24 J. Eberspächer GmbH & Co. KG Fördereinrichtung, insbesondere zum Fördern von Brennstoff zu einem Fahrzeugheizgerät

Also Published As

Publication number Publication date
DE59207393D1 (de) 1996-11-21
WO1993013296A1 (fr) 1993-07-08
JPH08503756A (ja) 1996-04-23
EP0617753A1 (fr) 1994-10-05
DK0617753T3 (da) 1997-03-24
ATE144307T1 (de) 1996-11-15
ES2096779T3 (es) 1997-03-16
DE9115838U1 (fr) 1992-02-13
US5580227A (en) 1996-12-03
CA2126326A1 (fr) 1993-07-08

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