EP0617201B1 - Füll-, Fluid-Transport- und Pumpeinrichtung - Google Patents

Füll-, Fluid-Transport- und Pumpeinrichtung Download PDF

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Publication number
EP0617201B1
EP0617201B1 EP94104731A EP94104731A EP0617201B1 EP 0617201 B1 EP0617201 B1 EP 0617201B1 EP 94104731 A EP94104731 A EP 94104731A EP 94104731 A EP94104731 A EP 94104731A EP 0617201 B1 EP0617201 B1 EP 0617201B1
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EP
European Patent Office
Prior art keywords
rotor
pump
gate valve
sealing
slide
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94104731A
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German (de)
English (en)
French (fr)
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EP0617201A1 (de
Inventor
Manfred Sommer
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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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • 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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members

Definitions

  • the invention relates to a filling, fluid transport and pumping device.
  • pumps There are many pumps, pumping devices, feeding and guiding devices, fluid transport devices and the like. These include vane pumps, eccentric vane pumps and gate valve pumps as well as rotary vane pumps and other pumps with eccentrically moving elements. Many pumps are designed for special applications. Many of these pumps compress the pumped medium for the purpose of transportation. In particular, when conveying food and other sensitive goods, components of the medium to be conveyed and pumped can suffer. Many pumps also cause a discontinuous or pulsating flow. Gentle conveyance is particularly important for sensitive goods. With many pumps, such as. B. gear pumps or the like., Residual quantities remain in partial areas of the transport elements when the seal occurs. This often results in strong impacts. The pumps must therefore run correspondingly slowly or be equipped with additional relief openings and relief channels.
  • the rotary piston machine with fixed abutments and vibrating piston wings according to DE 648 719 has the features b), g), h) and i). It has swinging piston wings that are mounted in the outer hollow cylinder. This solution is not comparable to gate valves.
  • the rotary lobe pump or the rotary lobe motor with outer rotor according to DE 37 24 077 has the features a), b), d), g) to i), 1) and m). It has roller-shaped sealing elements in the outer housing, which perform torsional vibrations around their axis and seal with an edge on the cylindrical stator. Radially moving slides that are pushed in and out according to the eccentricity are not provided. Details about the supply and discharge of the medium have not been dealt with. The same applies to the associated documents DE-OS 37 24 076 and 36 38 022.
  • the pump according to US 1,963,350 has the features b) to i) and l). It has an eccentrically rotating rotor with a smooth outer wall of cylindrical shape and partially cylindrical oscillating sealing elements in the walls of the stator, which are rotatably mounted on axially parallel axes arranged in partially cylindrical seal receiving spaces of the stator in the stator. Radially sliding sealing slides moving in and out are not provided. There are no sealing elements on the rotor attached. The medium is fed and removed axially. Arched guide surfaces inside the rotor ensure the deflection and control of the inlet and outlet. The pump medium emerging axially towards the cover is deflected in this and supplied to the outlet formed on the pump stator housing via guide openings and openings.
  • This pump which is technologically interesting from the basic concept, chooses sealing elements that are not suitable, in particular, for pumping media that carry sensitive components, such as beverages and foods that contain raw fruits such as strawberries.
  • the many small rooms and corners are also difficult to clean. This is mainly due to the bearings designed with relatively small dimensions, the springs required for the sealing vibrators and the like.
  • the invention has for its object to propose a pump or other pumping and conveying device of the type mentioned above, which is constructed with extremely gentle pumping from easy to assemble and disassemble and also simple and inexpensive to manufacture components, which are easily available in different series few modifications of the same or different types of pumps and types of pumps allows production and assembly to be designed and used in a manner that is favorable for production.
  • the gate valve pump has great advantages with regard to the seal, because on the one hand a sealing body running around a cylinder wall results in a seal with a relatively large area and little damage to the pump medium, and on the other hand the gate valve can be sealed over a relatively large area and accordingly very well.
  • a slide-in gate valve pump with a oscillating piston would lead to a very uneven flow and therefore cannot be used for food, pharmaceuticals and other high-quality goods.
  • the respective suction and pressure spaces and transport spaces located in between can be designed more cheaply and by the parallel arrangement of guide elements for the medium the various rooms can be opened and closed at suitable times in such a way that no disturbing pressure surges occur.
  • the device excellently fulfills the requirements of the task and results in an unexpectedly quiet, pressure surge-free or at least extremely low pressure fluctuation flow even at high speeds. High pressure build-up is possible.
  • Such a filling, fluid transport and pumping device is expediently designed with a cylindrical main space, in or on which jointly driven eccentric guide disks circulate in the region of both ends, and wherein the eccentric guide disks have cylindrical annular guide grooves, also known as ring grooves, in which Guide rings or slide rings are rotatable, from which the locking slides protrude outward into the respective sliding receiving spaces.
  • the pump can be manufactured inexpensively. Housing and cohesive components of the pump can be designed so that all parts subject to abrasion wear - rotor, gate valve, pump housing - are easily interchangeable and can also be replaced from a line system without removing the pump.
  • the pump is suitable for left-hand or right-hand flow. As a result of the narrow or small gaps between the moving parts that separate the suction and pressure chambers, the pump is able to build up a suitable vacuum for suction under conditions that occur in practice.
  • the locking slides extend radially with respect to the drive and axis of rotation of the pump, but swing in the process about a plane through the pump axis and the inlet openings of the slide receiving spaces.
  • the device or pump can be designed in a variety of important details. Above all, it can be provided that the locking slides are guided and supported, at least in the entrance area of the slider openings, with curved sealing and support surfaces corresponding to their shape or in slots of rotatable slide guide elements. Furthermore, the transitions from the pump chamber wall into the slide receiving spaces Arched contact sealing surfaces take place, in which the distance between the tips in the area of a slide opening is slightly larger than the thickness of the locking slide.
  • the pump chamber wall including the system sealing surfaces is formed by a pump housing made of rubber or coated with rubber.
  • the slide guide elements can be cylinder bodies made of plain bearing material, the diameter of which is greater than the immersion depth of the ends of the locking slide and which have a supporting cross connection in the area beyond the slide movement and in which relief channels are possibly formed.
  • the pump chamber wall, rotor and slide can be made of corrosion-resistant steel or other metal, and the slide guide elements can be made of a plastic that may be equipped with sliding aids. This is particularly important for pumps that, because of the media to be pumped, are to be made from certain steel materials, at least in most areas, and still have good sliding and running properties.
  • the slide receiving spaces are approximately triangular in cross section corresponding to the pivoting angle of the respective slide and / or that three locking slides are designed with associated slide receiving spaces and, if appropriate, guide and sealing elements.
  • the locking slides are designed as flat disks, the curved, inner end sealing surfaces of which are designed to lie on one another with the same radius on guide surfaces of the drive and guide body working as a rotor.
  • a sealing strip is arranged in the inner face sealing surface of each locking slide which vibrates on the outer wall of the rotor.
  • a sealing groove is incorporated in the metal gate valve, in which a sealing strip consisting of a plastic suitable for the material of the rotor and the medium to be pumped is arranged.
  • the rotor carries the eccentric guide disks and the locking slide sealing surfaces of the locking slides, which run normally to the pump axis, are displaceably and sealingly guided between the flat inwardly facing disk sealing surfaces of the eccentric guide disks.
  • a particularly expedient and advantageous variant of the invention provides that the locking slides are rotatably supported by means of slide rings or slide partial rings firmly connected to them, and the slide rings or slide partial rings are rotatably guided in annular grooves which are arranged in the end face of the cylindrical pump chamber eccentric guide disks rotating around the rotor, also forming wall parts, belonging to the locking slide holding and guiding means.
  • the first-mentioned embodiment there are no loss spaces filled by the medium in the annular groove.
  • the locking slides are suspended on both sides and can be better supported symmetrically even with large loads due to high pressures, so that lower bending and torsional forces occur.
  • the sealing surfaces and friction surfaces are not subjected to an unfavorable load and a smoother pump run can be achieved.
  • the two variants are to be selected individually depending on the intended use of the pump and the pumps are to be designed accordingly in terms of construction and assembly technology.
  • the locking slides which are only attached to a slide ring on one side, are easier to install. In the case of the locking slides fastened to partial rings on both sides, care must be taken that suitable dimensions are chosen for the nested mounting due to the sizes of the pumping chamber, the locking slide receiving spaces, the transition openings and the like will. In designs with slide partial rings, these should have the same inner and outer radii and the respective angular length must then be dimensioned such that it is shortened by at least the pivoting angle of the respective locking slide. Furthermore, it can be provided in all versions that the locking slides are formed or fastened on slide rings lying outside the sealing surfaces perpendicular to the pump axis.
  • Another advantageous variant provides that two rings of different sizes are arranged on one side of the rotor in matching ring grooves. This allows the pump to be designed more freely on the other hand, or better supports can be achieved.
  • the locking slide with their slide rings are designed as one-piece, identical components.
  • eccentric guide disks with their outer disk sealing surfaces run in a sealed manner on large-volume O-ring seals which are inserted into the end walls of the pump chamber housing.
  • the fluid guide channels are formed with a rotor inlet channel and a rotor outlet channel, each of which has an inlet opening or outlet opening pointing in different directions and a pump chamber inlet opening or pump chamber outlet opening open to the outer circumference of the rotor.
  • the rotor in the area of its circumferential sealing surface on the pump chamber wall deviates from the outer basic shape of the rotor in such a way that it is designed with a radius equal to the radius of the pump chamber wall.
  • two pump units can be arranged one behind the other on the same axis such that the pump closest to the inlet contains the low-pressure part and the pump closest to the outlet contains the high-pressure part and the media guide channels in the rotors of both pumps are designed to merge. So the outlet of one pump becomes the medium pressure transition into the inlet of the high pressure pump part.
  • the design according to the invention with the media guidance via a rotating central body with corresponding outlet and inlet openings as well as inclined surfaces and control edges is particularly suitable for this.
  • the drive shaft is guided through an inlet space for the pump medium and the pump medium inlet is either ring-shaped or through a lateral inlet connection, while an outlet space is arranged under the vertical drive shaft of the pump.
  • the pump can be designed to be self-cleaning. It then does not need to be disassembled for cleaning and still meets high hygienic requirements and allows many disassemblies to be dispensed with for cleaning purposes in most food processing plants.
  • the pump parameters are far more favorable than those of a rotary lobe pump because the flow is not divided and, in addition, much larger volume portions per delivery section are pushed onto the pressure side.
  • the pump system contains a rotating eccentric hollow body with wipers or locking slides supported and sealed on the end faces, which move and rotate in a housing during the rotation of the rotating parts in accordance with the eccentric turning, pivoting and sliding movements are supported in the housing preferably on two supports offset by 180 ° for the wipers or gate valves.
  • the pump 20 according to FIG. 1 has a bearing and seal housing 21 which is equipped with holders 22.1 and 22.2. With these, it can be attached to an entire device or a support device.
  • a drive shaft 23 has a connecting stub 24 with a spring groove 24.1 for the rotatable drive by a motor.
  • Two roller bearings 26.1 and 26.2 support the drive shaft 23 radially and axially in the bearing and seal housing 21.
  • An inlet connector 27 with screw thread 27.1 leads into the inlet space 28 in the bearing and seal housing 21, which is sealed with the help of the sealing rings 25 against the outside environment and is penetrated by the drive shaft 23. It belongs to the suction side.
  • the actual pump 20.1 is arranged in the area under the entry space 28.
  • outlet port 29.1 is used to connect the pressure side with the delivery lines to the other facilities in the system.
  • the pump 20.1 has a housing cover 90 at the bottom, which is screwed onto the flange 92 of the bearing and seal housing 21 with screws 91 penetrating the pump housing 31.
  • O-ring seals 93.1 and 93.2 are provided in associated grooves 94.1 and 94.2.
  • the eccentric guide disks 40.1 and 40.2 run on these sealed around.
  • the eccentric guide disks 40.1 and 40.2 are rotatably driven together with the aid of the drive shaft 23 via the toothing in the drive opening 56 and circulate in the pump housing 31 in the control part grooves 38.1 and 38.2.
  • the pump housing 31, which can be seen more clearly from FIGS.
  • a nut 95 is used to hold the pump parts on the drive shaft 23 and to easily loosen and remove and reinstall and secure them.
  • FIG. 2 has figures 2.1 marked with decimal digits, which serve to explain them jointly; 2.2 and 2.3. 2.3 and 3, 4 and 5 show details of the components more precisely and with more recognizable reference numerals.
  • the pump 20.1 is a blocking slide pump equipped with two blocking slides and an eccentric guide, in which the pumping medium to be pumped is fed and discharged in a new manner via moving guide elements.
  • the pump 20.1 has a pump housing 31, which can also be referred to as a stator, with a cylindrical pump chamber 30 (FIG. 1; FIG. 2.1), the pump chamber wall 32 of which is designed with slide openings 33.1 and 33.2 (FIG. 2.1).
  • a cylindrical pump chamber 30 FIG. 1; FIG. 2.1
  • the pump chamber wall 32 of which is designed with slide openings 33.1 and 33.2 (FIG. 2.1).
  • the length 35 and the diameter 36 of the cylindrical pump chamber 30 together with further parts and structures determine the volume of the pump.
  • the pump chamber wall 32 ends on both sides at a likewise cylindrical control part groove 38.1 and 38.2.
  • the eccentric guide disks 40.1 and 40.2 lie in these shoulder-like control part grooves 38.1 and 38.2. They are designed as flat cylindrical disks and each have their individual, described in more detail below, because of the difficult description of such shapes clearly z. T. also from the drawings resulting multi-surface structured limited entry and exit openings openings 83.1 and 83.2; some with shaped outlet surfaces 41.
  • a cylindrical annular groove 44 is arranged eccentrically to the pump axis 43 for the respective slide ring 45.1 and 45.2.
  • the locking slide 46.1 or 46.2 projects radially to the center 47 of the control part grooves 38.1 and 38.2, projecting outwards.
  • two identical slide rings 45.1 and 45.2 designed with the same dimensions lie on both sides of the pump chamber 30 and each carry one of the two locking slides 46.1 and 46.2 working in the pump chamber 30.
  • the center point 47 or the associated axis 47 are eccentric to the pump axis 43.
  • Each gate valve 46.1 or 46.2 has a length 48 which is equal to the length 35 of the pump chamber wall 32.
  • Each locking slide has a depth 49 which is dimensioned such that it can engage sufficiently deep into the respective slide receiving space 50.1 or 50.2 through the slide opening 33.1 or 33.2.
  • the slide receiving spaces 50.1 and 50.2 are arranged exactly diametrically opposite to the pump axis 43.
  • the locking slide 46.1 and 46.2 are equipped with flat, rectangular locking slide sealing surfaces 51.1, 51.2, 51.3, 51.4, which form sliding sealing surfaces for eccentrically caused relative sliding movements compared to the eccentric guide disks 40.1 and 40.2.
  • a multi-unit profiled rotor 55 serves for the pump medium guide and the rotary drive.
  • the rotor 55 has a drive opening 56 which is equipped with multi-spline internal teeth or can have a differently profiled configuration of the engagement opening around the central pump axis 43.
  • the drive shaft 23 is inserted with an external spline or the like.
  • This drive opening 56 is introduced with its axis 43 about the eccentricity 57 (FIG. 4, right) to the eccentric axis 47 into the rotor 55, which serves for the drive and the media guidance, as illustrated in particular in FIG. 2.3.
  • the rotor 55 is cylindrical in its basic structure and has several spatially structured openings.
  • the parts of its outer wall 59 which slide on the neighboring parts and do not fall as a result of perforations or depressions lie on a cylindrical surface with a diameter 58 (FIG. 4).
  • the axis of this cylinder surface is the eccentric axis 47.
  • the guide surfaces 59.1 and 59.2 can be seen, which are lateral surfaces.
  • the sealing system 76 separating between the suction area and the pressure area of the pump chamber is the part of the outer wall of the rotor 55 which is the most outer with respect to the pump axis 43 and runs in a circle along the pump chamber wall 32 with a small radius difference and a double wedge sealing gap.
  • FIGS Drawings The basic structure of the rotor 55, which appears to be complicated, is shown in FIGS Drawings clearly recognizable. He has another one outer, lying on cylinder jacket surface parts with a somewhat smaller diameter, and occupying a larger angular range, serving for the positioning centering.There is a thin-walled rotating guide collar 39 between the centering surface 60 serving for the fixed positioning and the cylindrical annular groove 44.1 in the eccentric guide disk 40.1 Slider ring 45.1 executes its torsional vibrations.
  • This cylindrical rotor 55 is integrally formed on the eccentric guide disk 40.2 or otherwise connected to it in a rotationally and motionally fixed manner. It is inserted with the aid of dowel pins 61 and dowel pin receiving holes 62 in the eccentric guide disk 40.1 located at the front in FIG. 2, the centering surface 60 entering the guide groove 63 which is designed as a shoulder and is open on both sides.
  • the slide rings 45.1 and 45.2 are rotatably inserted in the ring grooves 44.1 and 44.2 with a smooth sliding fit.
  • the rotor 55 rotates with its two eccentric guide disks 40.1 and 40.2, they only oscillate back and forth because - as can be seen in FIG. 2.3 - the locking slides 46.1 and 46.2 are held in the slide openings 33.1 and 33.2 and only execute rocker arms and axially in and out can emerge as the eccentric rotary movements require.
  • the ends 65.1 and 65.2 enter or exit the slide receiving spaces 50.1 and 50.2 corresponding to the eccentricity 57.
  • the locking slides 46.1 and 46.2 and formed as approximately square or rectangular disks delimited by parallel sealing surfaces 66.1 to 66.4, the end faces 67.1 and 67.2 of which can be shaped in any way, while the inner end sealing surfaces 68.1 and 68.2 are concavely partially cylindrical and limited by the radius 69, which corresponds to the outer diameter of the cylinder jacket partial surfaces serving for guiding and sealing, namely the guide surfaces 59.1 and 59.2, so that the respective locking slide when the rotor 55 rotates on the guide surfaces 59.1 and 59.2 of the rotor 55 and between the inner surfaces 52.2 and 52.4 of the two Eccentric guide plates 40.1 and 40.2 can swing back and forth sealed.
  • the remaining gate valve sealing surfaces 51.1 to 51.4 have already been dealt with at the front.
  • the contact sealing surfaces 70.1 to 70.4 between the two parts of the pump chamber wall 32 and the slide receiving spaces 50.1 and 50.2 are - as can be seen from FIG. 2.3 - designed as partial cylinder surfaces with a radius 71.
  • the distance 72 between their tips is greater than the thickness 74 (FIG. 2.4) of the locking slides 46.1 and 46.2, so that they have sufficient play to move them.
  • the contact sealing surfaces 70.1 to 70.4 can also have a shape corresponding to the precise movement shape of the locking slides 46.1 and 46.2 and their sealing surfaces, or the surfaces involved in the sealing can be formed with other surfaces which are shaped to match the movements and shape-generating lines.
  • the wing-like locking slides 46.1 and 46.2 can move freely with their freely rotatable slide rings 45.1 and 45.2 and move completely freely due to the higher pressure on one side or the other be pressed tightly. Accordingly, the receiving space 50.1 or 50.2 is at the respective pressure level, which corresponds to the free sealing side. Since the gaps formed here are narrow, larger components of the pump medium do not get into the slide receiving spaces 50.1 and 50.2. Larger components are only in the crescent-shaped media shift rooms. One can have two parts. The spatial areas of the pump chamber 30 are divided by the sealing system 76.
  • the rotor 55 which also serves to guide the pumping medium in the space, has a diagonally guided or approximately helical, running between the rotor inlet channel 80.1 and the rotor outlet channel 80.2, which spatially profiled partition wall 81 separates these two from one another and seals with the surrounding wall surfaces 82.1 and 82.2 the rotor wall parts surrounding the drive spline provided with internal splines and the wall parts of the rotor 55 forming the guide surfaces 59.1 and 59.2 are integrally formed.
  • the two rotor channels namely the rotor inlet channel 80.1 and the rotor outlet channel 80.2, each form an inlet opening 83.1 or outlet opening 83.2 which opens axially in opposite directions and at least partially in the form of a profile, and each have a large area radially into the pump chamber 30 opening pump chamber inlet opening 84.1 or pump chamber outlet opening 84.2.
  • FIG. 4 The pair of parallel lines shown in FIG. 4, designated "81", is an indication of the partition 81 which is concealed here. Compared to the usual relative position of various sectional views, in particular with respect to the oblique images, FIG. 4 is rotated by 90 °. The different inclined images in other figures clearly show the position of the partition 81.
  • the pump core parts shown are located between housing connection parts, each of which has an inlet space 28 and outlet space 29 which are open to the pump parts and which have an end face surface with an inserted O-ring seal 93.1 and 93.2 (FIG. 1).
  • the end faces of the eccentric guide disks 40.1 and 40.2 run around this large-volume O-ring seal.
  • the pump 20 / 20.1 shown is suitable for a wide variety of pumping media or can be suitably designed by means of suitable materials and material combinations or special configurations. It is particularly intended for food and especially designed for high hygiene requirements.
  • the pumping media can also contain sensitive components such as fruit or other food components. They can also consist of or contain chemically aggressive substances.
  • the pump can also be used for dairy products, beverages, cosmetics, pharmaceuticals and many other liquid and viscous substances.
  • the pumped medium to be pumped enters the inlet space 28 through the inlet nozzle 27 and exits through the outlet space 29 in the outlet nozzle 29.1.
  • the pump medium can be sucked in by the pump 20 / 20.1 or can be supplied in free fall or under natural liquid pressure from a funnel or reservoir. It can leave the outlet port 29.1 under pressure.
  • This pressure is determined according to the usual design rules for pumps and the sealing conditions, in particular the sealing gaps and the flow conditions in them. They are particularly cheap in the construction and the execution options explained. Therefore, relatively high pressures can be achieved in comparison to other pumps and unusually even and low-pressure flow rates.
  • the medium enters the room areas 97.1 and 97.2.
  • the rotor moves from the position shown in Fig. 7.1 to the position shown in Fig. 7.2; 8.2 is shown, rotates and then continues over the position of Fig. 7.3; 8.3 in the position of Fig. 7.4; 8.4, the medium sucked in is housed partly inside the rotor and partly in the area above the rotor and the blocking slide 46. Then the sucked-in medium Medium also divided into two parts, namely the part within the room areas 97.1 and 97.2 under the locking slide 46.2 and a completely separate part in the area 98.1.
  • FIG. 8 show different phases during the rotation of the rotor in oblique images. These correspond essentially to the positions shown in the partial figures in FIG. 7.
  • the pump medium is present in the inlet chamber 28 and passes through the inlet opening 83.1 into the rotor inlet channel 80.1 and is helically deflected therein by the inclined partition 81 and approximately radially through the pump chamber inlet opening 84.1 of the rotor inlet channel 80.1 into the pump chamber 30 the rotor 55 is led outwards as a central region, depending on the position of the rotor 55 and the locking slide 46.1 and 46.2. In the explanation it is assumed that the pump is filled.
  • the various rotational position states of the rotor 55 with the two locking slides 46.1 and 46.2 in the pump chamber 30 and the adjoining slide receiving chambers are shown in the four representations of the same basic structural structures of the main pump parts in FIGS 50.1 and 50.2 are shown.
  • the parts of the pump chamber 30 designated 97 or 97 and the decimal digit are always at the pressure level of the inlet chamber 28 and thus in the light suction area, that is to say under a pressure which is lower than atmospheric pressure.
  • the parts of the room designated 98.1 and 98.2 are separated from the inlet and from the outlet in the illustrated state of the pump and therefore allow the pumping medium to relax, because they enlarge slightly in some areas during a short circulating partial path until the pumping medium of the room area 98.1 as a result of the further movement of the rotor 55 with the rotor outlet channel 80.2 and the associated pivoting movement of the blocking slides 46.1 and 46.2 through the outlet opening 83.2 is in fluid communication with the outlet and that is behind that on the trailing side and from the trailing blocking slide ejected pump medium is now pressurized and reaches the outlet chamber 29 and thus the area of the outlet port 29.1 via the rotor outlet channel 80.2, through the outlet opening 83.2 and thus the pump under the desired pressure caused by the pump through the outlet line
  • the pump medium moves in the radial direction from the pump chamber through the pump chamber outlet opening 84.2 into the rotor outlet channel 80.2, is deflected in the axial direction on the spiral or inclined partition 81 and leaves through the Outlet opening 83.2 and outlet chamber 29 the actual pumping area in the direction of outlet port 29.1.
  • decimal digits used below clearly show which structurally different parts of the room are at the same pressure level.
  • the rotor inlet duct 80.1 is the first area that is at the suction level and is therefore designated 97.1. Otherwise, in this rotary position in the pump chamber 30 there is only the room area 97.2 in the small crescent-shaped gusset area on the right in FIG. 7.1 at the suction level, because the suction slide and the slight overpressure in the relaxation area 98 cause the blocking slide 46.2 - in FIG. 7.1 right - pressed against the system sealing surface 70.3 above and closes the room on this side.
  • the space 99.1 in the rotor outlet duct 80.2 is in fluid communication with the outlet space 29 in the outlet port 29.1 at the pressure level. Furthermore, the gusset space 99.2 - on the left in Fig. 7.1 - is at the same pressure level as the slide receiving space 50.2, because due to the greatest pressure prevailing here, the locking slide 46.2 is pressed against the system sealing surface 70.2, so that there is a small gap opposite it, which forms the pressure connection to the slide receiving space 50.2. At the same time, the room 98.1 is set in this rotational position and, by the position of the blocking slide 46.1, the slide receiving space 50.1 is set to the relaxation pressure level.
  • 8.2 to 8.4 are schematic skewed representations of the previously treated pump.
  • the numbers following the point in the figure designations correspond to those in FIG. 7, so that the same angular positions of the rotor are designated with the same decimal digits.
  • the angular positions are added to the designations.
  • a representation corresponding to FIG. 7.1 is not shown.
  • the illustrations contain part of the However, reference numerals, such as those used previously, are used primarily to represent the inlet and outlet openings of the rotor inlet duct and the rotor outlet duct. Only the edges of these two openings are additionally marked. From the positions shown in FIGS.
  • the pump chamber inlet opening 84.1 has boundary edges 86.1 and 86.2 running on the outer surface 59 of the rotor 55, as well as the leading control edge 87.1 and the trailing control edge 87.2, which are drawn here as axially parallel lines. They can also be rounded or otherwise profiled to improve the transition conditions in the corner areas. 8.2, 8.2.1 and 8.3, the trailing control edge 88.2 of the pump chamber outlet opening 84.2 is not visible, and consequently its corner 88.21 is shown. The leading control edge 88.1 is visible here. 8.4 only the trailing control edge 88.2 is visible, whereas the corner 88.11 is shown instead of the leading control edge.
  • the axially parallel control edges 87.1 and 87.2 as well as 88.1 and 88.2 of the pump chamber inlet opening 84.1 and the pump outlet opening 84.2 have a controlling function and behave like the control edges of slides in hydraulic valves or in two-stroke internal combustion engines.
  • All variants can be sensibly applied to the original pump by varying the corresponding components, but also to pumps with a different design with different housings, different inlets, different drives, but with the same basic principle of designing the pump chamber, rotor, gate valves, pump wall openings and the like.
  • the embodiment variant according to FIGS. 9.1 and 9.2 differs from the previously treated one in that the blocking slides 146.1 and 146.2 of a single pump are now not held on two slide rings lying on both sides of the pump housing. Instead, a slide ring 145.1 of approximately the size and relative assignment is provided for the one slide 146.1 as in the first exemplary embodiment. For the other slide 146.2, however, a larger slide ring 145.2 is provided, which is now on the same side of the pump housing as the slide ring 145.1 of the blocking slide 146.1. Due to its larger inner diameter 144, the slide ring 145.1 can be arranged inside the slide ring 145.2, as shown in FIG. 9.1, so that both locking slides 146.1 and 146.2 work independently of one another and in opposite directions with respect to the direction of rotation.
  • the corresponding ring grooves in the now only one eccentric guide disk are designed with suitable dimensions and preferably with a separating collar between the two.
  • Fig. 9.1 shows the two slide rings 145.1 and 145.2 with their locking slides 146.1 and 146.2 projecting from them individually and separately from one another
  • Fig. 9.2 shows how they are relative to each other in the installed state.
  • This training may make assembly and disassembly cheaper for certain pump designs.
  • the symmetry of the components is lost to a small extent. However, this can be offset by manufacturing and assembly advantages.
  • the embodiment variant according to FIG. 10 differs from the above in that the locking slides 246.1 and 246.2 on each of their locking slide sealing surfaces 251.1 to 251.4 each have a slide partial ring 245.1 and 245.2 on the locking slide 246.1 and with the slide partial rings 245.3 and 245.4 on the locking slide 246.2 are attached.
  • Locking slides supported on both sides can be arranged in ring grooves 244 in eccentric guide disks 240 in the same manner as in the first exemplary embodiment.
  • FIG. 11 and 12 show an embodiment variant in which the locking slides 246.1 and 246.2 are not freely guided between the contact sealing surfaces 70 as in the first exemplary embodiment, but rather slide guide elements 370.1 and 370.2 are arranged in the slide receiving spaces 350.1 and 350.2.
  • the slide guide elements are cylindrical elements with an outer diameter that corresponds to the inner diameter of the slide receiving spaces 350.1 and 350.2. Otherwise, these cylinder bodies have a diameter which is greater than the immersion depth of the ends of the locking slides 246.1 and 246.2.
  • a connection part 373 supporting the two cylinder sections 372.1 and 372.2 is provided in the area beyond the slide movement. Relief channels are also useful.
  • a relief channel 374 is indicated on the left in FIG. 12. It can also be formed in the sliding surfaces. The locking slides fit in the slots 375.
  • the system sealing faces 70 of the first exemplary embodiment with the inlet constrictions are omitted in this variant.
  • the slide guide elements take on their function, to which sufficiently large inlet openings 372 of the slide receiving spaces 350.1 and 350.2 are assigned for the pivoting and oblique movements of the blocking slides 346.1 and 346.2.
  • the slide guide elements 370.1 and 370.2 consist of a suitable material that is neutral with regard to the medium to be pumped and has good sliding properties, for example a plastic such as PEEK (polyether ether ketone), possibly with embedded carbon or other Materials that improve cohesion and / or sliding properties, also in fiber form. This material is referred to in the claims as "plain bearing material”.
  • FIG. 13 shows a further variant.
  • three locking slides 446.1, 446.2 and 446.3 are provided.
  • the entire pump must be designed accordingly.
  • the slide receiving spaces 450.1, 450.2 and 450.3 are not cylindrical, but have an approximately triangular cross-section in accordance with the pivoting angles of the locking slides 446.1 to 446.3. They are designed in such a way that the locking slides rest on the essentially straight inner surfaces 447 in the end positions of their pivoting movements.
  • Other slider receiving space shapes can also be selected based on the pump construction, the medium, possibly vibration processes and the like. However, you must always ensure the free movement of the locking slide to the extent dependent on the eccentricity. Housing with pump chamber wall 432, slide openings and rotor 455 are designed in accordance with the three locking slides 446.1 to 446.3.
  • the embodiment variant according to FIGS. 14 and 15 shows how the locking slides 546.1 and 546.2 sealing strips 570 are inserted into the inner end sealing surfaces 568.1 and 568.2.
  • the sealing strips 570 are designed here, for example, in the actual sealing part with a slightly concave partial cylinder surface 571, which is formed on a dovetail body part 572, which is inserted in a corresponding groove in the locking slide 546.1 or 546.2. For this purpose, it has a partially cylindrical retaining bead 573 and a parallel-walled transition part 574.
  • Such sealing strips 570 suitably consist of an elastic material which has the material properties of those previously treated Slider-guide elements can be the same or similar and, despite good or even improved sealing, prevents direct sliding of the same stainless steel materials onto one another.
  • the locking slides only perform pivoting movements, but must perform a turning movement at the end of their swinging movement and the sealing strips 570 can also perform small tilting movements due to the elasticity with regard to the support, which must be compensated for by suitably designed sealing strips and their materials.
  • 16 and 17 show that the sealing system 676 can be enlarged if necessary by not giving the rotor 655 a precisely cylindrical shape as in the first exemplary embodiment and the previously discussed design variants, but rather a longer sealing surface in the area of the sealing system 676 677 gives, which has exactly the radius as the pump chamber wall 32.
  • 15 and 16 differ in that the slide receiving spaces 50.1 and 50.2 in the embodiment variant according to FIG. 15 are designed without any internals and the locking slides 46.1 and 46.2 are supported on the contact sealing surfaces 70 ..., while in the embodiment variant according to FIG 17 are arranged in the slide receiving spaces 350.1 and 350.2 slide guide elements 370.1 and 370.2.
  • FIG. 18 shows an embodiment variant in which not the entire pump is shown, but only the inner pump housing with its installation parts. It is provided that two completely identical pumps according to the first embodiment are mounted on a single shaft and only one connecting ring 710 is arranged between the pumps, in the guide grooves 711 and 712 of which the two shoulders 715 and 716 of the pump housings 731.1 and 731.2 are aligned to align them right-hand pump 720.1 and left-hand pump 720.2 are used.
  • the liquid initially compressed in the right-hand pump 720.1 passes from the outlet opening 783.2 through the through-opening 785 in the right-hand eccentric guide disk 740.1 directly through the corresponding through-hole in the left-hand eccentric guide disk 740.2 into the inlet opening 783.1 of the left-hand pump 720.2, so that the pump on the right 720.1 works as a low pressure pump and the pump on the left 720.2 as a high pressure pump.
  • the head of a pump can be significantly improved with small dimensions and favorable construction conditions.
  • the pump has an inlet space (28) and a drive shaft (23) in a bearing and seal housing (21), which drives the rotor (55) and the two eccentric guide disks (40.2) connected to it.
  • Slide rings (45.1, 45.2) are stored in these in ring grooves. These carry the locking slides (46.1, 46.2), which plunge into slide receiving spaces via system sealing surfaces or are pulled out of these.
  • the pump is suitable for high hygienic requirements, such as for food, medication and cosmetics, and can also gently convey sensitive components such as fruit or other food components.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Basic Packing Technique (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Filling Of Jars Or Cans And Processes For Cleaning And Sealing Jars (AREA)
  • Eye Examination Apparatus (AREA)
  • Fluid-Driven Valves (AREA)
EP94104731A 1993-03-25 1994-03-24 Füll-, Fluid-Transport- und Pumpeinrichtung Expired - Lifetime EP0617201B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4309687 1993-03-25
DE4309687 1993-03-25

Publications (2)

Publication Number Publication Date
EP0617201A1 EP0617201A1 (de) 1994-09-28
EP0617201B1 true EP0617201B1 (de) 1997-10-15

Family

ID=6483813

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94104731A Expired - Lifetime EP0617201B1 (de) 1993-03-25 1994-03-24 Füll-, Fluid-Transport- und Pumpeinrichtung

Country Status (16)

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US (1) US5613846A (pt)
EP (1) EP0617201B1 (pt)
JP (1) JPH08501134A (pt)
KR (1) KR950701712A (pt)
CN (1) CN1106195A (pt)
AT (1) ATE159325T1 (pt)
AU (1) AU673071B2 (pt)
BR (1) BR9404742A (pt)
CZ (1) CZ281194A3 (pt)
DE (2) DE4410270A1 (pt)
GB (1) GB2283536B (pt)
HU (1) HUT71691A (pt)
PL (1) PL306378A1 (pt)
RU (1) RU94046109A (pt)
TW (1) TW268077B (pt)
WO (1) WO1994021920A1 (pt)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5885065A (en) * 1997-02-19 1999-03-23 Long; Marshall Method and pump for pumping liquid containing solids
KR100346457B1 (ko) * 2000-07-27 2002-07-27 현대자동차주식회사 자동차의 릴레이와 퓨즈 시험용 회로박스
US7134855B2 (en) * 2003-06-13 2006-11-14 Delaware Capital Formation, Inc. Vane pump with integrated shaft, rotor and disc
JP4305238B2 (ja) * 2004-03-23 2009-07-29 ブラザー工業株式会社 ポンプ及びこのポンプを備えたインクジェットプリンタ
DE102008009785A1 (de) * 2008-02-19 2009-08-20 BSH Bosch und Siemens Hausgeräte GmbH Dynamisches Pumpenrad für eine Pumpe sowie eine Pumpeneinrichtung mit einem dynamischen Pumpenrad
CN106017199B (zh) * 2016-07-27 2017-11-17 广州市昕恒泵业制造有限公司 用于管壳式换热器的泵
DE102018214805A1 (de) * 2018-08-31 2020-03-05 Magna Powertrain Bad Homburg GmbH Fördereinrichtung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB383538A (pt) *
US701299A (en) * 1901-02-16 1902-06-03 John F Craig Rotary steam-engine.
FR345995A (fr) * 1904-09-02 1904-12-24 Sidney John Lawrence Perfectionnements dans les moteurs et pompes rotatifs
US831933A (en) * 1905-03-08 1906-09-25 Harry Retzer Comly Rotary pump.
DE410147C (de) * 1921-12-06 1925-02-18 Justus Braun Dipl Ing Kapselpumpe mit einem von einem Exzenter bewegten Kolben
US1780614A (en) * 1927-12-23 1930-11-04 Calvin M Bolster Pump
US1900784A (en) * 1931-01-10 1933-03-07 Zint George Rotary steam engine
US1963350A (en) 1932-02-11 1934-06-19 Henry H Campbell Pump
DE648719C (de) 1934-11-21 1937-08-07 Leo Proestler Ing Drehkolbenmaschine mit feststehenden Widerlagern und schwingenden Kolbenfluegeln
US2611320A (en) * 1947-08-30 1952-09-23 Harry A Kraeling Gasoline or other liquid dispensing means
DE1190795B (de) * 1959-01-31 1965-04-08 Josef Frank Drehkolben einer rotierenden Verdraengermaschine zur Foerderung von Dickstoffen
FR1304017A (fr) * 1961-03-20 1962-09-21 Machine à palettes, à cylindre rotatif, travaillant en moteur ou en pompe
US3303790A (en) 1964-06-26 1967-02-14 Itt Rotating-cam vane pump
DE1553092A1 (de) * 1966-04-02 1970-12-03 Horst Knapp Kapselpumpe
GB1582494A (en) * 1976-08-19 1981-01-07 Wheeler C Rotary fluid machine
DE3638022A1 (de) 1986-11-07 1988-05-11 Karl Sturm Drehkolbenpumpe
DE3724076A1 (de) 1986-11-07 1989-01-19 Karl Sturm Heissgas- bzw. einspritz- bzw. saugmotor
DE3724077A1 (de) 1986-11-07 1989-01-19 Karl Sturm Drehkolbenpumpe- bzw. motor mit aussenrotor

Also Published As

Publication number Publication date
GB9423757D0 (en) 1995-03-01
GB2283536B (en) 1996-10-30
HUT71691A (en) 1996-01-29
CN1106195A (zh) 1995-08-02
EP0617201A1 (de) 1994-09-28
WO1994021920A1 (en) 1994-09-29
KR950701712A (ko) 1995-04-28
CZ281194A3 (en) 1995-04-12
JPH08501134A (ja) 1996-02-06
TW268077B (pt) 1996-01-11
GB2283536A (en) 1995-05-10
HU9403260D0 (en) 1995-02-28
AU6536094A (en) 1994-10-11
ATE159325T1 (de) 1997-11-15
DE4410270A1 (de) 1994-11-10
DE59404296D1 (de) 1997-11-20
BR9404742A (pt) 1999-06-15
PL306378A1 (en) 1995-03-06
RU94046109A (ru) 1996-09-20
AU673071B2 (en) 1996-10-24
US5613846A (en) 1997-03-25

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