EP3752715B1 - Pompe à piston rotatif - Google Patents

Pompe à piston rotatif Download PDF

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Publication number
EP3752715B1
EP3752715B1 EP19705493.5A EP19705493A EP3752715B1 EP 3752715 B1 EP3752715 B1 EP 3752715B1 EP 19705493 A EP19705493 A EP 19705493A EP 3752715 B1 EP3752715 B1 EP 3752715B1
Authority
EP
European Patent Office
Prior art keywords
lobe
sealing element
radius
rotary piston
contact
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.)
Active
Application number
EP19705493.5A
Other languages
German (de)
English (en)
Other versions
EP3752715A1 (fr
Inventor
Hans-Heinrich Westendarp
Folker Aljets
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BMA Braunschweigische Maschinenbauanstalt AG
Original Assignee
BMA Braunschweigische Maschinenbauanstalt AG
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Publication of EP3752715A1 publication Critical patent/EP3752715A1/fr
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Classifications

    • 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
    • F04C2/332—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 with vanes hinged to the outer member and reciprocating with respect to the inner member
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F04C2/40—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 group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/46—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 group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Definitions

  • the invention relates to a rotary lobe pump with a housing which has an inlet and an outlet for the medium to be pumped, at least one rotary lobe which is drivably and rotatably mounted in the housing and which has at least two transport vanes provided with a contour which convey the medium to be pumped Transport medium from the inlet to the outlet, and one sealing element per rotary piston, which is fastened to a sealing body that is in particular pivotably mounted and runs on the contour of the rotary piston during the rotation of the at least one rotary piston and an extension movement from a minimum diameter of the at least one rotary piston a maximum diameter of the at least one rotary lobe and a retraction movement from the maximum diameter of the at least one rotary lobe to the minimum diameter of the at least one rotary lobe.
  • Such a rotary piston pump is particularly suitable and intended for pumping highly viscous media, such as magma in sugar production.
  • Magma is a mixture of granulated sugar and syrup and is created during the cooking process as an intermediate product during sugar production.
  • such a rotary piston pump although it is particularly suitable for pumping crystal suspensions, is not limited to pumping magma.
  • a rotary piston pump with a folding symmetrical rotary piston is known, on the outer contour of which a sealing element runs.
  • the rotary piston has an essentially elliptical contour.
  • the sealing element is attached to a pivoting lever.
  • a rotary lobe pump having a housing, an inlet located below within the housing and an outlet located above it. Between the inlet and outlet is a spring-loaded Arranged slide, over which a sealing element is pressed against the rotary piston.
  • the rotary piston is designed as a rounded rhombus that is folding-symmetrical with respect to the short axis and the longitudinal axis.
  • DE-N 7251 relates to a rotary lobe pump for conveying viscous substances, in which a positively controlled abutment slide follows the outline of the rotary lobe.
  • the positive control is achieved via control cams, which cause a movement of a cylindrical sealing part following the contour of the transport piston.
  • the rotary piston has a cross-sectional shape curved in an S-shape.
  • the DE 125 174 C describes a rotary piston pump having two vanes.
  • a sealing element as a vibrating wall slides along the outside of the rotary piston.
  • the travel along the pressure side, on which the sealing element performs the extension movement, is longer than the travel on the suction side, along which the retraction movement is performed.
  • the NL 25 897 C describes a rotary lobe pump that is similar to this, in which the transport vanes of the rotary lobe have different contours on the pressure side and the suction side, with the extension movement performed by the sealing element on the pressure side being longer than the retraction movement performed on the opposite suction side.
  • the FR 626 596 A relates to a rotary lobe pump with a sealing element sliding along the outside of the rotary lobe, the rotary lobe having a different contour on the retraction and extension sides.
  • the DE 960 411 C describes a rotary piston pump which has two transport vanes and in which a sealing element as a vibrating wall rolls along the outside of the rotary piston.
  • the travel path is along the pressure side on which the sealing element makes the extension movement carried out, but shorter than the travel on the suction side, along which the retraction movement is carried out.
  • the object of the present invention is to provide a rotary lobe pump which has an increased pumping volume per revolution, so that the rotary lobe pump can be built smaller and cheaper with the same pumping volume.
  • the rotary lobe pump with a housing, which has an inlet and an outlet for the medium to be pumped, with at least one rotary lobe, which is drivably and rotatably mounted in the housing and which has at least two transport vanes provided with a contour, which transport the medium to be pumped from transport the inlet to the outlet, and with a sealing element per rotary lobe, which is mounted or formed on a sealing body and runs on the contour of the rotary lobe during the rotation of the rotary lobe and an extension movement from a minimum diameter of the rotary lobe to a maximum diameter of the rotary lobe and performs a retraction movement from the maximum diameter of the rotary piston to the minimum diameter of the rotary piston on different sides of the transport wing, provides that the distance that the sealing element executes on the retraction side of the transport wing during the retraction movement is shorter or smaller than the distance on the extension side during the extension movement.
  • the extension movement begins when the sealing element moves away from a minimum diameter of the rotary lobe from the axis of rotation of the rotary lobe, the retraction movement begins when the sealing element moves from the maximum diameter of the rotary lobe during rotation of the rotary lobe towards the minimum diameter of the rotary lobe.
  • the end of the retraction movement is reached when the contact point or the contact line between the contour of the rotary piston and the sealing element has reached the minimum diameter of the rotary piston, the extension movement ends when the maximum rotary piston radius of the contact point or the contact line has been reached.
  • the contour of the rotary piston is designed so that over a certain angular range of Diameter remains constant, in particular occupies the minimum diameter and/or maximum diameter of the rotary lobe, so that the total angle over which an inward movement and an outward movement is carried out is less than 180° if the rotary lobe is designed as a rotary lobe with two transport vanes.
  • the retraction speed of the sealing element as well as the extension speed is determined by the contour of the respective transport vane of the rotary piston at a constant speed.
  • the sealing element If it is possible for the sealing element to move very quickly in the direction of a minimum rotary piston radius or in the direction of the axis of rotation of the rotary piston, there is a high run-in speed, which is achieved by a steep drop in the contour over the angle of rotation. Conversely, the sealing element is slowly shifted radially outwards on the contour of the rotary piston if there is only a slight incline over a rotation angle. In particular when pumping highly viscous, viscous media, it is problematic to press the blocking element, which is mounted or formed on a sealing body, within the medium to the outside, ie from the minimum diameter of the rotary piston to the maximum diameter of the rotary piston.
  • the sealing element and the sealing body must also be moved through the highly viscous medium during the retraction movement. As a rule, these movements have to be applied against the resistance of the sealing body that is placed in the medium to be transported.
  • the transport wing itself, on which the sealing body with the sealing element slides along, cannot be made as thin as you like, since on the one hand strength conditions must be met and on the other hand acceleration limits must be observed, for example to prevent the sealing element from lifting off the surface of the rotary piston. It has proven to be advantageous to allow the sealing element to move out comparatively slowly. In the area of the maximum rotary lobe radius, a rounding is generally formed in order to avoid an abrupt reversal of movement of the sealing element running on the rotating rotary lobe.
  • the transport wing is narrower and steeper on the entry side than on the exit side.
  • the chamber volume formed by the housing and the contour of the transport wing is formed by the reduced volume of the transport wing on the retract side in relation to the exit side is increased in comparison to a folding-symmetrical contour on both sides of the connecting line of the respective maximum rotary piston radius through the axis of rotation and at the same time avoiding excessive loads on the material due to excessive acceleration during the extension movement.
  • the lower extension speed compared to the retraction speed takes place on an embodiment of the rotary piston with two transport vanes over an angle of rotation of at least greater than 90° up to an angle of rotation of up to 160°, in particular in a range of 110° to 130°, which means that the Sealing element and thereby an increase in the pump chamber can be achieved.
  • the contour on the extension side of the rotary piston has a curvature without turning points in the gradient of the contour, while the contour on the entry side preferably has at least one turning point, which defines that on the entry side there is a maximum reduction in the volume of the transport leaf and after a Phase with a very high entry speed, i.e. a very steep contour of the transport wing on the entry side, this is flattened to provide a smooth transition until the minimum diameter of the rotary piston is reached.
  • a variant of the invention provides that the minimum rotary lobe radius on the entry side of the sealing element is reached at a rotary angle between 30° and 90°, measured from the maximum rotary lobe radius. This ensures that the minimum rotary lobe radius is reached very quickly.
  • the extension movement can begin between 90° and 150° before the maximum rotary piston radius is reached, with the contour on the extension side preferably having a curvature without a turning point or points of discontinuity in order to achieve a uniform, comparatively slow extension movement of the sealing element and thus of the sealing body. Due to the fact that the discharge side is more solid than the entry side and has more material, it is still possible to apply the high forces and moments that have to be applied to transport the viscous product through the pump.
  • the maximum rotary lobe radius can be reached by the sealing element after leaving the minimum rotary lobe radius on the extension side at a rotary angle of between 90° and 150°, so that in a corresponding configuration on the retraction side the volume of the transport vane is reduced when the contour at the minimum rotary lobe radius is reached comparatively early on the entry side must be less than on the exit side.
  • the rotary piston particularly preferably has two transport wings, the contours of which are point-symmetrical to the axis of rotation of the rotary piston.
  • a large chamber volume is provided by the two-wing design.
  • the sealing body is pivotably mounted on a swivel arm inside the housing.
  • This makes it possible to achieve robust mounting with a comparatively compact design without complex spring and/or bearing mechanisms.
  • the position of the bearing point of the pivotable bearing in the housing makes it possible to utilize the pressure present within the pump housing, in particular the pressure difference between the inlet and the outlet, by exerting a force on the sealing element which, with a higher pressure difference, presses the sealing element more strongly pressed against the piston contour, thus reducing losses and increasing operational reliability.
  • the width of the sealing element is also a factor that, together with the pressure difference, influences the contact pressure on the contour of the transport wing.
  • the distance between the bearing point of the pivoted pivot arm and the point of contact of the sealing element on the transport vane is preferably large compared to the rotary piston radius.
  • An approximately linear movement of the sealing element in the extension or retraction direction is desirable.
  • This is achieved in that the swivel arm is chosen to be as long as possible.
  • the distance between the bearing point of the swivel arm and the contact point of the sealing element with the transport vane is preferably 1.5 to 2 times the radius of the rotary piston.
  • the length of the swivel arm is in competition with the most compact possible housing dimensions. The longer the Swivel arm is formed and must be stored in the housing, the larger the housing must be designed.
  • a radius of 1.5 to 2 times the radius of the rotary piston, preferably 1.65 to 1.85 times the radius, has therefore proven to be a good compromise in order to achieve the most linear possible retraction and extension movement of the sealing element.
  • the swivel arm is preferably mounted in the housing on the outlet side so as not to reduce the pump volume per revolution and to press the sealing element against the transport vane via the differential pressure between the inlet and outlet.
  • the swivel arm is rounded or has an oval cross-section in order to ensure a flow-optimized arrangement of the swivel arm within the pumped medium.
  • the sealing element has a wide, possibly flat contact surface and at least one rounded contact section adjoining it.
  • the contact section or sections can form the two ends of the sealing element. Due to the width of the contact surface, it is possible to design several lines of action between the sealing element and the contour of the rotary piston, in particular to also allow the contact point or line of contact of the sealing element to move on the contact surface with the sealing body in order to reduce wear. The wandering of the line of action along the contact surface results from the different gradients in the contour of the transport wings. Secure contact can also be achieved with changing curvatures via the rounded contact sections at the front or rear end of the sealing element.
  • the line of action advantageously has a larger radius on the entry side than on the exit side.
  • the point or line of contact thus travels outward on the seal member as the seal member retracts and then back towards the center of the seal member.
  • the point or line of contact travels inward on the seal member or toward the pivot point of the swing arm as the seal member extends and then back toward the center of the seal member.
  • the shape of the sealing element and its assignment to the contour of the rotary piston can be designed so that at a minimum rotary piston radius and a maximum rotary piston radius The contact point or line of contact of the sealing element is approximately in the middle.
  • the sealing element can have a flat contact surface and at least one rounded contact section adjoining it, at least one of the rounded contact sections extending over an arc of a circle with a central angle greater than or equal to 90°, so that a wiping surface adjoins it.
  • the angle between the wiper surface and the contact surface is therefore less than or equal to 90°.
  • the angle between the straight line through the pivot point of the swivel arm and the point of contact or the line of contact of the sealing element and a flat contact surface of the sealing element when in the position in the maximum rotary piston radius is between 5° and 25°, preferably between 10 ° and 20°, particularly preferably between 12° and 18°, in order to have only one point of contact in the cross section or one line of contact and thus a single sealing line when the sealing element contacts the contour of the transport vane or the rotary piston. Otherwise, pinching or leakage would occur if there was double line contact rather than single line contact.
  • the contours of the rotary piston and the sealing element can be coordinated in such a way that at the point of contact between the rotary piston and the sealing element, the angle between the perpendicular to the surface of the rotary piston and the tangent to the direction of movement of the sealing element is between 0° and 70°, with special designs between 0° and 50° when retracting and between 0° and a maximum of 45° when extending, whereby the sealing body is moved with less friction losses when it is pushed out and easy sliding is made possible for retracting.
  • retracting large angles indicate rapid retraction; when extending, the smallest possible value should be aimed for in order to reduce friction.
  • the lines of action of the sealing element which is defined as a radius around the pivot point of the blocking vane through the point of contact between the rotary piston and the sealing element, on the extension side is different from the line of action on the retraction side, it is possible to provide a comparatively large sealing element with a comparatively large width, since due to the different radii of the lines of action the friction point or the sealing line between the sealing element and the surface of the rotary piston on the sealing element must hike.
  • the radius of the line of action is preferably smaller on the exit side than on the entry side. The possibility of increasing the width reduces wear, since the total available sealing surface, which is subjected to abrasive stress, is increased.
  • figure 1 shows a schematic sectional view of a rotary piston pump 1 with a housing 10 which has an inlet 11 on the top and an inlet 11 oriented essentially perpendicularly to the inlet 11 in the figure 1 having outlet 12 arranged on the right side.
  • a rotary piston 20 is mounted within the housing 10 such that it can rotate about an axis of rotation 21 .
  • the particularly viscous medium in particular magma in sugar production, is conveyed from the inlet 11 to the outlet 12 via the rotary piston 20 , which has two transport vanes 22 on opposite sides.
  • the direction of rotation of the rotary piston 20 is counterclockwise, as indicated by the arrow.
  • the rotary piston 20 with the two transport wings 22 runs partially on a cylindrical housing wall and, together with a sealing element 30, which runs on the outer contour of the rotary piston 20 during its rotation, and a sealing body 42 of a barrier vane 40 separates the inlet side from the outlet side.
  • the sealing element 30 is mounted or formed on the sealing body 42 of the blocking wing 40 , which in turn is mounted in a bearing 41 via a swivel arm 43 .
  • the locking vane 40 is mounted within the housing 10 on the outlet side so that it can pivot about a pivot axis and, depending on the position of the rotary piston 20, moves in the direction of the rotary axis 21 of the rotary piston or away from the rotary axis 21 in the direction of a maximum rotary piston radius.
  • the sealing element 30 rests on the contour of the rotary piston 20 at a contact point 24 in the sectional view, and along a contact line 24 in the three-dimensional configuration. In the position shown according to figure 1 the sealing element 30 rests against the maximum rotary piston radius and is thus pivoted at most in the clockwise direction about the bearing point 41 or the pivot axis through the bearing point 41 . If the rotary piston 20 is rotated counterclockwise to transport the medium to be pumped, the sealing element slides on the surface of the rotary piston 20 in the direction of the pivot axis 21 and thus moves from a maximum rotary piston radius in the direction of a minimum rotary piston radius along an entry side 221.
  • the sealing element 30 slides along the contour of the rotary piston and moves clockwise again in the direction of the illustrated position according to FIG figure 1 pressed outwards, if necessary against a spring force which presses the sealing element 30 together with the sealing body 42 of the blocking vane 40 in the direction of the rotary piston 20.
  • the sealing element 30 thus executes an outward movement or an extension movement when the sealing element 30 slides along the extension side 222 .
  • the swivel arm 43 can be loaded in the area of the bearing point 41 or the pivot axis by the bearing point 41 with a corresponding spring force, which causes a bias against a clockwise movement.
  • the sealing body 42 and in particular the sealing surface of the locking wing 40 extends over the entire depth of the housing, so that an effective separation of the inlet side and the outlet side is always effected via the rotary piston 20 together with the sealing element 30 and the sealing body 42 .
  • FIG figure 2 shows an individual representation of the rotary piston and sealing device according to FIG figure 1 in a mirror image.
  • the direction of rotation of the rotary piston 20 is indicated by the arrow.
  • the rotary piston 20 has two transport wings 22 which are point-symmetrical to the center point which is defined by the point of rotation 21 or by the axis of rotation 21 .
  • the sealing element 30 has slid along the outer contour of the first transport wing 22 on the entry side 21, whereby due to the contour of the rotary piston 20 and the contour of the sealing element 30 a linear contact between the sealing element 30 and the rotary piston 20 was always realized.
  • the contact point 24 in drawing 2 or contact line 24 migrates along the surface of the sealing element 30 as the rotary piston 20 rotates.
  • the radius R F of the distance of the contact point 24 from the bearing point 41 or the contact line 24 from the axis of rotation of the pivot arm 43 through the bearing point 41 changes during the movement of the rotary piston 20.
  • the orientation of the surface of the sealing element 30 to the contour of the rotary piston 20 is selected in such a way that the angle ⁇ between the perpendicular S on the surface of the rotary piston and the tangent T to the direction of movement of the sealing element 30 on the extension side 222 is between 0° and a maximum of 45° and that when retracting the angle ⁇ between the perpendicular S and the tangent T is between 0° and 70° for special designs and otherwise between 0° and a maximum of 50°.
  • the oval or elliptical cross section 430 of the swivel arm 43 is also indicated. Due to the streamlined, drop-shaped or oval design of the pivot arm 43, a minimum flow resistance against the mass flow of the pumped medium can be provided in the outlet area with a high degree of rigidity in relation to the forces and moments applied by pumping. Since the swivel arm 43 and the entire sealing arrangement is arranged on the outlet side, the differential pressure between the outlet side and the inlet side are used to increase the contact pressure of the sealing element 30 on the contour of the rotary piston 20.
  • the distance between the contact line 24 and the pivot axis 41 of the pivot arm 43 changes depending on the angle of rotation and the position of the sealing element 30 on the contour of the rotary piston 20.
  • the maximum effective line radius Rwmax is reached when the rounded contact section 32 rests with its furthest point on the surface of the rotary piston.
  • the minimum effective line radius R Wmin is reached when the end remote from the rounded contact section 32 comes into contact with the rotary piston surface.
  • FIG 3 shows a rotary piston 20 which is rotatably mounted about the pivot axis 21 in a schematic sectional view.
  • the rotary piston 20 has a retraction side 221 and an extension side 222 .
  • the two-wing rotary piston 20 has a contour that is point-symmetrical to the center 21, which forms the pivot point.
  • the maximum rotary piston radius R Pmax results from the maximum distance from the axis of rotation 21 to the outer contour of the rotary piston 20. To the right and left of the line connecting the two maximum rotary piston radii R Pmax it can be seen that the contour of the transport vane 22 on the extension side 222 is further away from of the connecting line lies as the contour of the transport wing 22 on the entry side 221.
  • FIG 4 the geometric relationships and the contour of the rotary piston 20 are shown in more detail.
  • the contour of the rotary piston 20 shown is point-symmetrical to the center point 21 of the minimum rotary piston radius R Pmin . From the maximum rotary lobe radius R Pmax , the contour runs steeply on the entry side 221 in the direction of the minimum rotary lobe radius R Pmin .
  • the contour curve has a turning point in the curvature on the retraction side, approximately at half the maximum rotor radius.
  • the contour then merges into the minimum rotary lobe radius R Pmin , follows it and then merges into the extension side 222 on which the contour executes a curve without turning point up to the maximum rotary lobe radius R Pmax .
  • the retraction side 221 in this exemplary embodiment extends over an angle of rotation of approximately 40° when the position shown is the starting position.
  • the contour follows the minimum rotary piston radius R Pmin over an angular range of approximately 20°, in order then to form the extension side 222 for a rotational angle range of approximately 120°.
  • FIG 5 shows an individual representation of a sealing element 30 which can be arranged on the sealing body 42 in an exchangeable manner.
  • the sealing element 30 has a flat contact surface 31 and an adjoining rounded, distal contact section 32 which is oriented away from the bearing point 41 .
  • the sealing element 30 also has a proximal, rounded contact section 33 oriented towards the bearing point 41, which also matches the contour of the Rotary piston 20 can come into contact.
  • the rounded contact section 32 essentially slides off the contour of the rotary piston 20 during the retraction movement, while the contact line 24 or the contact point 24 between the sealing element 30 and the rotary piston 20 runs on the flat contact surface 31 after the minimum rotary piston radius has been reached and in Direction of the rounded contact portion 32 opposite end 33 of the sealing element 30, which is rounded, migrates.
  • the line of contact 24 or the point of contact 24 thus migrates along the sealing element 30 over the angle of rotation of the rotary piston. It has proven particularly advantageous to run the small radius 33 over an angle greater than 90° before the surface 34 connects. As a result, the surface 34 acts like a scraper for the medium to be conveyed from the rotary piston.
  • the sequence of the points of contact over half a revolution of a rotary piston with two transport vanes and thus a clarification of the line of action between the extreme values R Wmax and R Wmin is shown in figure 6 shown.
  • the line of action for the extension on the extension side 222 initially provides that the swivel arm 43 is moved outwards away from the axis of rotation 21 in the direction of the maximum rotary piston radius. This is in by the ascending right section of the chart figure 6 shown. If the maximum rotary lobe radius is reached, the line of action moves to the left-hand diagram area, which is illustrated by the arrow on the upper section of the diagram that extends diagonally to the left.
  • the contact point or the contact line on the entry side 221 migrates downwards on an enlarged effective line radius, i.e. in the direction of the axis of rotation 21.
  • the contact line or the contact point migrates again to a smaller radius, which is half the lower one and right area of the diagram.
  • FIG 7 is shown in a basic representation of how the contact point 24 or the contact line 24 between the sealing element 30 and the contour of the rotary piston 20 migrates between a maximum effective line radius R Wmax and a minimum effective line radius R Wmin .
  • the sealing strip at an angle ⁇ between the straight line through the pivot point of the swivel arm 43 and the contact point of the sealing element 30 and the flat contact surface 31 in the position in the maximum rotary piston radius between 5° and 25°, in particular between 12° and 18°.
  • a quasi-linear movement of the sealing element is achieved by the comparatively large radius with a pivotable mounting of the sealing body on a pivot arm, which is 1.5 to twice the radius of the rotary piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Claims (14)

  1. Pompe à piston rotatif, comprenant
    a. un boîtier (10) qui présente une entrée (11) et une sortie (12) pour le fluide à pomper,
    b. au moins un piston rotatif (20) susceptible d'être entraîné et monté de façon mobile en rotation dans le boîtier (10) et présentant au moins deux palettes de transport (22) pourvues d'un contour, transportant le fluide à pomper de l'entrée (11) vers la sortie (12),
    c. et, par piston rotatif (20), un élément d'étanchéité (30) qui est monté sur un corps d'étanchéité (42) et qui roule sur le contour du piston rotatif (20) pendant la rotation du piston rotatif (20) et exécute un mouvement de sortie pour passer d'un diamètre minimal du piston rotatif (20) à un diamètre maximal du piston rotatif (20) et un mouvement d'entrée pour passer du diamètre maximal du piston rotatif (20) au diamètre minimal du piston rotatif (20) sur différents côtés des palettes de transport (22),
    dans laquelle
    le trajet que l'élément d'étanchéité (30) parcourt sur le côté d'entrée (221) de la palette de transport (22) pendant le mouvement d'entrée est inférieur au trajet sur le côté de sortie (222) pendant le mouvement de sortie,
    caractérisée en ce que le contour sur le côté de sortie (222) présente une courbure sans point d'inflexion, et le contour sur le côté d'entrée (221) présente au moins un point d'inflexion.
  2. Pompe à piston rotatif selon la revendication 1,
    caractérisée en ce que le rayon minimal du piston rotatif sur le côté d'entrée (221) est atteint par l'élément d'étanchéité (30) à un angle de rotation compris entre 20° et 90° à partir du rayon maximal du piston rotatif.
  3. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que le rayon maximal du piston rotatif est atteint par l'élément d'étanchéité (30) après avoir quitté le rayon minimal du piston rotatif sur le côté de sortie (222) à un angle de rotation compris entre 90° et 160°.
  4. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que la surface de la section transversale de la palette de transport (22) est plus petite sur le côté d'entrée (221) que sur le côté de sortie (222).
  5. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que le piston rotatif (20) comprend deux palettes de transport (22) dont les contours sont à symétrie ponctuelle par rapport à l'axe de rotation (21).
  6. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que le corps d'étanchéité (42) est monté pivotant sur une palette de blocage (40) à l'intérieur du boîtier (10) ou est conçu comme un coulisseau mobile en translation, sollicité par un ressort.
  7. Pompe à piston rotatif selon la revendication 6,
    caractérisée en ce que la distance entre le point de montage (41) de la palette de blocage (40) et le point de contact (24) de l'élément d'étanchéité (30) avec la palette de transport (22) est comprise entre 1,5 fois et 2 fois le rayon du piston rotatif.
  8. Pompe à piston rotatif selon l'une des revendications 6 ou 7,
    caractérisée en ce que la palette de blocage (40) est montée dans le boîtier (10) du côté de sortie et comprend un bras pivotant (43) ayant une section transversale arrondie ou ovale (430).
  9. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que l'élément d'étanchéité (30) présente une surface de contact plane (31) et au moins une portion de contact arrondie (32, 33) qui s'y raccorde.
  10. Pompe à piston rotatif selon la revendication 9,
    caractérisée en ce que la portion de contact arrondie (32, 33) s'étend sur un arc de cercle avec un angle au centre supérieur ou égal à 90°, et une surface de raclage (34) s'y raccorde.
  11. Pompe à piston rotatif selon la revendication 9 ou 10,
    caractérisée en ce que l'angle (α) entre la droite passant par le point de montage (41) du bras pivotant (43) et le point de contact (24) de l'élément d'étanchéité (30) et la surface de contact plane (31) dans le rayon maximal du piston rotatif est compris entre 5° et 25°, de préférence entre 10° et 20°, de manière particulièrement préférée entre 12° et 18°.
  12. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que, au point de contact (24) du piston rotatif (20) et de l'élément d'étanchéité (30), l'angle (β) entre la perpendiculaire (S) à la surface du piston rotatif et la tangente (T) à la direction de déplacement de l'élément d'étanchéité (30) est compris entre 0° et 70° lors du mouvement d'entrée et entre 0° et 45° lors du mouvement de sortie.
  13. Pompe à piston rotatif selon l'une des revendications précédentes,
    caractérisée en ce que la ligne d'action de l'élément d'étanchéité (30), en tant que tracé de la distance entre le point de contact (24) de l'élément d'étanchéité (30) et son point de montage (41) sur le côté de sortie (222), est différente de la ligne d'action de l'élément d'étanchéité (30) sur le côté d'entrée (221).
  14. Pompe à piston rotatif selon la revendication 13,
    caractérisée en ce que la ligne d'action de l'élément d'étanchéité présente un rayon plus petit sur le côté de sortie (222) que sur le côté d'entrée (221).
EP19705493.5A 2018-02-15 2019-02-14 Pompe à piston rotatif Active EP3752715B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018103460.1A DE102018103460B4 (de) 2018-02-15 2018-02-15 Drehkolbenpumpe
PCT/EP2019/053640 WO2019158631A1 (fr) 2018-02-15 2019-02-14 Pompe à piston rotatif

Publications (2)

Publication Number Publication Date
EP3752715A1 EP3752715A1 (fr) 2020-12-23
EP3752715B1 true EP3752715B1 (fr) 2023-03-29

Family

ID=65440967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19705493.5A Active EP3752715B1 (fr) 2018-02-15 2019-02-14 Pompe à piston rotatif

Country Status (7)

Country Link
US (1) US11927185B2 (fr)
EP (1) EP3752715B1 (fr)
CN (1) CN111742114B (fr)
DE (1) DE102018103460B4 (fr)
MX (1) MX2020005971A (fr)
WO (1) WO2019158631A1 (fr)
ZA (1) ZA202004574B (fr)

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7251C (de) * SCHNEIDER und JAQUET in Strafsburg Lösbare Bremskuppelung
DE125174C (fr) * 1900-03-15 1901-11-13
US676687A (en) * 1900-03-09 1901-06-18 Abram S Piatt Rotary engine.
GB151338A (en) * 1919-06-19 1920-09-20 Richard Bracken Improvements relating to the manufacture of churns
FR626596A (fr) * 1926-12-21 1927-09-14 Pompe rotative aspirante et foulante
NL25897C (fr) * 1930-11-06 1931-11-17 N V Machinen Gebr Stork & Co
DE850721C (de) * 1950-01-10 1952-09-29 Franz Dipl-Ing Nebel Drehkolbenpumpe, vorzugsweise zum Foerdern von Beton und trockenem Schuettgut
GB746338A (en) * 1953-05-29 1956-03-14 Franz Nebel Improvements in or relating to rotary piston pumps
DE960411C (de) * 1953-05-30 1957-03-21 Franz Nebel Dipl Ing Drehkolbenpumpe zum Foerdern dickfluessiger Stoffe, bei der ein zwanglaeufig gesteuerter Widerlagerschieber der Umrissform des Drehkolbens folgt
DE1709909U (de) * 1954-09-22 1955-11-03 Braunschweigische Maschb Ansta Einachsige drehkolbenpumpe zur foerderung von fluessigkeiten.
AT189063B (de) * 1954-11-20 1957-02-25 Franz Dipl Ing Nebel Arbeits- und Kraftmaschine für gasförmige oder flüssige Medien bzw. Fördermaschine für flüssige und trockene Medien
DE1553140A1 (de) * 1964-07-30 1970-02-05 Nebel Franz Dipl Ing Drehkolbenpumpe,auch als Presse
DE1553163A1 (de) * 1965-07-10 1970-04-23 Lederle Pumpen & Maschf Drehkolbenpumpe
DE6753460U (de) 1968-09-21 1969-04-30 Gutehoffnungshuette Sterkrade Drehkolbenpumpe
DE6927594U (de) * 1969-07-12 1971-08-12 Braunschweigische Maschb Nstal Drehkolbenpumpe.
DE7811068U1 (de) 1978-04-13 1979-02-22 Wibau (Westdeutsche Industrie- Und Strassenbau-Maschinen-Gesellschaft Mbh), 6466 Gruendau Drehkolbenpumpe, insbesondere fuer die foerderung von beton o.dgl. baustoffmischungen
CN2411360Y (zh) * 1999-11-02 2000-12-20 韩梅 同轴多个输出端的组合泵
US20050254968A1 (en) * 2004-05-14 2005-11-17 Patterson Albert W Impeller pump with reciprocating vane and non-circular rotor
GB0921968D0 (en) * 2009-12-17 2010-02-03 Epicam Ltd A rotary deviceand method of designingand makinga rotary device
GB201202255D0 (en) * 2012-02-09 2012-03-28 Quantex Patents Ltd Pumps
GB201218428D0 (en) * 2012-10-15 2012-11-28 Quantex Patents Ltd Pump assemblies
GB201504553D0 (en) * 2015-03-18 2015-05-06 Quantex Patents Ltd Pumps

Also Published As

Publication number Publication date
US11927185B2 (en) 2024-03-12
MX2020005971A (es) 2020-12-07
EP3752715A1 (fr) 2020-12-23
DE102018103460B4 (de) 2023-02-16
US20210363988A1 (en) 2021-11-25
CN111742114A (zh) 2020-10-02
ZA202004574B (en) 2022-01-26
CN111742114B (zh) 2022-06-24
WO2019158631A1 (fr) 2019-08-22
DE102018103460A1 (de) 2019-08-22

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