EP1329635B1 - Rotationspumpe - Google Patents

Rotationspumpe Download PDF

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Publication number
EP1329635B1
EP1329635B1 EP03008760A EP03008760A EP1329635B1 EP 1329635 B1 EP1329635 B1 EP 1329635B1 EP 03008760 A EP03008760 A EP 03008760A EP 03008760 A EP03008760 A EP 03008760A EP 1329635 B1 EP1329635 B1 EP 1329635B1
Authority
EP
European Patent Office
Prior art keywords
cover
piston
rotor
air cylinder
end 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
Application number
EP03008760A
Other languages
English (en)
French (fr)
Other versions
EP1329635A1 (de
Inventor
Kazuo Morita
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.)
Nakakin Co Ltd
Original Assignee
Nakakin Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from JP10163699A external-priority patent/JP3366876B2/ja
Priority claimed from JP10163599A external-priority patent/JP3366875B2/ja
Priority claimed from JP10163499A external-priority patent/JP3366874B2/ja
Application filed by Nakakin Co Ltd filed Critical Nakakin Co Ltd
Priority claimed from EP00107112A external-priority patent/EP1043502B1/de
Publication of EP1329635A1 publication Critical patent/EP1329635A1/de
Application granted granted Critical
Publication of EP1329635B1 publication Critical patent/EP1329635B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/005—Removing contaminants, deposits or scale from the pump; Cleaning
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft

Definitions

  • the present invention relates to a rotary pump suitable for transporting liquid foods.
  • Figs. 10 and 11 show the commonly owned prior art.
  • the reference numerals 1A and 1B denotes rotors. From each of rotors 1A and 1B, a short rotor shaft 2 is provided from the central portion of one end surface thereof. A threaded bore 3 is coaxially formed from the end surface of the rotor shaft 2. A pumping segment 4 is integrally formed on the outer peripheral portion of each rotor 1A and 1B.
  • the reference numeral 6 denotes a pump casing.
  • the pump casing 6 includes a main casing defining a concave pumping chamber 7 loosely accommodating the pumping segments 4 or revolution therein and formed with a suction port 8 and a discharge port 9, and a casing cover 11 detachably attached on the main casing 10 flush with the end surface of each rotor 1A and 1B by means of bolts and nuts.
  • the reference numeral 12A and 12B denote hollow rotor drive shafts provided corresponding to the rotors 1A and 1B.
  • the rotor drive shaft is supported by means of a bearing 14 within a gearbox 13 for the drive shaft for rotation and restricting movement in an axial direction.
  • the reference numeral 15 denotes a rotor fastening bolt inserted through a hollow portion of each of the hollow rotor drive shafts 12A and 12B from one end to the other end.
  • a bolt head 15a of the rotor fastening bolt 15 is engaged with one end surface rotor drive shaft 15.
  • a hollow portion 16a at the tip end of each rotor drive shaft 12A and 12B is externally engaged with the rotor shaft 2 of each rotor 1A and 1B.
  • a threaded portion 15b at the tip end of the rotor fastening bolt 15 is threadingly engaged with the threaded bore 3 of the rotor shaft 2.
  • the reference numeral 17 denotes a gearbox for a transmission shaft.
  • a transmission shaft 21 is rotatably supported via bearings 18 and 19 within the gearbox 17, and is connected to a motor (not shown).
  • a gear 22 is mounted on the transmission shaft 21.
  • gears 23a and 23b for transmitting rotation for driving a pair of rotor drive shafts 12A and 12B in mutually opposite direction in synchronism with each other and a gear 23c meshing with the gear 22 mounted on the transmission shaft 21 are provided. Accordingly, a driving force of the motor to be transmitted to the transmission shaft 21 is transmitted to one rotor shaft 12A via the gears 22 and 23c. The driving force of the rotor drive shaft 12A is transmitted to the other rotor drive shaft 12B via the gears 23a and 23b.
  • each rotor shaft 2 is engaged with the hollow portion 16a at the tip end of the hollow rotor drive shaft 12 supported within the gearbox 13.
  • the rotor fastening bolt 15 is inserted within the rotor drive shaft 12 from one end to threadingly engage the threaded portion 15b at the tip end thereof with the threaded bore 3 of the rotor shaft 2.
  • the bolt head 15a is rotated by a rotary tool, such as spanner or the like for tightening to draw each rotor 1A and 1 B toward the rotor drive shaft 12 for fixedly fastening.
  • overall inner side surface of the casing cover 11 is a flat surface forming in flush with the external end surface of the rotors 1A and 1B so as not to form recessed portion between the rotors 1A and 1B. Therefore, retention of the transported liquid flowing through the pumping chamber 7 will never be caused. Accordingly, washing of the pumping chamber can be easily performed.
  • the gearbox 16 for the transmission shaft 21 is provided separately from the gearbox 13 of the drive shaft, and driving force has to be transmitted to the rotor drive shaft 12 via the gear mounted on the transmission shaft 21 on the side of the motor and the gear 23a housed within the gearbox 13 for the drive shaft.
  • the transmission shaft 21 for transmitting the rotational torque of the motor to the rotor drive shafts 12A and 12B and thus at least three shaft in total are required. Therefore, the construction is inherently complicate.
  • the rotor fastening bolt 15 inserted into the hollow portion of the hollow rotor drive shaft 12 is rotated by rotating the bolt head 15 at the rear end portion with the rotary tool in the condition where the threaded portion 15b at the tip end is threadingly engaged with the rotor 1A (1B) to draw the rotor 1A backward by the rotor fastening bolt 15 and to abut the bolt head 15a onto the end surface of the hollow rotor drive shaft 12.
  • the rotors 1A and 1B can be disassembled easily only by loosening the rotor fastening bolt 15 by rotatingly operating the bolt head 1 5a.
  • the mating surfaces of the rotor 1A (1B) and opposing casing cover 11 maybe formed in flush. Coupling between the rotor 1A (1B) and the hollow rotor drive shaft 12A (12B) is effected by externally engaging the tip end portion of the drive shaft and by maintaining external engagement by drawing force applied by tightening the rotor fastening bolt 15 into the rotor shaft 12. Therefore, connection force therebetween is insufficient. Also, centering of the rotor 1A (1B) and the hollow rotor drive shaft 12A (12B) cannot be complete to possibly cause center vibration.
  • the conventionally rotary pump defines the pumping chamber 7 with the main casing 10 and the casing cover 11 mounted thereon.
  • a pair of rotors 1A and 1B are housed within the pumping chamber 7.
  • the end surface 1a of the casing cover 11 of each of rotors 1A and 1B are placed in substantially contacting state with a minimum fine gap required for permitting rotation of the rotor 1A and 1B.
  • Both rotors 1A and 1B are synchronously rotated in mutually opposite directions by mutually engaging the pumping segments 4 of the rotors 1A and 1B by the rotor drive shafts 12 as shown by the arrows of Fig. 11.
  • the present invention has been worked out in view of the problems set forth above. Therefore, it is the first object of the present invention to construct a rotary pump with simple construction by omitting a transmission shaft on the side of a motor and whereby to make a cost of the rotary pump as low as possible, with maintaining feature that assembling and disassembling is facilitated.
  • a rotary pump comprises the features of claims 1 to 3.
  • a rotary pump comprises:
  • a rotary pump comprises:
  • a rotary pump comprises:
  • a rotary pump comprises:
  • Fig. 1 shows a rotary pump.
  • a construction of the rotary pump is basically the same as the prior art shown in Figs. 10 and 11.
  • a pump casing 30 is constructed with a main casing 43 which define a concave pumping chamber 42 one the side of one end surface for housing a pair of rotors 31A and 31B (which will be identified by the reference numeral 31 as generally referred to) and loosely engage with pumping segments 32 which are integrally formed with the rotors 31A and 31B for rotation therein, and also defines a suction port 50 and a discharge port 51 communicated with the pumping chamber 42, and a casing cover 44 detachably mounted on the main casing 43 by bolts 52 in flush with the end surface of a pair of rotors 31.
  • a pair of rotors 31 are mounted o n hollow rotary drive shafts 34A and 34B (which will be identified by reference numeral 34 as generally referred to) by tightening rotor fastening bolt 36 into hollow portions 35 of the rotary drive shafts 34.
  • particular mounting structure is differentiated from the prior art. As shown in Fig. 3 a through opening 53 formed with an internal peripheral surface 46 with spline groove and a recessed portion 48 communicated with the through opening 53, having greater diameter that the through opening 53 and opening on the side of the casing cover 44 are formed in the rotors 31, respectively.
  • Tip ends of a pair of hollow rotor drive shafts are formed as spline shafts 45 engaging with the spline of the inner periphery 46 of the through opening 53 so that the rotors 31 and the hollow rotary drive shafts 34 are integrated for rotation in accurately and coaxially aligned condition by engaging the spline shafts 45 with the through openings 53.
  • the rotor fastening bolt 36 integrally formed with flange portion 47 which engages with the recessed portion 48 formed in the rotor 31, is inserted from the side of the casing cover 44.
  • the rotor fastening bolt 36 is then inserted into the hollow portion 35 of the hollow rotor drive shaft 34 to extend a tip end thereof from an outer end surface of the hollow rotor drive shaft to be exposed therefrom.
  • a fastening nut 49 is engaged with the exposed tip end of the rotor fastening bolt 36.
  • the rotor 31 By tightening the fastening nut 49 onto the rotor fastening bolt 36, the rotor 31 is drawn toward the hollow rotor drive shaft 34 to be fixed in a condition firmly abutting onto an inner end surface at a tip end of the hollow rotor drive shaft 34. It should be noted that in the condition where the flange 47 received within the recessed portion 48, the flange 47 and the rotor 31 form a flush surface mating with the casing cover 44.
  • the fastening nut 49 may be replaced with a washer to engage the washer with the rotor fastening bolt 36 and a lock nut 57 is employed as the fastening nut so that the fastening nut 57 is engaged and tightened with the rotor fastening bolt 36 via the washer to achieve the similar effect, as a matter of course.
  • a sealing member 72 such as an O ring is disposed between the flange portion 47 and the recessed portion 48, and in conjunction therewith, the flange 47 and the rotor 31 form the flash surface to be mated with casing cover 44 in the condition where the flange 47 is engaged with the recessed portion 48, as shown in Fig. 3.
  • the reference numerals 73 and 74 denote mechanical seals for maintaining between the pump chamber 42 and the outside in liquid tight state.
  • the rotor fastening bolt 36 is provided with the foregoing flange portion 47 on the tip end portion thereof to engage with the recessed portion 48 provided in the rotor 31.
  • the rotor fastening bolt 36 integrally with the rotor 31 to extend axially as shown in Fig. 4.
  • a pair of the hollow rotor drive shafts 34 (34A and 34B) are supported by bearings 55 and 56 in a gearbox 33 (housing 54) which is located adjacent the pump casing 30. Also, within the gearbox 33, gears 37 and 37 for synchronous driving are provided for respective of the hollow rotor drive shafts 34 so that the hollow rotor drive shafts 34A and 34B are synchronously driven for rotation in mutually opposite directions.
  • one hollow rotor drive shaft 34A is extended from the gearbox 33 in greater extent to form an extended drive shaft portion 39.
  • a cylindrical frame shaped transmission coupling 42 which is important feature of the present invention, is connected.
  • the transmission coupling 42 is formed with a cylindrical frame shaped coupling body 59 having a large operation window 58 on the circumference thereof, a boss hole projected on one end surface for connection, a connecting frame 62 for connecting a coupling 61 on the side of the other end portion of the transmission member, an operation window 63 and a connecting hole 64.
  • the extended drive shaft 39 is engaged with the connecting boss hole 60 of the transmission coupling 41 to establish a key coupling with a key groove 66 and a key 67 provided between the extended drive shaft 39 and the transmission coupling 41.
  • a connecting nut 68 is engaged and tightened for coupling the extended drive shaft portion 39, and namely the hollow rotor drive shaft 34 with the transmission coupling 41 for integral rotation.
  • a transmission member 69 connected on the side of the motor is connected to the transmission coupling 41 via the coupling on the side of the transmission member by bolt and nut 70, the connecting hole 64 of the connecting frame 62 engaged with the bolt and nut 70 and a buffering connecting member 71 engaged with the connecting hole 64.
  • a rotational force of the transmission member 69 connected on the side of the motor is transmitted to the transmission coupling 41 via the coupling 61 on the side of the transmission member.
  • the coupling 41 drives the hollow rotor drive shaft 34A on one side which is connected directly to the coupling 41, and drives the other hollow rotor drive shaft 34B via a pair of synchronous driving gears 37 and 38.
  • a pair of rotors 31 are synchronously rotated in mutually opposite directions.
  • the rotor drive shaft 34 is inserted into the through opening 53 in such a manner that the spline shaft 45 of the rotor drive shaft 34 is engaged with spline surface of the rotor 31.
  • the rotor fastening bolt 36 is then inserted into the hollow portion 35 of the hollow rotor drive shaft 34 from the side of the casing cover 44.
  • the operator tightens the fastening nut (washer) 49 and the lock nut 57 (fastening nut) onto the rotor fastening bolt 36 within the operation space 40 through the operation window 58 or 63.
  • the rotary pump can be easily assembled.
  • the spline shaft 45 at the tip end portion of the hollow rotor drive shaft is engaged with the spline surface on the inner periphery of the through opening 53 of the rotor 31, and the hollow rotor drive shaft 34 and the rotor 31 are rigidly secured with each other by the rotor fastening bolt 36. Therefore, slip will never be caused therebetween to assure integral rotation. Furthermore, concentric relationship between the rotor and the hollow rotor drive shaft can be maintained for a long period.
  • Figs. 5 to 9 show an embodiment of the rotary pump according to the present invention. It should be noted that, in the following disclosure, components common to Figs. 1 to 4, will be identified by the same reference numerals, and detailed discussion for such common components will be omitted in order to avoid redundant discussion and whereby to keep the disclosure simple enough to facilitate clear understanding of the present invention. Therefore, the following disclosure will be concentrated to the particular construction of the shown embodiment.
  • a space 80 having a given width in a thickness direction of a casing cover 44A is defined at the center portion of the casing cover 44A with the end surface 31a of the rotor 31 by forming a recess on the surface of the casing cover 44A mating with the end surface 31a of the rotor 31.
  • a cover piston 81 is engaged with the peripheral wall defining the space 80 in gas tight fashion for reciprocal motion in the thickness direction, namely toward and away from the end surface 31a of the rotor 31.
  • An air cylinder 82 is mounted on the casing cover 44A in coaxial relationship with the cover piston 81 by mounting bolts 83.
  • the air cylinder 82 is constructed with a cylinder body 82a, a cylinder cover 86 located on the side of the casing cover 44A, a cylinder cover 87 on the opposite side, a piston 88 slidingly reciprocating within the cylinder body 82a, a piston rods 83a and 83b (which will be identified by reference numeral 83 as generally referred to) extending from both sides of the piston 88, and inlet and outlet ports and 92 communicated with forward drive side and reverse drive side cylinder chambers 89 and 90 defined on both sides of the piston 88.
  • the cylinder cover 86 on the side of the casing cover 44A may be formed to be common with the casing cover 44A.
  • the cylinder cover 86 may be provided separately on the side of the air cylinder 82.
  • the space 80 of the casing cover 44A is formed through the casing cover 44A.
  • the cylinder cover 86 formed separately on the side of the air cylinder 82 may serve as the casing cover 44A and the cylinder cover 86 and the casing cover may be formed integrally with each other.
  • the cylinder cover 86 of the air cylinder is mounted directly on the main casing 43 as the casing cover 44A by the bolts.
  • the end surface 81a on the side of the rotor 31 of the cover piston 8 is mated with the inner end surface 44a of the casing cover 44A for tight fitting with each other.
  • the end surface 81a of the rotor 31 is substantially in contact with the end surface 31a of the rotor 31 with maintaining a fine gap therebetween.
  • the piston rod 83a extended from the piston 88 of the air cylinder 82 toward the casing cover 44A is integrally connected to the cover piston 81 through the cylinder cover 86.
  • the piston rod 83b projecting from the piston toward the opposite side is extended externally through the other cylinder cover 87. More accurately, the piston rod 83b is formed with a collar 94 engaging with a small.diameter portion 93 and a nut 95 threadingly engaged with a thread portion at the tip end of the small diameter portion in order to secure the collar 94.
  • a lock cylinder 85 is coaxially mounted as shown in Fig. 5.
  • a lock bolt 84 is threadingly engaged, which lock bolt may abut against a tip end surface of the piston rod 83b of the air cylinder 82 and is movable back and forth along motion direction of the piston rod 83b.
  • a lock nut 46 is threadingly engaged for locking the lock bolt 84 at a predetermined position.
  • the lock cylinder 85 is not limited to the cylindrical shape but can be any appropriate shape. Namely, the lock cylinder is only required to be any appropriate shape of the frame body, to which the lock bolt 84 is threadingly engaged for linear motion in back and forth direction.
  • Fig. 6 shows a modification of another embodiment of the rotary pump, in which shape of the cover piston 81A to be engaged with the space 80 in gas tight fashion.
  • an end surface 81a at one side of the rotor of the cover piston 81 In contrast to this, the present invention shown in Fig. 6 has the cover piston 81A, in which a head portion 99a of the bolt 99is projected from the rotor 31. Therefore, a recessed portion 100 is provided for, in which a head portion 99a of the bolt 99 is projected from the rotor 31. Therefore, a recessed portion 100 is provided for receiving the heat portion 99a of the bolt 99.
  • a rotor drive shaft 117 is engaged at the center portion of the rotor 21 for mounting the rotor 31 on the rotor drive shaft 117.
  • the bolt 99 is threadingly engaged with the threaded hole 102 provided on the end surface of the rotor drive shaft 117.
  • the rotor 31 is mounted on the rotor drive shaft.
  • the lock bolt 84 of the lock cylinder 85 Upon automatic operation by the air cylinder 82, the lock bolt 84 of the lock cylinder 85 is retracted from the tip and surface of the piston rod 83b at the right side of the air cylinder 82 in the drawing.
  • the lock bolt 84 of the lock cylinder 85 may be kept in contact with the tip end surface of the piston rod 83 so as to prevent the cover pistons 81 and 81A from being retracted from the end surface 31a of the piston to reduce pumping effect even when the internal pressure of the pumping chamber 32 is elevated to be higher than or equal to a predetermined pressure to overcome the biasing force of the piston 88 of the air cylinder 82.
  • a griping portion of the lock bolt 42 is operated to retract the lock bolt 84 from the tip end surface of the piston rod 83 and also, the air is introduced into the reverse side cylinder chamber 90 under pressure and the air in the cylinder chamber 89 on the opposite side is discharged through the discharge port 92, and in conjunction therewith the air in the space 80 defined by the casing cover 44 and the cover piston 81 is discharged through the air discharge opening 103.
  • the piston 88 is moved toward right in the drawing.
  • the cover pistons 81 and 81A connected to the piston rod 83a is retracted away from the end surface 31a of the rotor 31 to define a large gap 104 between the cover piston 81 and 81A and the end surface of the rotor 31.
  • large amount of the washing water may flow as shown by arrow and discharged through the discharge port 51. Larger amount and higher flow velocity may result in higher washing effect to effectively improve washing effect for the pumping chamber 42, particularly the end surface 31a of the rotor 31 and the inner end surface 44a of the casing cover 44 opposing to the end surface 31a.
  • the rotor 31 may be rotated at low speed or held stopped.
  • the washing water is preferable fed by a dedicated pump for the washing water. In this case, it is advantageous to make the bypass piping for feeding the washing water unnecessary in the rotary pump.
  • the cover pistons 81 and 81A are placed in opposition to the pumping action position of the end surface 31a of the rotor 31 by the piston 88 biased by the air pressure.
  • the discharge pressure of the pump is elevated beyond the given pressure to build up a pressure to retract the cover pistons 81 and 81A away from the end surface 31a of the rotor 31 overcoming the biasing pressure of the piston 88, the cover piston 81 is retracted from the end surface 31a of the rotor 31 to lower pumping function and relief the discharge pressure.
  • the discharge pressure of the rotary pump can be regulated.
  • FIG. 9 shows a further embodiment of the rotary pump according to the present invention.
  • the shown embodiment is provided with another air cylinder 82A mounted by bolts 105, in addition to the air cylinder 82.
  • Respective pistons 36 and 106 are connected to piston rod 108 extending through a common cylinder cover 107.
  • the lock bolt 84 is threadingly engaged with the cylinder cover 109 of the later air cylinder 82.
  • two air cylinders 82 and 82A are connected with each other. However, more than two air cylinders may be employed.
  • the lock bolt 84 is threadingly engaged with the rearmost air cylinder 82A.
  • the cover pistons 81 and 81A are held by both pistons 88 and 106 to maintain the cover pistons 8 1 and 81 A at the position opposing to the pumping action position of the end surface 31 a of the rotor 31 at greater force.
  • the cover piston 81 and 81A are held at predetermined action position by the lock bolt 84 as required.
  • the reference numerals 113 and 114 denote inlet and outlet ports provided in reverse side cylinder chambers 90 and 115 of both air cylinders 82 and 82A, and the reference numeral 116 may be a ventilation aperture provided in the space 80.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (3)

  1. Kreiselpumpe, geeignet für den Transport flüssiger Lebensmittel, umfassend:
    ein Hauptgehäuse (43);
    eine Gehäuseabdeckung (44A), die mit dem Hauptgehäuse (43) so zusammenwirkt, dass dazwischen eine Pumpkammer (42) definiert wird;
    ein Paar von Rotoren (31), die innerhalb der Pumpkammer (42) mit gegenseitig im Eingriff stehenden Pumpsegmenten (32) zur synchronen Umdrehung in einander entgegengesetzten Richtungen aufgenommen sind;
    einen Raum (80), der in einem Abschnitt der Gehäuseabdeckung definiert ist;
    einen Abdeckungskolben (81), der innerhalb des Raums zu einer Vor- und Zurück-Bewegung in Bezug auf eine Endoberfläche (31a) des Rotors (31) angeordnet ist;
    gekennzeichnet durch
    einen Verriegelungszylinder (85), der einen Verriegelungsbolzen (84) aufweist, welcher an der Gehäuseabdeckung (44A) zur Beschränkung der Bewegung des Abdeckungskolbens (81) mittels des Verriegelungsbolzens (84) befestigt ist.
  2. Kreiselpumpe gemäß Anspruch 1,
    dadurch gekennzeichnet, dass
    ein Luftzylinder (82) an der Gehäuseabdeckung (44A) befestigt ist und eine Kolbenstange (83a) aufweist;
    ein Verriegelungszylinder einen Verriegelungsbolzen (84) aufweist, der an dem Luftzylinder befestigt ist;
    wobei der Abdeckungskolben mit einer Kolbenstange (3a) verbunden ist, die von einer Endfläche des Kolbens (88) des Luftzylinders (82) hervorsteht;
    und wobei eine Kolbenstange (83b), die von der anderen Endfläche des Kolbens (88) des Luftzylinders (82) hervorsteht, an den Verriegelungsbolzen zur Beschränkung der Bewegung des Abdeckungskolbens (81) mittels des Verriegelungsbolzens (84) anstößt.
  3. Kreiselpumpe gemäß Anspruch 2,
    dadurch gekennzeichnet, dass
    eine Vielzahl von Luftzylindern (82, 82A) an der Gehäuseabdeckung (44A) in einem Zustand befestigt ist, in dem deren Kolbenstangen (108) miteinander verbunden sind und der Abdeckungskolben mit einer Kolbenstange (83) verbunden ist und eine Kolbenstange (83) aufweist, mit der der Abdeckungskolben verbunden ist;
    wobei ein Verriegelungsbolzen (84) koaxial an dem Luftzylinder (82A) an der hintersten Position vorgesehen ist und der Abdeckungskolben (81) mit der Kolbenstange (83) des Luftzylinders (82) an der vordersten Seite verbunden ist;
    und wobei ein Kolben (54) oder eine Kolbenstange (54a) des Luftzylinders (82a) an der hintersten Position in Kontakt mit dem Verriegelungsbolzen zur Beschränkung der Bewegung des Abdeckungskolbens mittels des Verriegelungsbolzens in Kontakt steht.
EP03008760A 1999-04-08 2000-04-06 Rotationspumpe Expired - Lifetime EP1329635B1 (de)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP10163699A JP3366876B2 (ja) 1999-04-08 1999-04-08 ロータリーポンプ
JP10163699 1999-04-08
JP10163599 1999-04-08
JP10163499 1999-04-08
JP10163599A JP3366875B2 (ja) 1999-04-08 1999-04-08 ロータリーポンプ
JP10163499A JP3366874B2 (ja) 1999-04-08 1999-04-08 ロータリーポンプ
EP00107112A EP1043502B1 (de) 1999-04-08 2000-04-06 Rotationspumpe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP00107112A Division EP1043502B1 (de) 1999-04-08 2000-04-06 Rotationspumpe

Publications (2)

Publication Number Publication Date
EP1329635A1 EP1329635A1 (de) 2003-07-23
EP1329635B1 true EP1329635B1 (de) 2007-06-20

Family

ID=33313968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03008760A Expired - Lifetime EP1329635B1 (de) 1999-04-08 2000-04-06 Rotationspumpe

Country Status (2)

Country Link
EP (1) EP1329635B1 (de)
DE (2) DE60014742T2 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013120483A1 (de) * 2012-02-17 2013-08-22 Netzsch Mohnopumpen Gmbh Drehkolbenpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4073605A (en) * 1976-09-15 1978-02-14 Crepaco, Inc. Rotary pump construction with cleaning feature
US4453901A (en) * 1983-02-28 1984-06-12 Ladish Co. Positive displacement pump
GB8806242D0 (en) * 1988-03-16 1988-04-13 Ibex Eng Co Ltd Improved lobe pump
GB9004594D0 (en) * 1990-02-28 1990-04-25 Apv Crepaco Pumps Ltd Improvements in or relating to rotary pumps
JP2563865Y2 (ja) * 1992-06-29 1998-02-25 株式会社ナカキン ロータリーポンプ
IT1285662B1 (it) * 1996-04-04 1998-06-18 Catta 27 S R L Pompa idraulica, in particolare del tipo a lobi, con predisposizioni per il lavaggio automatico interno e con spie di malfunzionamento,
DE19646469C2 (de) * 1996-11-11 1999-06-24 Andreas Czwaluk Drehkolbenpumpe

Also Published As

Publication number Publication date
DE60035295T2 (de) 2008-02-21
EP1329635A1 (de) 2003-07-23
DE60014742D1 (de) 2004-11-18
DE60014742T2 (de) 2006-03-09
DE60035295D1 (de) 2007-08-02

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