US3765805A - Positive displacement pump - Google Patents

Positive displacement pump Download PDF

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Publication number
US3765805A
US3765805A US00160437A US3765805DA US3765805A US 3765805 A US3765805 A US 3765805A US 00160437 A US00160437 A US 00160437A US 3765805D A US3765805D A US 3765805DA US 3765805 A US3765805 A US 3765805A
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US
United States
Prior art keywords
piston
pump
casing
entraining member
disc
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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
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US00160437A
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English (en)
Inventor
L Juhasz
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.)
KONZERV ES PAPRIKAIPARI KUTATO
Original Assignee
KONZERV ES PAPRIKAIPARI KUTATO
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member

Definitions

  • valved piston pump of which numerous constructions are known. Its disadvantages include the high cost of manufacture, the considerable work involved in carrying out repairs because of the valve and of the associated crank mechanism which is necessary to convert the rotary movement of the prime mover into a rectilinear reciprocating movement of the piston, and the considerable space requirements.
  • Pumps with a single, concentrically fitted rotor and a sliding-valve seal have the disadvantage of liability to wear and the abrasive effect of the valve, the necessity for springs to be incorporated, and, further, that the liquid path is blocked along a single line.
  • Pumps with rotating valves and rotating blades display the appreciable defect of being liable to wear at their casing and blades because of the centrifugal forces acting on the latter.
  • Screw pumps with two or more rotors are further examples of positive displacement pumps, and are highly efficient.
  • their manufacture is expensive, the pump components require to be accurately machined, they are sensitive to contamination and dry running, even briefly, leads to rapid destruction of the internal sealing surfaces.
  • An aim of this invention is to eliminate or reduce the disadvantages of known positive displacement pumps.
  • a positive displacement pump comprising a pump casing, a cover for the casing, a fluid inlet and a fluid outlet in the pump casing, a rotary drive shaft, an entraining member drivingly connected to the drive shaft, a piston pivotally connected for movement with the entraining member and formed with a recess, eccentric means secured to said cover and slidably engaging in said recess for reversibly oscillating the piston with variable eccentricity, and sealing means on the entraining member disposed so that the piston divides the interior of the pump casing into two mutually sealed chambers of variable volume, whereby on rotating the shaft through 360 the said chambers are each connected twice to said inlet and to said outlet to produce a double-acting pump.
  • the entraining member is a disc sealingly connected to said shaft, the sealing means being constituted by two peripheral arcuate, segmental lands on the disc. 7
  • the eccentric means may consist of a radially displaceable stay bolt detachably secured to the cover, and a bearing surrounding the stay bolt and engaged in the recess.
  • a wear resistant lining is provided on the wall of the recess engaging with the bearing.
  • a wear-resistant bush surrounds the bearing and is adapted to slide on one side of the recess only.
  • the disc may carry an upstanding, eccentrically disposed, integral pivot pin, and the piston has a bore in which said pin'is received.
  • the piston is preferably substantially tuning-fork shaped, with the limbs of the fork connected at their end remote from the stem of the fork, the bore being in the stem.
  • FIG. 1 shows a pump according to this invention partly in front elevation and partly in section, and with its cover removed for the sake of clarity,
  • FIG. 2 is a section through the pump taken on line A-B of FIG. 1,
  • FIG. 3 is an enlarged perspective representation of the pump disc forming part of the pump of FIG. 1, and
  • FIGS. 4 to 6 are schematic views showing the pump disc and rotating piston of FIG. 1 during seccessive stages of operation.
  • FIGS. 1 and 2 there is shown a rotary pump according to the invention. More particularly, referring to FIGS. 1 and 2a rotary disc 2 is arranged in a pump casing 1 and is readily detachably keyed to a pump shaft 3. The periphery of the disc 2 is constructed in such a way that the disc 2 serves for both opening and closing of the inlet and outlet openings (indicated by appropriate arrows) during rotation.
  • a pin 4 rotatably supporting a rotary tuning-fork shaped piston 5 in a piston bore, is rigidly connected with the disc 2.
  • a cover plate 6 serves to seal the pump casing I and is detachably secured thereto by any suitable means such as screwing, e.g., with headless screws and wing nuts.
  • a stay bolt 7 is detachably and eccentrically secured to the cover 6 and, according to the desired pumping rate, can be moved radially away from the centre of the cover 6 into a different bore constructed in and located along the vertical centre line of the cover 6.
  • the stay bolt7 is journalled in a cylindrical rolling bearing 8 inserted to make a lit in a wear-resistant bush which slides through respectively 180 alternatingly on either side ofa recess 9 formed in the piston and lined with wear-resistant shoes 10.
  • the outer periphery of the bush of the rolling bearing 8 accommodating the stay bolt 7 is in contact with only one surface of the track, i.e., makes contact withone of the shoes only on one side of the recess 9.
  • a liquid seal, indicated by cross-latching, between the shaft 3 and the casing 1 is provided by means of a packing sleeve. Via appropriate bearings the pump shaft 3 is connected to a reduction gear driven by an electric motor (not shown).
  • the perspective view of the pump disc .2 shown in FIG. 3 reveals that the disc 2 is provided with a central bore and is reinforced or thickened on both sides. These reinforcements a and b are in the form of peripheral, segmental lands constituting sealing means.
  • the pin 4 is permanently secured to the disc 2 in the centre of the sealing element a. In order to ensure that there is sufficient space between the pin 4 and the centre of the disc 2, the sealing element a is thinner than the sealing element 17.
  • the top and bottom surfaces (as viewed in FIG. 1) of the piston S are provided with packings ll, 12 and are matched to the internal surfaces of the sealing elements a, b; while its left and right end surfaces (as viewed in FIG. 2) are so matched to the cover 6 and the disc 2, respectively, that the piston divides the interior of the casing 1 into two mutually sealed chambers of variable volume between which no flow of liquid can occur.
  • the wear at the two ends of the piston 5 and of the inner surfaces of the sealing elements a and b can be compensated for by inserting sealing platelets of a thickness matching the degree of wear underneath the packings ll, 12.
  • the shaft 3 is set in rotation by the electric motor and reducing gear.
  • the disc 2 serves as the entraining member for the rotating piston 5, seated on the pin 4 permanently secured to the rotating disc 2.
  • the piston 5 is also supported on the stay bolt 7 via the rolling bearing 8 and by the bush surrounding the bearing 8 sliding longitudinally on one side or the other of the recess 9 altematingly after respective 180 turns of the shaft 3, i.e., on the shoes 10 located there.
  • the piston 5 On rotation of the disc 2 the piston 5 is deflected by a variable amount dependent on the distance between the pump shaft'3 and the stay bolt 7. The movement of the piston 5 produces suction, i.e'., an increase in volume, on one side. During this phase of the movement, the suction and delivery openings are in the open position. When the direction of oscillation of the piston 5 is reversed no communication obtains between the suction and delivery sides (suction and pressure cham bers), because the gaps between the disc 2 and the sealing elements a and b are closed. During rotation of the shaft 3 the pivot pin 4 approaches close to the stray bolt 7 and during the second half of the rotation moves away from same.
  • the distance between the pin secured to the rotating disc and the stay bolt secured to the lid must be controlled in such a manner that the closest distance that the pin and bolt approach to one another is not less than the distance between the stay bolt and the upper edge of the piston, i.e., these distances should be approximately the same if possible.
  • FIG. 4 shows the disc 2 containing the piston 5 during the rotation phase when the sealing element a closes the suction (inlet) opening and sealing element b closes the delivery (outlet) opening.
  • the chamber that has the larger volume during suction (shown shaded) is filled with liquid.
  • both the suction and delivery openings are open and the pump sucks the liquid through the suction opening into the suctionside chamber which is increasing in volume, while liquid is forced out of the delivery chamber, which is of decreasing volume, through the delivery opening.
  • FIG. 6 shows a position similar to that illustrated in FIG. 4 i.e., both the suction and delivery openings are closed and the disc 2 moves the delivery chamber (shown shaded) filled with liquid in the direction of the delivery opening and the emptied chamber of reduced volume in the direction of the suction opening.
  • the pump according to the illustrated embodiment of the invention can be manufactured relatively cheaply, its operation is reliable and economic, its is notparticularly susceptible to interfering effects and faults are relatively easily diagnosed and eliminated. Assembling and dismantling, elimination of leaks and renewing of worn packings after prolonged use can be carried out very quickly.
  • the piston 5 After removing the det'achably secured cover 6 from the casing l, the piston 5 can be simply pulled off the pivot pin 4.
  • the gaps formed after prolonged use can be eliminated by laying platelets of a thickness matching the degree of wear underneath the insert incorporated at the two ends of the piston.
  • the drive shaft is simply and reliably sealed.
  • a positive displacement pump comprising a pump casing having a fluid inlet and a fluid outlet, a rotary drive shaft extending through the casing, an entraining member carried by the drive shaft for rotation with the drive shaft in said casing, a piston carried by said entraining member for rotation with said entraining member in said casing, said piston dividing the interior of said casing into a pair of chambers of variable volume, means pivotally interconnecting said piston and said entraining member for pivotal movement of said piston relative to said entraining member about an axis eccentric to the drive shaft, said piston having a recess therein, and eccentric means secured to said casing and slidably disposed in said recess for reversibly oscillating the piston upon rotation of said entraining member.
  • a pump as claimed in claim 1 said casing having a cover in which said eccentric means are secured.
  • a pump as claimed in claim 1 and sealing means carried by said entraining member and cooperating with said piston to seal said chambers from each other.
  • a pump as claimed in claim 3 said entraining member being a disc, said sealing means comprising 8.
  • the piston having substantially the shape of a tuning fork having a stem and limbs branching from said stem and disposed on either side of said eccentric means, said limbs being connected at their ends remote from said stem, said bore being in said stem.
  • a pump as claimed in claim 1 the eccentricity of said eccentric axis being greater than the eccentricity of said eccentric means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US00160437A 1970-07-23 1971-07-07 Positive displacement pump Expired - Lifetime US3765805A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
HUKO002355 1970-07-23

Publications (1)

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US3765805A true US3765805A (en) 1973-10-16

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ID=10997873

Family Applications (1)

Application Number Title Priority Date Filing Date
US00160437A Expired - Lifetime US3765805A (en) 1970-07-23 1971-07-07 Positive displacement pump

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US (1) US3765805A (enExample)
CS (1) CS162913B1 (enExample)
DE (1) DE2131475A1 (enExample)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4861236A (en) * 1988-09-26 1989-08-29 Ryon Kustes Birotational pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2151848A (en) * 1937-02-19 1939-03-28 Grunert Kurt Compressor pump, and the like
US2215873A (en) * 1938-06-14 1940-09-24 Gahm Samuel Bernard Motor driven pump
GB789375A (en) * 1953-04-29 1958-01-22 Henri Delmer A pump or engine of the oscillating-vane type
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2151848A (en) * 1937-02-19 1939-03-28 Grunert Kurt Compressor pump, and the like
US2215873A (en) * 1938-06-14 1940-09-24 Gahm Samuel Bernard Motor driven pump
GB789375A (en) * 1953-04-29 1958-01-22 Henri Delmer A pump or engine of the oscillating-vane type
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4861236A (en) * 1988-09-26 1989-08-29 Ryon Kustes Birotational pump

Also Published As

Publication number Publication date
DE2131475A1 (de) 1972-01-27
CS162913B1 (enExample) 1975-07-15

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