US1492456A - Rotary pump - Google Patents

Rotary pump Download PDF

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Publication number
US1492456A
US1492456A US631563A US63156323A US1492456A US 1492456 A US1492456 A US 1492456A US 631563 A US631563 A US 631563A US 63156323 A US63156323 A US 63156323A US 1492456 A US1492456 A US 1492456A
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Prior art keywords
piston
fluid passage
pump
cylinder
inoperative
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Expired - Lifetime
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US631563A
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Hansen-Ellehammer Ja Christian
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Priority to US631563A priority Critical patent/US1492456A/en
Priority to US694581A priority patent/US1535832A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3443—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation with a separation element located between the inlet and outlet opening

Definitions

  • the present invention relates to a rotary pump having an essentially circular fluid passage between the piston cylinder and the pump body which in the inoperative section has a projection separating the suction side from the delivery side.
  • the pumps of this kind heretofore employed show the disadvantage that they would quickly wear onthe guiding surfaces which are situated within the range of the fluid when the pump is employed for conveying impure water. This becomes partic- .ularly apparent when such water contains essential quantities of sandor grit which H within a very short time will completely wear out the guiding surfaces.
  • the present invention aims at obviating this disadvantage by disposing the entire controlling mechanism towards the center, outside of the range of the fluid so that the centrifugal forces on the fluid will hold sand particles and the like away from the guiding surfaces.
  • the enclosing walls of the pump body are made with pockets or recesses at such pointswhere the pistons pass from the inoperative section to the operative section. It is thereby obtained that the pistons are practically instantly relieved, as immediately on the pistons leaving the said pockets, the fluid can flow from the one side of the pistons to the other side.
  • FIG. 1 is a vertical section through a con structional. form of the pump andatright angles to the spindle of the pump, and
  • Fig. 2'v is an axial section through the pump.
  • the pump has an essentially circular fluid passage 1 between the piston cylinder 2 and the pump body 3.
  • the latter has on the inoperative section a projection 4 separating delivery side .12.
  • radially' slidable pistons 5 and 6 having tenons 7 and 8, respectively, outside of the fluid passage, and the axes of which are parallel to the axis, of rotation of the jump.
  • These tenons are controlled by 'uide surfaces formed by the inner sides of cylindrical 'bodies .9 and 10 whichhave on their outside a circular cylindrical surface and on their inside a cylindrical surface, the axes of these two cylindrical surfaces being parallel to the axis of rotation of the pump.
  • the guide surfaces are formed in such a manner that they will produw an even displacement of the piston or pistonsfrom their outer position, the operative position, to
  • pockets or recesses 13, 14 In the wall of the pump body 3 are formed pockets or recesses 13, 14; at such points where the pistons pass from the inoperative position into operative position, and from operative position to inoperative position.
  • the casing has inlet andoutlet ports 11 and 12 and has a circular bore forming with a circular piston cylinder 2 a circular fluid passage 1, the rotary piston cylinder 2 within said casing is co-axially with the bore and the circular fluid passage uninterruptedly surrounds the piston cylinder 2 to 180 of its circumference.
  • the wall of the casing at both ends of said 180 fluid passage is provided with outwardly extending recesses 13 and 14 located substantially in a horizontal plane at the axial center line of the casing.
  • the discharge port channel at the outlet end of the 180 fluid passage in direct continuation thereof is tangentially arranged with the outlet end of the 180 fluid passage.
  • the barrier 4 is arranged between the suction-and delivery ports 11 and 12 and extends towards the piston cylinder 2.
  • the piston 5 is readily movable in the iston cylinder 2 and is directed outwardly fi'om the same to operative position by centrifugal force when i passing-through and crosses said 180 fluid passage.
  • the piston is limited in its outward radial movement by means 7 or the like, which prevents frictional wearing contact of saidpiston on the wall forming the 180 fluid passage and in cooperating with the parts 9, 10 is retracted within the periphery of said cylinder to inoperative position during the remaining 180 travel of said cylinder 2.
  • the other channel 11 is substantially tangential with the circular fluid passage 1 and with the recesses l3 and 14 and arranged on the juncture of the 180 fluid passagewith the inlet and outlet channels 11 and 12, the walls of the inlet and outlet channels forming continuations of the recesses.
  • a rotary pump the combination of a casing having inlet and outlet ports and having a circular bore, a rotary piston cylinder within said casing and co-axially with the bore forming therebetween a circular fluid passage uninterruptedly surrounding said cylinder 180 of its circumference, the wall of said casing at both ends of said 180 fluid passage being provided with outwardly extendingrecesses located substantially in a horizontal plane at the axial center line of the casing, a discharge port channel at the outlet end of the 180?
  • a rotary pump the combination of a casing having a circular bore, a rotary piston. cylinder within said bore and arranged co-axially' witlrthe same so as to form an essentially circular fluid passage of said recesses being provided at the juncture 1 of the 180 fluid passage with the inlet and outlet channels, and the walls of the inlet and outlet channels forming continuations of the recesses where the piston passes from the inoperative to the operative position and vice versa and saidrecesses being located substantially in a horizontal plane of the axial center line of the casing and spaced 180 apart, pistons radially movable in the cylinder and directed outwardly by the rotation of the same by centrifugal force across said 180 fluid passage portion, and means in said casing relatively stationary in respect to said piston limiting the outward radial movement of the piston to prevent frictional wearing contact of said piston with the bore of the 180 passage portion, said means coacting with the piston to retract the same within the periphery of said cylinder during the remaining 180 travel thereof

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Description

awms
Aprii 29, 1924;
J. c. k-iANSEPkELLEHAR/IMER ROTARY PUMP Filed April 12. 1923 ZZZZQ Patented Apr. 29, 1924.
ear oasis.
-J'ACOIB CHRISTIAN HANSEN-ELLEHAMMER, 01E LERUP, DENIZIARK.
scram rum.
. Application filed April 12, 1923. Serial No. 631,563.
7 '0 all whom it mag 'concewt:
Be it known that ,I, JACOB CHRISTIAN HANsEN-ELLEHAMMER, subject of the King ofDenmark, residing at Hellerup, Denmark, have invented certain new and useful Improvements in Rotary Pumps, of which the following is a specification.
The present invention relates to a rotary pump having an essentially circular fluid passage between the piston cylinder and the pump body which in the inoperative section has a projection separating the suction side from the delivery side. j I
The pumps of this kind heretofore employed show the disadvantage that they would quickly wear onthe guiding surfaces which are situated within the range of the fluid when the pump is employed for conveying impure water. This becomes partic- .ularly apparent when such water contains essential quantities of sandor grit which H within a very short time will completely wear out the guiding surfaces.
The present invention aims at obviating this disadvantage by disposing the entire controlling mechanism towards the center, outside of the range of the fluid so that the centrifugal forces on the fluid will hold sand particles and the like away from the guiding surfaces.
Furthermore, the enclosing walls of the pump body are made with pockets or recesses at such pointswhere the pistons pass from the inoperative section to the operative section. It is thereby obtained that the pistons are practically instantly relieved, as immediately on the pistons leaving the said pockets, the fluid can flow from the one side of the pistons to the other side.
It is clear from the above description that a pump like the one in question is partic:
ularly adapted to be used as a fire pump, the fact that the pump can deal with impure water being of the greatest importance in this respect.
In the accompanying drawing Fig. 1 is a vertical section through a con structional. form of the pump andatright angles to the spindle of the pump, and
Fig. 2'v is an axial section through the pump.
The pump has an essentially circular fluid passage 1 between the piston cylinder 2 and the pump body 3. The latter has on the inoperative section a projection 4 separating delivery side .12.
Within the piston cylinder 2 are disposed radially' slidable pistons 5 and 6 having tenons 7 and 8, respectively, outside of the fluid passage, and the axes of which are parallel to the axis, of rotation of the jump. These tenons are controlled by 'uide surfaces formed by the inner sides of cylindrical 'bodies .9 and 10 whichhave on their outside a circular cylindrical surface and on their inside a cylindrical surface, the axes of these two cylindrical surfaces being parallel to the axis of rotation of the pump. The guide surfaces are formed in such a manner that they will produw an even displacement of the piston or pistonsfrom their outer position, the operative position, to
In the wall of the pump body 3 are formed pockets or recesses 13, 14; at such points where the pistons pass from the inoperative position into operative position, and from operative position to inoperative position.
The operation of the ump is readily understood by regarding igure 1 where the fluidwhich, for example, at a given moment enters into the suction part 11 of the pump will by means 'of the piston 5 be carried downwards and round to the delivery side 12, F ions the foregoing it will be seen that the casing has inlet andoutlet ports 11 and 12 and has a circular bore forming with a circular piston cylinder 2 a circular fluid passage 1, the rotary piston cylinder 2 within said casing is co-axially with the bore and the circular fluid passage uninterruptedly surrounds the piston cylinder 2 to 180 of its circumference. The wall of the casing at both ends of said 180 fluid passage is provided with outwardly extending recesses 13 and 14 located substantially in a horizontal plane at the axial center line of the casing. The discharge port channel at the outlet end of the 180 fluid passage in direct continuation thereof is tangentially arranged with the outlet end of the 180 fluid passage. The barrier 4 .is arranged between the suction-and delivery ports 11 and 12 and extends towards the piston cylinder 2. The piston 5 is readily movable in the iston cylinder 2 and is directed outwardly fi'om the same to operative position by centrifugal force when i passing-through and crosses said 180 fluid passage. The piston is limited in its outward radial movement by means 7 or the like, which prevents frictional wearing contact of saidpiston on the wall forming the 180 fluid passage and in cooperating with the parts 9, 10 is retracted within the periphery of said cylinder to inoperative position during the remaining 180 travel of said cylinder 2.
The change from operative to inoperative,
and inoperative to operative position of the piston 5 takes place when the piston is in radial line with one of the recesses 13 or 14. Furthermore it will be seen that the other channel 11 is substantially tangential with the circular fluid passage 1 and with the recesses l3 and 14 and arranged on the juncture of the 180 fluid passagewith the inlet and outlet channels 11 and 12, the walls of the inlet and outlet channels forming continuations of the recesses.
This invention may be developed within the scope of the following claims without departing from the essential features of the same and it is desired that the specification and drawings be read as being merely illustrative and not in a limiting sense except as necessitated by the prior art.
.I claim: p I
1. In a rotary pump, the combination of a casing having inlet and outlet ports and having a circular bore, a rotary piston cylinder within said casing and co-axially with the bore forming therebetween a circular fluid passage uninterruptedly surrounding said cylinder 180 of its circumference, the wall of said casing at both ends of said 180 fluid passage being provided with outwardly extendingrecesses located substantially in a horizontal plane at the axial center line of the casing, a discharge port channel at the outlet end of the 180? fluid passage in direct continuation thereof tangentially with the oulet end of the 180 fluid passage, a barrier between the suction and delivery ports extendin to the cylinder, a piston radially movab e in the cylinder and directed outwardly from the same to operative position by centrifugal force when passing through and across said 180? fluid passage, means in said casing relatively stationary to said piston limiting the outward radial movement of the piston to prevent frictional wearing contact of said piston with the bore forming the 180 fluid passage, and retracting the piston within the periphery of said cylinder to inoperative position during the remaining 180 travel thereof, the change inoperative to inoperative, and inoperative to operative position of the piston taking place when the piston is in radial line-with one of said recesses.
2. In a rotary pump, the combination of a casing having a circular bore, a rotary piston. cylinder within said bore and arranged co-axially' witlrthe same so as to form an essentially circular fluid passage of said recesses being provided at the juncture 1 of the 180 fluid passage with the inlet and outlet channels, and the walls of the inlet and outlet channels forming continuations of the recesses where the piston passes from the inoperative to the operative position and vice versa and saidrecesses being located substantially in a horizontal plane of the axial center line of the casing and spaced 180 apart, pistons radially movable in the cylinder and directed outwardly by the rotation of the same by centrifugal force across said 180 fluid passage portion, and means in said casing relatively stationary in respect to said piston limiting the outward radial movement of the piston to prevent frictional wearing contact of said piston with the bore of the 180 passage portion, said means coacting with the piston to retract the same within the periphery of said cylinder during the remaining 180 travel thereof between the delivery and suction channels.
In testimony whereof I aflix my signature.
JACOB CHRISTIAN HANSEN-ELLEHAMMER.
US631563A 1923-04-12 1923-04-12 Rotary pump Expired - Lifetime US1492456A (en)

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US631563A US1492456A (en) 1923-04-12 1923-04-12 Rotary pump
US694581A US1535832A (en) 1923-04-12 1924-02-23 Coupling arrangement between a pump and an automobile

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3904327A (en) * 1971-11-10 1975-09-09 Rovac Corp Rotary compressor-expander having spring biased vanes
US3988083A (en) * 1971-08-28 1976-10-26 Daihatsu Kogyo Company Limited Non-contact vane pump
US4451219A (en) * 1980-12-15 1984-05-29 Kurherr Motoren A.G. Valveless bi-chamber rotary steam engine with turbine effect
US4917584A (en) * 1986-12-03 1990-04-17 Eagle Industry Co., Ltd. Vane pump with annular aetainer limiting outward radial vane movement
US5417555A (en) * 1994-02-15 1995-05-23 Kurt Manufacturing Company, Inc. Rotary vane machine having end seal plates
US5474043A (en) * 1994-06-17 1995-12-12 Mallen Research Ltd. Partnership Helicotoroidal vane rotary engine
US5524586A (en) * 1995-07-19 1996-06-11 Mallen Research Ltd. Partnership Method of reducing emissions in a sliding vane internal combustion engine
US5524587A (en) * 1995-03-03 1996-06-11 Mallen Research Ltd. Partnership Sliding vane engine
US5727517A (en) * 1996-01-30 1998-03-17 Mallen; Brian D. Equivalence-boosted sliding vane internal combustion engine
US6412280B1 (en) 2000-05-11 2002-07-02 Thermal Dynamics, Inc. Fluid motor
US6606857B1 (en) 2002-02-28 2003-08-19 Thermal Dynamics, Inc. Fluid actuated generator
US6616433B1 (en) 2001-12-06 2003-09-09 Thermal Dynamics, Inc. Fluid pump
US6688869B1 (en) 2002-09-11 2004-02-10 Thermal Dynamics, Inc. Extensible vane motor
US6784559B1 (en) 2002-02-28 2004-08-31 Thermal Dynamics, Inc. Fluid pressure regulator assembly with dual axis electrical generator
US6843436B1 (en) 2002-09-11 2005-01-18 Thermal Dynamics, Inc. Chopper pump
US6905322B1 (en) 2002-09-24 2005-06-14 Thermal Dynamics, Inc. Cam pump
US20100015001A1 (en) * 2008-07-18 2010-01-21 Panasonic Electric Works Co., Ltd. Vane pump
US20120275907A1 (en) * 2009-01-14 2012-11-01 Dirk Vinson Fluid energy machine
US20130266466A1 (en) * 2012-04-09 2013-10-10 Gene-Huang Yang Blade-Type Fluid Transmission Device

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3988083A (en) * 1971-08-28 1976-10-26 Daihatsu Kogyo Company Limited Non-contact vane pump
US3904327A (en) * 1971-11-10 1975-09-09 Rovac Corp Rotary compressor-expander having spring biased vanes
US4451219A (en) * 1980-12-15 1984-05-29 Kurherr Motoren A.G. Valveless bi-chamber rotary steam engine with turbine effect
US4917584A (en) * 1986-12-03 1990-04-17 Eagle Industry Co., Ltd. Vane pump with annular aetainer limiting outward radial vane movement
US5417555A (en) * 1994-02-15 1995-05-23 Kurt Manufacturing Company, Inc. Rotary vane machine having end seal plates
US5474043A (en) * 1994-06-17 1995-12-12 Mallen Research Ltd. Partnership Helicotoroidal vane rotary engine
US5524587A (en) * 1995-03-03 1996-06-11 Mallen Research Ltd. Partnership Sliding vane engine
US5524586A (en) * 1995-07-19 1996-06-11 Mallen Research Ltd. Partnership Method of reducing emissions in a sliding vane internal combustion engine
US5727517A (en) * 1996-01-30 1998-03-17 Mallen; Brian D. Equivalence-boosted sliding vane internal combustion engine
US6412280B1 (en) 2000-05-11 2002-07-02 Thermal Dynamics, Inc. Fluid motor
US6616433B1 (en) 2001-12-06 2003-09-09 Thermal Dynamics, Inc. Fluid pump
US6606857B1 (en) 2002-02-28 2003-08-19 Thermal Dynamics, Inc. Fluid actuated generator
US6784559B1 (en) 2002-02-28 2004-08-31 Thermal Dynamics, Inc. Fluid pressure regulator assembly with dual axis electrical generator
US6688869B1 (en) 2002-09-11 2004-02-10 Thermal Dynamics, Inc. Extensible vane motor
US6843436B1 (en) 2002-09-11 2005-01-18 Thermal Dynamics, Inc. Chopper pump
US6905322B1 (en) 2002-09-24 2005-06-14 Thermal Dynamics, Inc. Cam pump
US20100015001A1 (en) * 2008-07-18 2010-01-21 Panasonic Electric Works Co., Ltd. Vane pump
US8257071B2 (en) * 2008-07-18 2012-09-04 Panasonic Corporation Vane pump
US20120275907A1 (en) * 2009-01-14 2012-11-01 Dirk Vinson Fluid energy machine
US20130266466A1 (en) * 2012-04-09 2013-10-10 Gene-Huang Yang Blade-Type Fluid Transmission Device
US8985983B2 (en) * 2012-04-09 2015-03-24 Gene-Huang Yang Blade-type fluid transmission device
US20150139846A1 (en) * 2012-04-09 2015-05-21 Gene-Huang Yang Blade-type fluid transmission device
US9482226B2 (en) * 2012-04-09 2016-11-01 Gene-Huang Yang Blade-type fluid transmission device

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