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US1619429A - Blade pump - Google Patents

Blade pump Download PDF

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Publication number
US1619429A
US1619429A US148027A US14802726A US1619429A US 1619429 A US1619429 A US 1619429A US 148027 A US148027 A US 148027A US 14802726 A US14802726 A US 14802726A US 1619429 A US1619429 A US 1619429A
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United States
Prior art keywords
blade
cylinder
rotatable cylinder
pump
rotatable
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Expired - Lifetime
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US148027A
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Maillefer Arthur
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Individual
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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
    • F04C2/34—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
    • F04C2/3442—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 the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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

Definitions

  • the subject mat-ter of the present invention is a blade pump.
  • FIGS 1 to 6 in the accompanying drawings illustrate, by way of example, one torni of the pump according to the invention in these drawings.
  • Figure 1 is an end view of the pump, one of the side walls of the fixed cylinder being removed.
  • Figure 2 is a longitudinal section to a larger scale along the line rtf-B in Figure 1.
  • Figure 3 is a diagrammatic end view shows the relative position of the blade also that of the ball bearing 21.
  • Figure 4 is a diagrammatic end view shows the relative positions of the blade the inner bearing rings 20 and 18.
  • Figures 5 and 6 are diagrammatic end views of the cylinder and show the relative positions ot the blade and of the inner'rings 20 and 18 when the rotatable cylinder makes a quarter of a turn.
  • the fixed cylinder 1 comprises lateral walls, 2, 2 in which are formed circular apertures serving as lodgements for the ball bearings 3, 3' in the exterior of which rotate the shafts el, 1 disposed in axial alignment; the shafts l1, L1' each comprise towards their inner end a disc 5, 5' between and in axial alignment with which are mounted by means of' the screw-bolts 6, 6' the two shafts torming the rotatable cylinder 7.
  • the shafts L1, 4;' are placed eccentricaily relatively to the cavity ot' the cylinder 1 in such al way that the periphery ot' the rotatable cylinder 7 ].ienetrates slightly into the fixed cylinder 1, the effect of which is and and and and and to increase the zone of contact between the rotatable cylinder and make it possible for this region to be made iiuid tight.
  • The. eccentric position of the rotatable cylinder 7 in the interior ot the cylinder 1 is for the purpose of producing a suction and delivery space indica-ted by the reference numeral S.
  • the two halves of the rot-ary cylinder 7 are spaced apart in such a way as to leave a central transverse slot 9 between them in the interior of which slot is displaced transversely a blade 10 the ends of which are provided with grooves 11, 11' in each ot' which are located packing plates 12, 12', placed alternately the ones on the side ot the others.
  • the latter are cut out so as to iorin cavities 13, 13 in the interior of each of which is located a spring 14 the pressure of' which has the effect of pressing the plates 12, 12' against the lateral walls 2, 2 of the cylinder 1.
  • the plates 12, 12 are con stantly pressed against the circular wall of the cylinderV 1 by the effect alone of the centrifugal force.
  • the Huidtight joint is obtained between the ends of ghe blade and the centre walls of the cylin-
  • the blade 10 is guided in its movements by means of rollers 15, 15', 15, against which it presses, the latter being located in cavities formed in the rotatable cylinder 7 and are in addition held in position by means of the screw-bolts 6, 6' around which the said rollers rotate.
  • the blade 10 is provided on each side at two points equi-distant from its centre with pins 16, 16,16", 16"', which passed respectively through radial slots 17, 17', 17", 17"', formed in discs 5, 5.
  • the said pins are also attached to the inner bearing rings 1 8, 18 ot the ball bearings 19 and'19' respectively.
  • the outer bearing rings of the latter are secured in circular cavities formed in the ⁇ bearing rings 20, 20 and placed eccentrically relatively to the bearings 21, 21' in such a way that the ball bearings 19, 19 which are located therein have their centre on a point oi the circle 0', Figures 3 to 6.
  • Figure 1, 5- and 6 show the ends A*B of the blade 10 in their different positions when the said blade driven by the rotatable cylinder 7 makes a quarter of a turn, while at the same time the eccentric bearing rings 20, 20' make half a turn, that is to say move at a speed which is twice that of the rotatable cylinder 7 and thus give a reciprocating motion to theblade 10.
  • the eccentric bearing rings 20, 20 each comprise ak mass 22, 22 which masses are disposed upon the opposite side relatively to the center 0 ot' the centre oi the blade, these masses being destined to balance the force of inertia due to the reciprocating motion of the blade 10. ⁇
  • the fixed cylinder 1 is provided with a suction orifice 23 and adelivery orifice 24; the latter may comprise a delivery valve not shown in the drawings.
  • the operation ofthe pump is as follows:
  • the shaft having been put into rotation by any source of power, for example by means of a pulley or by direct engagement upon the. driving shaft by means of a mutiJ coupling, rotates the cylinder 7 and also the blade 10.
  • 'Thelatter is coupled by means of the pins 16, 16', 16, 16 to theeccentric ball bearings 19, 19..
  • the latter drive the bearings 21, 21', the outer bearing rings of which are supported upon the lateral walls 2, 2 of the fixed cylinder 1.
  • a blade pump characterized by the feature that it comprises a fixed cylinder provided with suction and delivery orifices in the interior of which moves a rotatable cylinder, the shaft of which is placed eccentrically Vin such a way that the periphery of the rotatable cylinder penetrates slightly into the fixed cylinder' with which it thus presents a large contact zone a suction and delivery space, the rotatable cylinder comprisinga central transverse.
  • a blade pump according to claim 1 characterized by therfeature that the inner ring of the eccentric ball bearing pressing upon the fixed cylinder is provided with a mass placed opposite relatively to the centre of this bearing, the centreV of the blade, the said .mass being destined to balance the inertia force due to the to-and-fromovement of the blade.
  • a pump of the character described comprising a casing, a pair of shafts eccentrically journaled within said casing, 1a disc carried by each shaft, a rotatably cylinder arranged within said casing, a blade slidably mounted within said cylinder, packing plates extending from the V,opposite ends of said blade andadapted to ⁇ contact the inner walls of said casing, oppositely positioned rollers journaled within said cylinder and adapted to ride upon the opposite sides ofsaid blade, laterally extending pins carried by said blade and projecting through radial slotsj formed within said discs, 'ball bearing rings connected to said casing and arrangedLconcentrically about said shafts, a weighted means eccentrically rotatable about said ball bearing rings and connected to said pins.

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

Description

March l 1927.
A. MAILLEF ER BLADE PUMP Filed Nov. 12, 1926 3 Sheets-Sheet 1 BLADE PUMP Filed Nov. l2, 1926 3 Sheets-Sheet 2 A. MAILLEFER BLADE PUMP March 1, 1927. 1,619,429
Filed Nov. l2,v 1926 3 Sheets-Sheet 5 fuffa/1to1' A nm/mzlwf,
ayf
Patented Mar. 1, 1927.
UNITED STATES ARTHUR MAILLEFER, or LAUSANNE, SWITZERLAND.
BLADE PUMP.
Application led November 12, 1926, Serial No. 148,027, and Yin Switzerland August 29, 1925.
The subject mat-ter of the present invention is a blade pump.
Figures 1 to 6 in the accompanying drawings illustrate, by way of example, one torni of the pump according to the invention in these drawings.
Figure 1 is an end view of the pump, one of the side walls of the fixed cylinder being removed.
Figure 2 is a longitudinal section to a larger scale along the line rtf-B in Figure 1.
Figure 3 is a diagrammatic end view shows the relative position of the blade also that of the ball bearing 21.
Figure 4 is a diagrammatic end view shows the relative positions of the blade the inner bearing rings 20 and 18.
Figures 5 and 6 are diagrammatic end views of the cylinder and show the relative positions ot the blade and of the inner'rings 20 and 18 when the rotatable cylinder makes a quarter of a turn.
The fixed cylinder 1 comprises lateral walls, 2, 2 in which are formed circular apertures serving as lodgements for the ball bearings 3, 3' in the exterior of which rotate the shafts el, 1 disposed in axial alignment; the shafts l1, L1' each comprise towards their inner end a disc 5, 5' between and in axial alignment with which are mounted by means of' the screw-bolts 6, 6' the two shafts torming the rotatable cylinder 7.
The shafts L1, 4;' are placed eccentricaily relatively to the cavity ot' the cylinder 1 in such al way that the periphery ot' the rotatable cylinder 7 ].ienetrates slightly into the fixed cylinder 1, the effect of which is and and and and to increase the zone of contact between the rotatable cylinder and make it possible for this region to be made iiuid tight.
The. eccentric position of the rotatable cylinder 7 in the interior ot the cylinder 1 is for the purpose of producing a suction and delivery space indica-ted by the reference numeral S.
The two halves of the rot-ary cylinder 7 are spaced apart in such a way as to leave a central transverse slot 9 between them in the interior of which slot is displaced transversely a blade 10 the ends of which are provided with grooves 11, 11' in each ot' which are located packing plates 12, 12', placed alternately the ones on the side ot the others. The latter are cut out so as to iorin cavities 13, 13 in the interior of each of which is located a spring 14 the pressure of' which has the effect of pressing the plates 12, 12' against the lateral walls 2, 2 of the cylinder 1. f
In addition the plates 12, 12 are con stantly pressed against the circular wall of the cylinderV 1 by the effect alone of the centrifugal force. In this way the Huidtight joint is obtained between the ends of ghe blade and the centre walls of the cylin- The blade 10 is guided in its movements by means of rollers 15, 15', 15, against which it presses, the latter being located in cavities formed in the rotatable cylinder 7 and are in addition held in position by means of the screw-bolts 6, 6' around which the said rollers rotate. '1
The blade 10 is provided on each side at two points equi-distant from its centre with pins 16, 16,16", 16"', which passed respectively through radial slots 17, 17', 17", 17"', formed in discs 5, 5. The said pins are also attached to the inner bearing rings 1 8, 18 ot the ball bearings 19 and'19' respectively. The outer bearing rings of the latter are secured in circular cavities formed in the` bearing rings 20, 20 and placed eccentrically relatively to the bearings 21, 21' in such a way that the ball bearings 19, 19 which are located therein have their centre on a point oi the circle 0', Figures 3 to 6.
Thus, on account ot the eccentricity oi? the ball bearings 21, 21 and 19, 19' and when t-he rotatable cylinder 7 a rectilinear to-andtro movement relatively to the cylinder 7, the effect ot which is to make each ot the ends of the blade 10 pass out ot the periphery of the rotatable cylinder 7, alternately and this takes pl ce while the rotatable cylinder 7 makes one revolution.
Figure 1, 5- and 6 show the ends A*B of the blade 10 in their different positions when the said blade driven by the rotatable cylinder 7 makes a quarter of a turn, while at the same time the eccentric bearing rings 20, 20' make half a turn, that is to say move at a speed which is twice that of the rotatable cylinder 7 and thus give a reciprocating motion to theblade 10.
The eccentric bearing rings 20, 20 each comprise ak mass 22, 22 which masses are disposed upon the opposite side relatively to the center 0 ot' the centre oi the blade, these masses being destined to balance the force of inertia due to the reciprocating motion of the blade 10.`
The fixed cylinder 1 is provided with a suction orifice 23 and adelivery orifice 24; the latter may comprise a delivery valve not shown in the drawings. v
The operation ofthe pump is as follows: The shaft having been put into rotation by any source of power, for example by means of a pulley or by direct engagement upon the. driving shaft by means of a mutiJ coupling, rotates the cylinder 7 and also the blade 10. 'Thelatter is coupled by means of the pins 16, 16', 16, 16 to theeccentric ball bearings 19, 19.. The latter drive the bearings 21, 21', the outer bearing rings of which are supported upon the lateral walls 2, 2 of the fixed cylinder 1.
As the speed of rotation of the bearing rings 20, 20 is twice the speed of the rotatable cylinder 7, it follows that while the latter makes one turn the blade 10 is given rectilinear to-an`dfro movement in such a way that in turn each of the said blades passes out of the periphery of the rotatablev cylinder 7 Thus, each time end of the blade 10 passes in front of the suction orifices 23 the iuid contained in the compression space 8 is de livered, from which spa-:1e the said fluid escapes through the'delivery orifice 24, which is provided with a deliveryvalve not shown in the drawings, and from which the fluid is led to the place where it is to be employed.
Having rnow particularly described and ascertained the nature of my said invention and in what manner the same is to be pe-rformed, I declare that what I claim iszx1. A blade pump, characterized by the feature that it comprises a fixed cylinder provided with suction and delivery orifices in the interior of which moves a rotatable cylinder, the shaft of which is placed eccentrically Vin such a way that the periphery of the rotatable cylinder penetrates slightly into the fixed cylinder' with which it thus presents a large contact zone a suction and delivery space, the rotatable cylinder comprisinga central transverse. slot, in which moves transversely a blade, the ends of which are provided with packing plates of the fixed cylinder` the blade being givenrectilinear tosand-fro movement relativeh7 to the rotatable cylinder by means of a ball bearing eccentric relatively to the shaft of the rotatable cylinder in the lateral wall of the `fixed cylinder, thecinner bearing ring of which ball bearing also comprises a circular cfvity placed eccentrically relatively to the i'irst ball bearing, in the interior of which cavity is located a second ball bearing the inner bearing ring of which is connected to the blade by pins, the wholef arrangement being so constructed that when the rotatable cylinder makes one turn the blade is driven alternately in `one direction and the other in such a way that its issuing end is constantly in contact with the inner wall of the fixed cylinder.
2. A blade pump according to claim 1, characterized by therfeature that the inner ring of the eccentric ball bearing pressing upon the fixed cylinder is provided with a mass placed opposite relatively to the centre of this bearing, the centreV of the blade, the said .mass being destined to balance the inertia force due to the to-and-fromovement of the blade.
3. A pump of the character described comprising a casing, a pair of shafts eccentrically journaled within said casing, 1a disc carried by each shaft, a rotatably cylinder arranged within said casing, a blade slidably mounted within said cylinder, packing plates extending from the V,opposite ends of said blade andadapted to` contact the inner walls of said casing, oppositely positioned rollers journaled within said cylinder and adapted to ride upon the opposite sides ofsaid blade, laterally extending pins carried by said blade and projecting through radial slotsj formed within said discs, 'ball bearing rings connected to said casing and arrangedLconcentrically about said shafts, a weighted means eccentrically rotatable about said ball bearing rings and connected to said pins.
Dated this 21 September, 1926.
In witness whereof I have hereunto set my hand.
ARTHUR MAILLEFER.
US148027A 1925-08-29 1926-11-12 Blade pump Expired - Lifetime US1619429A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2633292A (en) * 1948-02-21 1953-03-31 Voznica Karel Rotary compressor for gas or liquids with rotor eccentrically mounted in cylindrical housing
US3954358A (en) * 1974-08-16 1976-05-04 Michel Normandin Compressor
US3964447A (en) * 1974-08-12 1976-06-22 Michel Normandin Vane-type rotary internal combustion engine
US4025246A (en) * 1974-08-12 1977-05-24 Michel Normandin Rotary machine with counterweights for interfitted vanes
FR2330854A1 (en) * 1975-11-04 1977-06-03 Ettridge John Eccentric rotary piston engine with radial sealing strips - has ports controlled by lobes moving in recesses in the housing
US4086039A (en) * 1975-11-04 1978-04-25 Ettridge John P Orbital machine with cooperating lobe and recess guide means

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2633292A (en) * 1948-02-21 1953-03-31 Voznica Karel Rotary compressor for gas or liquids with rotor eccentrically mounted in cylindrical housing
US3964447A (en) * 1974-08-12 1976-06-22 Michel Normandin Vane-type rotary internal combustion engine
US4025246A (en) * 1974-08-12 1977-05-24 Michel Normandin Rotary machine with counterweights for interfitted vanes
US3954358A (en) * 1974-08-16 1976-05-04 Michel Normandin Compressor
FR2330854A1 (en) * 1975-11-04 1977-06-03 Ettridge John Eccentric rotary piston engine with radial sealing strips - has ports controlled by lobes moving in recesses in the housing
US4086039A (en) * 1975-11-04 1978-04-25 Ettridge John P Orbital machine with cooperating lobe and recess guide means

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