WO1989005405A1 - Pompe oleohydraulique - Google Patents

Pompe oleohydraulique Download PDF

Info

Publication number
WO1989005405A1
WO1989005405A1 PCT/KR1988/000023 KR8800023W WO8905405A1 WO 1989005405 A1 WO1989005405 A1 WO 1989005405A1 KR 8800023 W KR8800023 W KR 8800023W WO 8905405 A1 WO8905405 A1 WO 8905405A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuating
rotor
section
eccentric
eccentric rotational
Prior art date
Application number
PCT/KR1988/000023
Other languages
English (en)
Inventor
Young Jae Kim
Chul Kim
Original Assignee
Young Jae Kim
Chul Kim
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 KR1019870013759A external-priority patent/KR900008511B1/ko
Priority claimed from KR1019870015463A external-priority patent/KR920001693B1/ko
Application filed by Young Jae Kim, Chul Kim filed Critical Young Jae Kim
Publication of WO1989005405A1 publication Critical patent/WO1989005405A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics

Definitions

  • the present invention relates to an oilhydraulic pump, specifically relates to an oil pressure pump utilizing a centrifugal 5 force of eccentric rotational body which a rotor with own axle shaft being coupled to this eccentric rotational body is allowed to rotate so that high discharging pressure can be obtained by actuating a several numbers of fluid pumping means arranged radially around the casing, and said rotor is rendered to rotate more closely 1 Q around the primary center axle shaft in case where overload is loaded to an oil pressure circuit utilizing this discharging oil pressure so that overload is not loaded to a driving motor which drives an oil hydraulic pump of the invention.
  • Such oil hydraulic pump is, obtainable the required discharging oil pressure, however, there is the problems that in case where an overload is loaded to the oil pressure circuit of certain equipment utilizing such oil hydraulic pump, the oil pressure flows back and then it would be applied uniformly to each pistons and transferred to the eccentric wheel thereby it is allowed to stop the eccentric wheel so that overload is loaded to a driving motor coupled to the axle shaft of this eccentric wheel and accordingly excessive electric power is consumed.
  • the present invention is invented to solve and consider the problems as described herein above, which is constructed such that in the case where the oil pressure circuit is over ⁇ loaded, it causes the result to apply only the action which the driving motor which drives an oil hydraulic pump renders the rotor axle shaft rather simply to move with rotational movement of less load so that nevertheless it is the case of overload in oil pressure circuit, the consuming electric power of the driving motor can be decreased an thereby the whole efficiency can be enhanced.
  • FIG. 1 shows an exploded perspective view of the present 5 invention.
  • FIG. 2 shows a longitudinal cross sectional view of the present invention.
  • FIG. 3 is a cross sectional view taken along the A-A line in FIG. 2 showing a state that each components are in a position 10 with an operational condition.
  • FIG. 4 is a cross sectional view taken along the B-B line in FIG. 2 showing that the pump is in a operating position.
  • FIG. 5 is a cross sectional view showing a state which the pumping operation is not executed in the case when an overload -. c is loaded to the oil pressure circuit of certain equipment utilized with the oil pressure pump of the present invention.
  • FIG. 6 is a cross sectional view taken along the C-C line in FIG. 2.
  • FIG. 7 is a schematic explanatory diagram showing a movement 2Q condition of an eccentric rotational body of the pump according to the present invention.
  • FIG. 8 is a schematic explanatory diagram illustrating that the rotor for piston operation is carrying out the circular movement by a centrifugal force of the eccentric rotational body.
  • FIG. 9 and FIG. 10 are the cross sectional views showing another embodiment of the present invention which are similar to FIG. 4 and FIG. 5.
  • FIG. 1 is an exploded perspective view which shows almost all of the components of the first embodiment according to the present invention being exploded, which the present invention if It is generally divided, for example, is constructed with the input section 10 which a driving power is in putted from an electrical driving motor (not shown) , first actuating section 11, second actuating section 12 which has larger capacity as much as almost about double than the capacity of said first actuating section 11, and third actuating section which is the same structure with this first actuating section 11 and is for the balance with the first actuating section 11.
  • An input section 10 together with support section 14 form the both side support section of an oil pressure pump of the present invention, which are fomed of the supporting plate 17 having several numbers of coupling lug 16 with coupling hole 15, a bushing 18 is extended to the exterior, through which bushing 18 is inserted an input axle shaft 19, which a coupling 20 to be coupled with a driving motor at an external end is coupled, at an internal end of which input axle shaft 19 there is fixed the transmission plate 21, on which plate 21 there is protruded a coupling stub 22 at a position to form an eccentric coupling point relative to the input axle shaft 19.
  • the first actuating section it is shown a part in FIG. 1 and the cross sectional view is shown in FLGS. 2 to 4, and the third actuating section 13 which is symmetrical with this first actuating section 11 will be explained together with said first actuating section 11.
  • the first actuating section 11 is formed of a casing 24 having an actuating chamber 23 of circular cross section, to which casing 24 is formed a fluid pumping means. That is to say, a several numbers of cylinder 25 are arranged to the casing radially, to these cylinder 25 are each inserted the piston 26. To both side of casing 24 are fixed the guide side plates 28a, 28b which have a circular opening 27 being smaller in diameter than that of actuating chamber 23. Within an actuating chamber 23 is arranged a rotor 29.
  • This rotor 29 is fixed rotatably on a rotor shaft 32 together with a large diameter boss 30 at a central position and the small diameter bosses 31a, 31b at both side concentrically with the axis of said rotor shaft 29, to the large diameter boss 30 is fixed a rotor wheel 33 which operates within a actuating chamber 23.
  • This rotor wheel 33 corresponds to in practical an outer rase of ball bearing 34.
  • the quide bearings 36a, 36b of ball bearing type which the radially outer case 35 fixed at the small diameter bosses 31a, 31b is carrying out the cicular movement by contacting to the interior circumferential surface within the circular opening 27 of the guiding side plates 28a, 28b.
  • the diameter of rotor wheel 33 is smallar than the inside diameter of actuating chamber 23 having circular cross section and similarly the outside diameter of the guid bearings 36a, 36b are smaller than the inside diameter of circular opening 27.
  • a rotor axle shaft 32 of rotor 29 is extended axially to both side of the casing 24, to which rotor axle shaft there is provided fixedly the eccentric rotational bodies 40a, 40b which are formed of semicircular weight portion 37 and extended portion 39 having a rectangular guide openings 40a, 40b.
  • the valve blocks 43 which the suction valve 41 and the discharge valve 42 are ccmmunicated with toward the cylinder 25 opening, and as will be explained more in detail hereinafter, above the valve blocks 43 there is provided the oil flow channel 46 which is formed with a suction tube portion 44 communicated with the suction valve 41 and a discharge tube portion 45 corrmunicated with the discharge valve 42.
  • the third actuating section 13 is same to the structure of the first actuating section 11 as mentioned hereinabove, they are represented by the reference code which a prime code(') is added with respect to the same component, and the description for that structure will be deleled.
  • the second actuating section 12 as mentioned previously in the begining of description with regard to structure, it is a 5 form which has about double capacity of the capacity of the first actuating section 11, the form of eccentric rotational body 47a, 47b which correspond to the eccentric rotational body 40a, 40b and 40a' , 40b' of the first actuating section 11 and the third actuating section 13 is formed of only the weight portion 48 of semicireular -
  • This eccentric rotational body 47 of the second actuating section 12 is larger as much as almost double 5 in weight than the eccentric lotational boy of the first and the third section.
  • the supporting section 14 is disposed symmetrically with the input section 10, except that the coupling 20 of input section 10 is not shown, it has same structure with this input 0 section, therefore they are denoted with same numeral code by adding only a prime code ( ' ) for the same component.
  • the input section 10, first actuating section 11, second actuating section 12, third actuating section 13 and supporting section 14 which are the essential constitution section of the 5 present invention as described hereinabove are coupled as follows. That is to say, coupling stub 22 fixed at a tranmission plate 21 of the input section 10 is inserted to a rectangular guid opening 38 formed at an extension portion 39 of one side eccentric rotational body 40a of the first actuating section 11 through a slider 50, other side eccentric rotational body 40b of the first actuating section 11 is Inserted with a coupling stub 49 fixed at one side eccentric rotational body 47a of the second actuating section 12 through a slider 51 mounted slidably in the rectangular guide opening 38 of said extension portion 39 so that they are coupled, and the other side eccentric rotational body 40b of the first actuating section 11 and the one side eccentric rotational body 47a of the second actuating section 12 are coupled with opposite direction of 180 angle.
  • a coupling stub 49 of the other side eccentric rotational body 47b of the second actuating section 12 is coupled to the one side eccentric rotational body 40a' of the third actuating section 13 through the other slider 52, and 10 the other side eccentric rotational body 40b' of the third actuating section 13 there is coupled the coupling stub 22' fixed on the transmission plate (crank plate) 21' of the supporting section 14 through a slider 53.
  • aligned input section 10 and supporting section 14 are bolted with a several numbers of tightening bolt 54 passing through the coupling holes 15, 15 r of the coupling lugs 16, 16' formed at the periphery of the supporting plates 17, 17' , respectively; between eaches of the input section 10, first actuating section 11, second actuating section 12, third actuating section 13 and supporting section 14 there are respectively interposed the housings 55a, 55b, 55c, 55d; and the supporting legs 56a, 56b are respectively fixed to the supporting section 14 and input section 10.
  • an oil flow channel 46 which is coupled to each valve blocks 43, 43', 43", is coupled to each valves in common with both suction tube portion 44 and discharge tube portion 45 so that they form the suction pipe inlet and discharge pipe outlet (not shown) of the oil pressure pump according to the present invention.
  • An oil pressure pump carries out the operation as follows.
  • each eccentric rotational bodies 40a, 40b, 47a, 47b, 40a', 40b 1 of each actuating section 11, 12, 13 are rotated around the axis of primary input shaft 19
  • the rotors 29, 29", 29' are rotated with contacting to the internal circumferential surface of each actuating chamber 23, 23", 23' which define the moving extent of them, and the pressure which would be applied to the Internal circumferential surface becomes raised largely by the centrifugal force being actuated.
  • each pairs of eccentric rotational bodies 40a, 40b, 40a', 40b' and 47a, 47b of the first, second and third actuating sections 11, 12, 13 which produce the centrifugal force and render the rotors 29, 29", 29' to do the rotational movement, for the balance of eccentric amount
  • the eccentric rotational bodies 40a, 40b, 40a' 40b' of the first and third actuating section 11, 13 are eccentric with same weight and same direction
  • the weight of a pair of the eccentric rotational bodies 47a, 47b of the second actuating section 12 are equal to the weight of each pairs of eccentric rotational bodies 40a, 40b, 40a', 40b' of the first and third actuating section 11, 13 being added all together, but the eccentric direction of them are in opposite each other.
  • the present invention is capable of obtaining the high discharge pressure by actuating an oil pressure pump such that the centrifugal force of the eccntric rotational body of weight is utilized and the rotor coupled with rotor axle shaft to this eccentric rotational body is rendered to carry out the rotational movement so that a plurality of the pistons arranged radially are allowed to operate.
  • FIG. 7 shows the rotation state of one eccentric rotational body 40a and that a rotor coupled to this eccentric rotational body Is executing the rotational movement within an actuating chamber 23
  • FIG. 8 is a schematic explanatory diagram which is shown the eccentric rotational body 40a by a mass (M) in order to explain more simply than the rotor 29 is executing the rotational movement within an actuating chamber 23.
  • FIG. 9 and FIG. 10 show the another embodiment of the present invention, which to the rotor 128 arranged within an actuating chamber 123 there is fixed the rotor wheel 132 with metal bearing manner with respect to a large diameter boss 131 on the rotor axle shaft 129 in order to seal the actuating chamber 123.
  • the eccentric rotational body At both end side portion of the rotor axle shaft 129 of the rotor 128 there is fixed the eccentric rotational body as mentioned previously in foresaid first embodiment, and also they are structured with multiple stages as first embodiment.
  • the casing 124 which forms an actuating chamber 123, there are formed a several numbers of slot 125 radially, to these slots 125 there are inserted respectively the platelike vanes 126.
  • vanes 126 are arranged resiliently to inward of the actuating chamber 123 by the springs 127 inserted within the slots 125 which are the outer side of the vane 126.
  • rotor 128 Within an actuating chamber 123 there is arranged the rotor 128.
  • small diameter bosses 130 (only one is shown) at both sides on an rotor axle shaft 129 and concentrically on the central position, a large diameter boss 131 is formed, to the external circumference of said large diameter boss 131 is inserted outwardly with metal bearing coupling menner.
  • This rotor wheel 132 in its width equals to the width of the large diameter boss 131 as well as the width of the vane 126. And, the width of the vane 126 equals to the width of an actuating chamber 123.
  • vanes 126 and a rotor 128 within an actuating chamber 123 partition the actuating chamber 123 into a several numbers of variable unit chambers 135. If it is assumed that a rotor 128 rotates clockwise with contacting closely to the ends of adjacent two vanes 126 which forms a unit variable chamber 135, a fluid suction port 136a is formed at backward of the rotational direction and a fluid discharge port 136b is formd at frontward of the rotational direction.
  • a fluid suction port 136a of one side variable unit chamber 135 and a fluid discharge port 136b of other side variable unit chamber 135 which are located on both side of one vane 136 are combined as a pair and arranged, at which location there is provided the valve block 143 which is communicated with each of suction valve 141 and discharge valve 142, on the valve block 143 there is provided an oil flow channel 146 which a suction tube portion 144 communicated with the suction valve 141 and a discharge tube portion 145 communicated with the discharge valve 142, are formed.
  • variable unit chamber 135 By these volume variation of variable unit chamber 135, the low pressure oil sucked into the corresponding variable unit chamber 135 through the suction valve 141 and the fluid suction port 136a is supplied with high pressure high pressure circuit through the fluid discharg port 136b and the discharge valve 142.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)

Abstract

La pompe oléohydraulique décrite utilise la force centrifuge d'un petit nombre de corps en rotation excentrique (40a, 40b, 47a, 47b, 40a', 40b'), disposés à l'opposé les uns des autres pour s'équilibrer, et le rotor (29, 29'', 29') couplé auxdits corps par l'intermédiaire de l'arbre de rotor (32, 32'', 32') fixé au rotor adopte le mouvement de rotation excentrique autour de l'axe central primaire, de sorte qu'une pression de décharge élevée peut être obtenue par actionnement de plusieurs pompes à fluide (25, 26, 41, 42, 43) disposées radialement au niveau du carter (24, 24'', 24'). Ainsi, au cas où une surcharge est appliquée sur le circuit d'huile sous pression par ladite pression de décharge élevée, le rotor avec son arbre se déplace vers l'axe central primaire adjacent et adopte le mouvement de rotation excentrique autour dudit axe, de sorte que la surcharge causée par la pression élevée renvoyée par le circuit d'huile sous pression externe, ne s'applique pas sur un moteur d'entraînement, ce qui permet une économie d'électricité avec ou sans surcharge et un fonctionnement de la pompe oléohydraulique de la présente invention sans consommation excessive d'énergie.
PCT/KR1988/000023 1987-12-03 1988-12-01 Pompe oleohydraulique WO1989005405A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR1987/13759 1987-12-03
KR1019870013759A KR900008511B1 (ko) 1987-12-03 1987-12-03 유압펌프
KR1987/15463 1987-12-30
KR1019870015463A KR920001693B1 (ko) 1987-12-30 1987-12-30 유압펌프

Publications (1)

Publication Number Publication Date
WO1989005405A1 true WO1989005405A1 (fr) 1989-06-15

Family

ID=26627777

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR1988/000023 WO1989005405A1 (fr) 1987-12-03 1988-12-01 Pompe oleohydraulique

Country Status (2)

Country Link
AU (1) AU2808489A (fr)
WO (1) WO1989005405A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007095824A1 (fr) * 2006-02-22 2007-08-30 Guangzhou Panyu Huanan Motors Group Co., Ltd. Pompe à huile

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE701334C (de) * 1938-10-30 1941-01-14 Paul Kretzschmar Kolben- oder Membran-Pumpensatz
US3003428A (en) * 1958-06-13 1961-10-10 Gen Motors Corp Pump
DE2616192A1 (de) * 1975-04-14 1976-10-28 Gerard Leduc Exzenter-hydraulikpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE701334C (de) * 1938-10-30 1941-01-14 Paul Kretzschmar Kolben- oder Membran-Pumpensatz
US3003428A (en) * 1958-06-13 1961-10-10 Gen Motors Corp Pump
DE2616192A1 (de) * 1975-04-14 1976-10-28 Gerard Leduc Exzenter-hydraulikpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007095824A1 (fr) * 2006-02-22 2007-08-30 Guangzhou Panyu Huanan Motors Group Co., Ltd. Pompe à huile

Also Published As

Publication number Publication date
AU2808489A (en) 1989-07-05

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