WO2012002141A1 - Pompe à mouvement alternatif - Google Patents

Pompe à mouvement alternatif Download PDF

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Publication number
WO2012002141A1
WO2012002141A1 PCT/JP2011/063549 JP2011063549W WO2012002141A1 WO 2012002141 A1 WO2012002141 A1 WO 2012002141A1 JP 2011063549 W JP2011063549 W JP 2011063549W WO 2012002141 A1 WO2012002141 A1 WO 2012002141A1
Authority
WO
WIPO (PCT)
Prior art keywords
motor
spherical
pump
reciprocating member
reciprocating
Prior art date
Application number
PCT/JP2011/063549
Other languages
English (en)
Japanese (ja)
Inventor
敬一郎 大野
幹雄 水越
Original Assignee
株式会社イワキ
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
Application filed by 株式会社イワキ filed Critical 株式会社イワキ
Publication of WO2012002141A1 publication Critical patent/WO2012002141A1/fr

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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
    • 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
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the present invention relates to a reciprocating pump in which a reciprocating coaxial of a reciprocating member and a drive shaft of a motor are coupled via a drive joint at a predetermined angle.
  • Patent Document 1 discloses that the liquid is transferred by reciprocating the suction port and the discharge port alternately to the cylinder chamber by reciprocating the nozzle while rotating it.
  • the machine difference variation such as misalignment is caused.
  • a difference in flow rate occurs between the finished products.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2001-248543
  • An object of the present invention is to provide a reciprocating pump capable of supplying a stable flow rate by suppressing a machine difference variation of a pump generated in a manufacturing process.
  • a reciprocating pump comprises a cylinder having a suction port and a discharge port, a reciprocating member in which the tip end portion is reciprocally and rotatably accommodated in the cylinder, and a motor for rotationally driving the reciprocating member.
  • the spherical bearing portion has a spherical inner ring coupled to the base end of the reciprocating member and a spherical outer ring for holding the spherical inner ring, and the fixing portion and the spherical outer ring are integrally formed. It is characterized.
  • FIG. 1 is a side view with a part cut away of a plunger pump according to a first embodiment of the present invention. It is a top view of the same plunger pump. It is a sectional side view of the drive coupling in the same plunger pump. It is a top view of the drive joint. It is a front view of the same drive coupling. It is a figure for demonstrating the operation
  • FIG. 1 is a side view showing a portion of a plunger pump according to a first embodiment of the present invention cut away
  • FIG. 2 is a plan view.
  • the plunger pump includes a pump frame 1, a motor 2 mounted on the back of the pump frame 1, and a pump head 3 mounted on the front of the pump frame 1. .
  • a bipolar stepping motor which is a high efficiency motor is adopted as the motor 2 and this is driven in the micro step mode.
  • the bipolar stepping motor in the present embodiment has a rotational speed detecting function such as a photomicro sensor or a Hall IC sensor.
  • the motor bracket 21 of the motor 2 is integrally formed with the pump frame 1. Therefore, the pump frame 1 is integrally assembled to the motor 2 when the motor 2 is assembled.
  • the pump frame 1 is integrally formed in a bowl shape by, for example, aluminum die-casting, and the back plate 11 is perpendicular to the bottom plate 12 and the front plate 13 forms a predetermined angle ⁇ with the back plate 11 It is formed.
  • a mounting flange portion 14 extending outward is formed on the back plate 11 of the pump frame 1, and a through hole is provided at a central position of the back plate 11, thereby forming the motor bracket 21. Further, a through hole is formed at the central position of the front plate 13 of the pump frame 1 and female screws are formed on the left and right thereof.
  • the drive shaft 22 of the motor 2 projects from the back plate 11 of the pump frame 1 to the inside of the pump frame 1 via the motor bracket 21.
  • the drive joint 5 is attached to the end of the drive shaft 22 of the motor 2 and is fixed by an external thread 511.
  • the drive joint 5 will be described in detail later, but a disk-like fixed portion 51 mounted on the drive shaft 22 of the motor 2 and a portion extending from the peripheral portion of the fixed portion 51 in the distal direction of the drive shaft 22 And a spherical bearing 52 formed on
  • the pump head 3 is fixed to the front plate 13 of the pump frame 1.
  • the pump head 3 has a cylindrical pump head main body 31 whose tip is closed.
  • a cylindrical discharge port 33 and a suction port 34 are formed opposite to each other on the side surface on the tip end side of the pump head main body 31.
  • a pair of fixing plates 36 is provided on the side surface on the proximal end side of the pump head body 31.
  • the pump head 3 has the fixed plate 36 and the front plate 13 of the pump frame 1 in a state where the open end side of the pump head body 31 is inserted to the inside through the through hole provided in the front plate 13 of the pump frame 1. It is fixed to the pump frame 1 by fixing it by means of an external screw 35.
  • a cylindrical cylinder 32 made of ceramic such as alumina is accommodated inside the pump head 3. Inside the cylinder 32, a tip end portion of a plunger 4 which is a reciprocating member made of the same ceramic as the cylinder 32 is accommodated so as to freely reciprocate and rotate. A discharge port 37 and a suction port 38 communicating with the discharge port 33 and the suction port 34 of the pump head 3 are formed in a tip side surface of the cylinder 32.
  • a cut surface 42 (FIG. 6) is formed at the tip of the plunger 4. Further, a pin 41 extending in a direction perpendicular to the central axis of the plunger 4 is fixed to the base end of the plunger 4, and the tip of the pin 41 is connected to the spherical bearing 52.
  • the front plate 13 and the back plate 11 of the pump frame 1 form a predetermined angle ⁇ , and as a result, the pump head 3 fixed to the front of the pump frame 1 and the motor fixed to the rear
  • the center axis of 2 is fixed at a predetermined angle ⁇ .
  • the motor bracket 21 and the pump frame 1 are integrally formed, and the pump frame 1 and the pump head 3 are fixed by the male screw 35. Since the pump frame 1 is box-shaped, the distance between the motor 2 and the cylinder 32 and the angle ⁇ can be firmly fixed. In addition, in such a configuration, since there are few components, variation in machine difference in the connection portion and the movable portion hardly occurs.
  • the motor bracket 21 and the pump frame 1 are integrally formed in the present embodiment, the motor bracket 21 may be partially included in the motor case, or may be housed inside the motor case.
  • the format may be In the present embodiment, the outer diameter of the plunger 4 is substantially equal to and uniform with the inner diameter of the cylinder 32, but only the tip end portion is equal to the inner diameter of the cylinder 32; It is also possible to use parts having the same radius. Moreover, in this embodiment, although it fixes by several places screwing, you may fix by the method different from this. Furthermore, the pump head 3 may be accommodated inside the pump frame 1.
  • FIG. 3 shows a side sectional view of the drive joint 5
  • FIG. 4 shows a plan view
  • FIG. 5 shows a front view.
  • the drive joint 5 includes a disk-shaped fixed portion 51 and a spherical bearing portion 52.
  • the fixing portion 51 is formed with an insertion hole 513 at its center into which the drive shaft 22 of the motor 2 is inserted. Further, a female screw 512 is formed in a direction perpendicular to the insertion hole 513 from the side surface of the fixing portion 51 to the insertion hole 513.
  • the drive shaft 22 of the motor 2 is fixed to the fixing portion 51 by screwing the male screw 511 to the female screw 512.
  • the spherical bearing portion 52 is configured to include a spherical inner ring 521 to which the pin 41 of the plunger 4 is coupled, and a spherical outer ring 523 for holding the spherical inner ring 521.
  • the outer surface of the spherical inner ring 521 is spherical, and an insertion hole 525 for press-fitting the pin 41 at the center is formed.
  • the spherical outer ring 523 is formed by integral molding of resin together with the fixing portion 51 so as to extend from the outer edge portion of the fixing portion 51 in the direction of the drive shaft 22 of the motor 2.
  • the surface on the drive shaft 22 side of the spherical outer ring 523 is formed by a curved surface coaxial with the drive shaft 22 and separated from the drive shaft 22 by a predetermined distance in the radial direction. Thereby, mechanical interference with the proximal end member of the plunger 4 is prevented.
  • An annular groove 524 is formed on the curved surface of the spherical outer ring 523 on the drive shaft 22 side, and a retainer portion 526 for holding the spherical inner ring 521 is formed inside thereof.
  • the retainer portion 526 is an annular body rising from the bottom of the annular groove 524 and has three notches 522 at regular intervals in the circumferential direction, and the inner peripheral surface forms a spherical receiving surface for slidably holding the spherical inner ring 521 doing.
  • the spherical inner ring 521 is held by the spherical receiving surface of the retainer portion 526 such that the insertion hole 525 faces in a direction substantially orthogonal to the drive shaft 22 of the motor 2 at a position deviated from the drive shaft 22 of the motor 2 .
  • the spherical bearing portion 52 is fitted to the drive joint 5 as a separate part from the drive joint 5.
  • the spherical outer ring 523 of the spherical bearing portion 52 and the fixing portion 51 of the drive joint 5 are integrally formed of resin, the center position of the spherical inner ring 521 with respect to the drive shaft 22 of the motor 2 It is possible to determine accurately and to achieve no adjustment. For this reason, it is possible to suppress the machine difference variation that has conventionally occurred between the spherical inner ring 521 and the fixed portion 51 of the drive joint 5.
  • the notches 522 and the annular groove 524 improve the flexibility of the retainer portion 526 to facilitate the work of press-fitting and mounting the spherical inner ring 521 on the spherical outer ring 523 and prevent damage to the drive joint 5. It is provided to
  • FIG. 6 shows the principle of rotational reciprocation of the plunger 4.
  • the swing angle ⁇ is defined by the shape of the pump frame 1, and the stroke length of the plunger 4 is determined by the angle ⁇ .
  • the base end portion of the plunger 4 is held by the spherical inner ring 521 on the inner peripheral portion of the drive joint 5 via the pin 41, and the spherical bearing portion 52 is a circle around the rotational axis of the drive joint 5 by the rotational drive of the drive joint 5. Because it moves and its circular orbit is inclined with respect to the central axis of the plunger 4, the plunger 4 reciprocates in the cylinder 32 while rotating.
  • FIG. 6 (a) shows a state in which the plunger 4 is pulled out the most
  • Fig. 6 (b) shows a state in which the plunger 4 is pushed the most.
  • the rotation and reciprocation of the plunger 4 causes the liquid to be transferred by the method described below.
  • FIG. 7 shows the operation principle of the plunger pump in the present embodiment.
  • FIG. 7A With the rotation of the plunger 4, the leading side of the cut surface 42 at the tip of the plunger 4 comes in contact with the suction port 34 and the suction port 34 communicates with the cylinder chamber.
  • FIG. 6B When the plunger 4 is pulled out from the state while rotating in the direction shown by the arrow in the figure, as shown in FIG. 6B, the transfer liquid is sucked from the suction port 34 into the cylinder chamber.
  • FIG. 6C when the rear side of the cut surface 42 at the tip of the plunger 4 is separated from the suction port 34, the suction port is closed by the plunger 4 and the suction process 12 is completed. Subsequently, as shown in FIG.
  • the positional relationship between the drive shaft 22 of the motor 2 and the cylinder 32 is fixed.
  • the drive joint 5 can also stably hold the plunger 4 by the inset structure of the spherical inner ring 521.
  • the plunger 4 and the cylinder 32 are made of ceramic, and if the combination of the two is considered, the machine difference generated in the manufacturing process is small. From the above reasons, in such a structure, the stroke length is less susceptible to machine differences, and it becomes possible to supply a stable flow rate.
  • the manufacturing cost can be reduced and the yield can be improved.
  • the structure is simpler than that of the prior art, it is suitable for miniaturization.
  • the pump frame 1 is die-cast molded and the spherical bearing portion 52 is integrally formed with the fixing portion 51, the pump frame 1 is formed of sheet metal, and the spherical bearing portion is formed.
  • the angular error between the drive shaft 22 of the motor 2 and the plunger 4 of the plunger pump in which the fixed portion 51 is separately formed from the fixed portion 51 is ⁇ 0.2 °, ⁇ 0.1 ° It was possible to improve. As a result, it was possible to improve the discharge amount error of one shot of the pump from 2% to 2% to 3% of the conventional one.
  • FIG. 8 shows a drive coupling 5 of a plunger pump according to a second embodiment of the present invention.
  • the basic configuration is the same as that of the first embodiment, but the shape of the side wall portion of the spherical bearing 52 and the mechanism of the fixing portion 51 are different from those of the first embodiment.
  • the side wall of the spherical bearing portion 52 is formed in a partially chipped shape.
  • the plunger 4 does not easily interfere with the side wall portion of the spherical bearing portion 52, so that the movable range of the plunger 4 is expanded, and the swing angle ⁇ can be set larger. This makes it possible to increase the discharge amount.
  • pin holes 514 are provided in the fixing portion 51 instead of the internal thread 512.
  • the drive joint 5 and the drive shaft 22 of the motor 2 are fixed not by the male screw 51 but by press-fitting of parallel pins or spring pins (not shown).
  • the drive shaft 22 and the fixing portion 51 are penetrated by the parallel pin, the drive shaft 22 and the drive joint 5 can be fixed more firmly.
  • FIG. 9 is a perspective view of the pump head 3 in the present embodiment
  • FIG. 10 (a) is a plan view partially cut away
  • FIG. 10 (b) is a side sectional view.
  • the left half of FIG. 10 shows a cross section taken along the line AA of FIG. 9 and viewed in the arrow direction.
  • the basic configuration is the same as that of the first embodiment, but the shapes of the tip of the cylinder 32, the corresponding bottom surface in the pump head 3, and the opening of the pump head 3 are different.
  • a D-shaped cut is applied to the outer periphery of the tip end portion of the cylinder 32.
  • the ridge is provided in the bottom part inner periphery in the pump head 3 corresponding to this. This makes it possible to prevent the movement of the cylinder 32 relative to the pump head 3 in the rotational direction.
  • a plurality of notches 36 in the circumferential direction and a locking piece 37 to which elasticity is imparted by the notches 36 are provided.
  • the cylinder 32 is fixed by the locking piece 37 to prevent the cylinder 32 from moving in the axial direction.
  • the movement to the rotation direction and axial direction of the cylinder 32 with respect to the pump head 3 is prevented, and stable pump operation
  • the cylinder 32 is inserted into the pump head 3 in the manufacturing process, it is possible to easily determine the position and the angle of the cylinder, so it is possible to improve the yield.

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

Abstract

Pompe à mouvement alternatif susceptible d'être fabriquée sans engendrer de variations entre les produits dans le processus de fabrication et capable d'assurer un débit stable. La pompe à mouvement alternatif selon l'invention comporte : un cylindre doté d'une ouverture d'aspiration et d'une ouverture de refoulement; un organe à mouvement alternatif dont l'extrémité avant est contenue à l'intérieur du cylindre de telle manière que l'extrémité avant puisse aller et venir tout en pivotant; un moteur servant à entraîner en rotation l'organe à mouvement alternatif; un bâti de pompe servant à fixer le moteur et le cylindre de telle manière que l'arbre tournant de l'organe à mouvement alternatif et l'arbre d'entraînement du moteur forment un angle prédéterminé; et un accouplement d'entraînement servant à relier l'arbre d'entraînement du moteur à l'extrémité d'embase de l'organe à mouvement alternatif. L'accouplement d'entraînement comprend une section de fixation montée sur l'arbre d'entraînement du moteur et comprend également une section de palier sphérique reliée à l'extrémité d'embase de l'organe à mouvement alternatif. La section de palier sphérique comprend une bague intérieure sphérique qui est jointe à l'extrémité d'embase de l'organe à mouvement alternatif et comprend également une bague extérieure sphérique destinée à maintenir la bague intérieure sphérique. La section de fixation et la bague extérieure sphérique sont formées d'un seul tenant.
PCT/JP2011/063549 2010-06-28 2011-06-14 Pompe à mouvement alternatif WO2012002141A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-146820 2010-06-28
JP2010146820 2010-06-28

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WO2012002141A1 true WO2012002141A1 (fr) 2012-01-05

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PCT/JP2011/063549 WO2012002141A1 (fr) 2010-06-28 2011-06-14 Pompe à mouvement alternatif

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107023450A (zh) * 2016-02-01 2017-08-08 株式会社易威奇 柱塞泵
JP2021076028A (ja) * 2019-11-05 2021-05-20 シナノケンシ株式会社 プランジャポンプ

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168807A (en) * 1990-10-30 1992-12-08 Como Technologies, Inc. Printing apparatus and method
JP2003112408A (ja) * 2001-10-05 2003-04-15 Tokyo Kikai Seisakusho Ltd 印刷機用ポンプ
WO2009015915A1 (fr) * 2007-08-02 2009-02-05 Fluid Management Operations Llc Pompe de mélange à double chambre

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168807A (en) * 1990-10-30 1992-12-08 Como Technologies, Inc. Printing apparatus and method
JP2003112408A (ja) * 2001-10-05 2003-04-15 Tokyo Kikai Seisakusho Ltd 印刷機用ポンプ
WO2009015915A1 (fr) * 2007-08-02 2009-02-05 Fluid Management Operations Llc Pompe de mélange à double chambre

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107023450A (zh) * 2016-02-01 2017-08-08 株式会社易威奇 柱塞泵
US10711779B2 (en) * 2016-02-01 2020-07-14 Iwaki Co., Ltd. Plunger pump
JP2021076028A (ja) * 2019-11-05 2021-05-20 シナノケンシ株式会社 プランジャポンプ

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