WO2014156842A1 - Pompe volumétrique - Google Patents

Pompe volumétrique Download PDF

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Publication number
WO2014156842A1
WO2014156842A1 PCT/JP2014/057354 JP2014057354W WO2014156842A1 WO 2014156842 A1 WO2014156842 A1 WO 2014156842A1 JP 2014057354 W JP2014057354 W JP 2014057354W WO 2014156842 A1 WO2014156842 A1 WO 2014156842A1
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WO
WIPO (PCT)
Prior art keywords
pump chamber
pump
disk member
positive displacement
eccentric drive
Prior art date
Application number
PCT/JP2014/057354
Other languages
English (en)
Japanese (ja)
Inventor
義朗 敦賀
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
Priority to JP2015508370A priority Critical patent/JP6341908B2/ja
Publication of WO2014156842A1 publication Critical patent/WO2014156842A1/fr

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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
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/04—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type
    • F04C2/045—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type having a C-shaped piston
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle

Definitions

  • the present invention relates to a positive displacement pump that sucks and discharges fluid by changing the volume of a pump chamber using an eccentric drive member.
  • a positive displacement pump that sucks and discharges fluid by changing its volume performs fluid suction from the suction port while increasing the volume of the pump chamber, and discharges fluid from the discharge port while decreasing the volume of the pump chamber.
  • an arc-shaped pump chamber is divided into an inner pump chamber and an outer pump chamber by an arc-shaped partition formed on an eccentric disk (eccentric drive member).
  • an eccentric disk eccentric drive member.
  • the conventional positive displacement pump described above has a problem in durability because a thrust load is applied by the pressure in the pump chamber.
  • This invention is made in view of such a subject, and it aims at providing the positive displacement pump which can reduce a thrust load.
  • the positive displacement pump includes a rotary shaft, an eccentric drive member that is eccentrically mounted on the rotary shaft, and moves along an annular path centering on the rotary shaft in accordance with a rotational operation of the rotary shaft, A first cylinder disposed on one side of the eccentric drive member in the rotational axis direction and forming a first pump chamber together with the eccentric drive member; and a first cylinder disposed on the other side of the eccentric drive member in the rotational axis direction.
  • a second cylinder that forms a second pump chamber together with the eccentric drive member; a suction port for introducing fluid into the first pump chamber and the second pump chamber; and the first and second pump chambers.
  • a pump head having a discharge port for discharging fluid.
  • the pump chambers are formed on both sides in the rotational axis direction of the eccentric drive member, so that the thrust load generated by each pump chamber is in the opposite direction, and is just offset.
  • the generation of thrust load can be reduced.
  • the eccentric drive member includes a first disk member and a second disk member that are coaxially arranged, and the first cylinder rotates with the first disk member.
  • the first pump chamber having an annular shape or a circular arc shape is formed opposite to one side in the axial direction together with the first disk member, and the second cylinder is connected to the second disk member in the rotational axis direction.
  • the second pump chamber can be configured so as to face the other side and form an annular or arcuate second pump chamber together with the second disk member.
  • the first disk member includes a first partition that divides a first pump chamber into a first inner pump chamber and a first outer pump chamber on a surface facing the first cylinder; A first inner pump chamber discharge port communicating with the discharge port and the first inner pump chamber; and a first outer pump chamber discharge port communicating with the discharge port and the first outer pump chamber;
  • the second disk member includes a second partition wall that divides a second pump chamber into a second inner pump chamber and a second outer pump chamber on a surface facing the second cylinder, and the discharge port.
  • a second inner pump chamber discharge port communicating with the second inner pump chamber, and a second outer pump chamber discharge port communicating with the discharge port and the second outer pump chamber, 1 cylinder includes the suction port, the first inner pump chamber, and the first outer side.
  • a second pump chamber having a first pump chamber suction port communicating with the pump chamber, wherein the second cylinder communicates with the suction port, the second inner pump chamber, and the second outer pump chamber. It can also be configured to have a suction port.
  • the change in the discharge flow rate from the first inner pump chamber and the second inner pump chamber due to the movement of the eccentric drive member along the annular path is reversed, and the first outer Changes in the discharge flow rate from the pump chamber and the second outer pump chamber may be reversed.
  • the pulsation of the flow rate can be further reduced and theoretically eliminated.
  • the first outer pump may have the same phase as a change in discharge flow rate from the first inner pump chamber and the second inner pump chamber due to the movement of the eccentric drive member along the annular path.
  • the change in discharge flow rate from the chamber and the second outer pump chamber may be in phase.
  • the suction port and the discharge port can be arranged at the same phase position in the rotation direction in the first pump chamber and the second pump chamber. There is an advantage that maintenance such as processing becomes easy.
  • first disk member and the second disk member may be independently formed so that their positions can be adjusted. Thereby, the position of the first disk member and the second disk member can be independently or automatically adjusted without strictly managing the processing accuracy and assembly accuracy of the disk member and cylinder. As compared with the case where both are integrated, the processing accuracy management and the assembly accuracy management become easier, and the positive displacement pump can be manufactured more easily.
  • the positive displacement pump is coupled to the distal end of the rotational shaft so that the position in the rotational axis direction can be adjusted, and the first disk member and the second disk member are mounted, and the second disk is disposed on the proximal end side.
  • An eccentric shaft having a first positioning portion for defining a position of the member in the rotation axis direction, and a position of the first disk member in the rotation axis direction coupled to the tip of the eccentric shaft so that the position of the rotation axis direction can be adjusted.
  • Front end side rotation shaft portion Drive side rotation shaft portion Cap member Front end side rotation shaft portion This allows the first disk and the second disk to be individually adjusted in the direction of the rotation axis and assembled. Clearance management suitable for the characteristics becomes possible, and a positive displacement pump with higher pump efficiency can be provided.
  • first disk member and the second disk member may be independently rotatable within a predetermined angle range. This enables automatic position adjustment in the rotational direction between the first disk member and the first cylinder and between the second disk member and the second cylinder. It is possible to easily prevent the occurrence of problems such as noise and wear due to contact.
  • the first cylinder includes a first fluid path for communicating the suction port and the first pump chamber suction port
  • the second cylinder includes the suction port and the second pump chamber suction port.
  • a second fluid path that communicates the mouth may be provided.
  • the position where the first pump chamber suction port communicates with the first fluid path and the position where the second pump chamber suction port communicates with the second fluid path are the rotation of the rotating shaft. You may substantially agree in the direction.
  • the transfer target is a liquid
  • the transfer target can be sucked into the first and second pump chambers from the lower ends of the first and second fluid paths, and the liquid is supplied to the first and second fluids. Can be suitably discharged from the fluid path.
  • FIG. It is a figure which shows the mode of the 1st pump chamber at the time of operation
  • FIG. It is a front view which notches and shows a part of positive displacement pump which concerns on 2nd embodiment of this invention. It is sectional drawing which looked at the same volume type pump from the side surface direction. It is a disassembled perspective view of the positive displacement pump. It is a sectional side view of the eccentric drive member of the positive displacement pump. It is a front view of the 1st disc member 24 of the positive displacement pump.
  • FIG. 1 is a front view showing a part of the positive displacement pump according to the first embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of the positive displacement pump as viewed from the side.
  • FIG. 3 is an exploded perspective view of the same displacement pump.
  • the positive displacement pump includes a rotation driving force transmission unit 1 centering on a rotation shaft 11 that transmits a rotation driving force from a rotation driving source such as a motor (not shown), and a rotation shaft of the rotation driving force transmission unit 1. 11, the disk-shaped eccentric drive member 2 mounted in an eccentric state is opposed to the front side in the rotational axis direction of the eccentric drive member 2 and is supplied with fluid from the first flow path.
  • the first pump head 3 forming one pump chamber 6 faces the rear side of the eccentric drive member 2 in the direction of the rotation axis, and is supplied with fluid from the second flow path.
  • the rotational driving force transmission unit 1, the first pump head 3, the second pump head 4, and the third pump head 5 include bolts 61 that pass through the bolt through holes 319, 329, 519, and 419 shown in FIG. It is fixed by the register mark screw 62.
  • the front surface of the first pump head 3 is covered with a front cover 34.
  • the rotational driving force transmission unit 1 includes a rotation shaft 11 and a bearing portion 17 that rotatably supports the rotation shaft 11.
  • the bearing portion 17 is composed of a pair of tapered roller bearings 171 and 172 that are arranged in plane symmetry to receive loads in the radial direction and the thrust direction (axial direction). These tapered roller bearings 171 and 172 are accommodated inside a cylindrical bearing casing 122 and the inside is sealed by seal members 173 and 174 disposed at both ends.
  • the front end of the bearing casing 122 is fixed to the flange 121, and is fixed to the second pump head 4 via the flange 121.
  • an attachment portion 13 for attaching the positive displacement pump to a fixed portion such as a floor surface or a wall surface is fixed to the flange 121.
  • a mechanical seal 14 is attached to the rotating shaft 11.
  • a portion of the rotating shaft 11 disposed inside the first to third pump heads 3 to 5 is an eccentric shaft 15 that is eccentric with respect to the rotating shaft 11.
  • the eccentric drive member 2 is rotatably mounted on the eccentric shaft 15 via a bearing 16. Thereby, the eccentric drive member 2 moves along an annular path centering on the rotation shaft 11 as the rotation shaft 11 rotates.
  • FIG. 4 is a side view of the eccentric drive member 2.
  • FIG. 5 is a front view of the eccentric drive member 2 housed in the third pump head 5
  • FIG. 6 is a rear view of the same.
  • the eccentric drive member 2 includes a first disk member 22 and a second disk member 23 that are coaxially arranged, and a connecting portion 21 that connects them.
  • the first disk member 22 and the second disk member 23 are formed with bearing cylinders 221 and 231 each having an insertion hole 211 formed in the center for mounting on the eccentric shaft 15 via the bearing 16 (FIG. 2). Has been.
  • the axially outer surfaces of the first and second disk members 22 and 23 form a first pump chamber 6 and a second pump chamber 7 together with a first cylinder 312 and a second cylinder 412 described later, respectively. It functions as pump chamber forming surfaces 223, 224, 233, 234.
  • the first and second disk members 22 and 23 have C-shaped or arc-shaped first partition walls 222 arranged on the outer surfaces in the axial direction of the first and second disk members 22 and 23 with the positions of their open ends shifted by 180 °.
  • the second partition walls 232 are provided so as to protrude outward in the axial direction.
  • the first partition 222 and the second partition 232 are provided between the bearing cylinders 221 and 231 and the outer peripheral edges of the disk members 22 and 23 on the outer surfaces of the first and second disk members 22 and 23, respectively. Is formed coaxially with the insertion hole 211 at an intermediate position in the radial direction.
  • the first disk member 22 and the second disk member 23 are respectively close to the open ends of the first partition 222 and the second partition 232 at the inner and outer positions sandwiching the partition walls 222 and 232.
  • 23 and inner pump chamber discharge ports 225, 235 and outer pump chamber discharge ports 226, 236 are formed, respectively.
  • the discharge ports 225 and 226 formed in the first disk member 22 and the discharge ports 235 and 236 formed in the second disk member 23 are also formed at positions shifted from each other by 180 °.
  • FIG. 7 is a rear view of the first pump head 3.
  • the first pump head 3 includes a first frame 31 and a second frame 32 (see FIGS. 2 and 3).
  • the first frame 31 has a first bearing cylinder housing port 311 for housing the bearing cylinder 221 (FIG. 5) in the center, and a first partition 222 (FIG. 5) on the outside thereof.
  • a first cylinder 312 that forms a C-shaped or arc-shaped first pump chamber 6 is formed.
  • a facing surface 314 facing the pump chamber forming surface 224 (FIG. 5) is formed on the outer periphery thereof, and an outer peripheral flange 315 is formed on the outer side thereof.
  • a frame portion 313 between the first bearing cylinder housing port 311 and the first cylinder 312 is coupled to the facing surface 314 of the first frame 31 via a connecting portion 316.
  • the position of the connecting portion 316 corresponds to the position of the open end of the first partition 222 of the eccentric drive member 2.
  • a bolt through hole 319 is formed in the outer peripheral flange 315.
  • the pump chamber forming surface 323 that forms the first pump chamber 6 of the second frame 32 is formed with a suction port 322 that penetrates the second frame 32 at a position near the connecting portion 316. ing.
  • the suction port 322 and the discharge ports 225 and 226 (FIG. 5) of the eccentric drive member 2 are disposed on the opposite sides with respect to the connecting portion 316.
  • a first fluid path 321 is formed in the second frame 32, and the first fluid path 321 and the suction port 322 communicate with each other.
  • the upper end of the first fluid channel 321 is closed by a cap 33 so as to be opened and closed.
  • FIG. 8 is a front view of the second pump head 4.
  • the second pump head 4 is configured in substantially the same manner except that the positional relationship with the first pump head described above is different by 180 °. That is, the second pump head 4 includes a third frame 41.
  • the third frame 41 has a second bearing cylinder accommodating port 411 that penetrates the third frame 41 at the center and accommodates the bearing cylinder 231 (FIG. 6), and a second partition wall on the outside thereof.
  • a second cylinder 412 that accommodates 232 (FIG. 6) and forms a C-shaped or arc-shaped second pump chamber 7 is formed. Further, an opposing surface 415 facing the pump chamber forming surface 234 (FIG.
  • a frame portion 413 between the second bearing cylinder housing port 411 and the second cylinder 412 is coupled to the facing surface 415 of the third frame 41 via a connecting portion 418.
  • the position of the connecting portion 418 corresponds to the position of the open end of the second partition wall 232 of the eccentric drive member 2.
  • a bolt through hole 419 is formed in the outer peripheral flange 410.
  • the pump chamber forming surface 414 that forms the second pump chamber 7 of the third frame 41 has a second fluid path 416 ( A suction port 417 communicating with FIG. 2) is formed.
  • the suction port 417 and the discharge ports 235 and 236 (FIG. 6) of the eccentric drive member 2 are disposed on the opposite sides with respect to the connecting portion 418.
  • a second fluid path 416 is formed in the third frame 41, and the second fluid path 416 and the suction port 417 communicate with each other.
  • the upper end of the second fluid channel 416 is closed by a cap 42 so as to be opened and closed.
  • the third pump head 5 has a suction port 512 for introducing a transfer fluid (liquid or gas) at its upper end, and a fluid from the suction port 512 to the first fluid path.
  • a fluid branch path 513 for branching and feeding to 321 and the second fluid path 416 is provided.
  • the fluid branch path 513 is connected to the first fluid path 321 and the second fluid path 416 via sealed joints 52 and 53.
  • the space in which the eccentric drive member 2 of the third pump head 5 is accommodated becomes a discharge fluid flow path 511 in which the transfer fluid discharged from the first and second pump chambers 6 and 7 is accommodated.
  • the third pump head 5 is formed with a discharge port 514 that communicates with the discharge fluid flow path 511 and discharges the transfer fluid to the outside.
  • FIG. 9 is a diagram showing the position of the eccentric drive member 2 in the first pump chamber 6 at each time point of one cycle of the same displacement pump
  • FIG. 10 is also the eccentric drive member 2 in the second pump chamber 7.
  • the first partition 222 divides the first pump chamber 6 into a first inner pump chamber 6a and a first outer pump chamber 6b on the inner peripheral side and the outer peripheral side
  • the second partition 232 divides the second pump chamber 7 into a second inner pump chamber 7a and a second outer pump chamber 7b on the inner peripheral side and the outer peripheral side.
  • FIGS. 9 and 10 show a state in which the eccentric drive member 2 moves counterclockwise when viewed from the front, and the center position of the eccentric drive member 2 is shown in FIGS. 9 (a) and 10 (a).
  • each is located at a position of 270 °.
  • FIG. 11 is a graph showing a change in the discharge amount of the transfer fluid from each pump chamber.
  • the discharge flow rate of the transfer fluid from the discharge port 225 of the first inner pump chamber 6a reaches the maximum value from the minimum value.
  • the discharge flow rate of the transfer fluid from the discharge port 226 of the first outer pump chamber 6b is in the middle stage from the maximum value to the minimum value.
  • the amount of suction through the suction port 322 into the first inner pump chamber 6a is increasing.
  • the discharge flow rate of the transfer fluid from the discharge port 225 of the first inner pump chamber 6a reaches the maximum value
  • the discharge flow rate of the transfer fluid from the discharge port 226 of the outer pump chamber 6b reaches the minimum value.
  • the suction via the suction port 322 to the first outer pump chamber 6b is started.
  • the change in the discharge flow rate from the first inner pump chamber 6a and the change in the discharge flow rate from the first outer pump chamber 6b are 180 ° out of phase with each other.
  • the flow rate from the first outer pump chamber 6b is slightly larger than the flow rate from the first inner pump chamber 6a due to the pump volume and the like, the discharge flow rate of the first pump chamber 6 is Slight pulsation will occur.
  • the change in the discharge flow rate from the second inner pump chamber 7a and the change in the discharge flow rate from the second outer pump chamber 7b are 180 ° out of phase with each other.
  • the flow rate change in the first pump chamber 6 and the flow rate change in the second pump chamber 7 are in a phase different by 180 °. Therefore, by adding up the flow rate from the first pump chamber 6 and the flow rate from the second pump chamber 7, it is possible to realize the supply of fluid without pulsation.
  • suction is always performed by the 1st pump chamber and the 2nd pump chamber, and it arises by the force produced by the suction of the 1st pump chamber, and the suction of the 2nd pump chamber.
  • the force is in the opposite direction. Therefore, it is possible to reduce the load on the crankshaft (rotating shaft 11) in the axial direction, and to reduce the burden on the tapered roller bearings 171 and 172 (bearings) shown in FIG. Therefore, it is possible to apply small bearings as the tapered roller bearings 171 and 172, and it is possible to keep the pump chamber periphery in a substantially complete non-sliding state, thereby effectively preventing contamination. It is possible to suppress.
  • FIG. 12 is a front view of the positive displacement pump according to the second embodiment of the present invention, with a part thereof cut away, and
  • FIG. 13 is a cross-sectional view as seen from the side of the positive displacement pump.
  • FIG. 14 is an exploded perspective view of the positive displacement pump.
  • the positive displacement pump according to the present embodiment includes a first disk member 24 and a second disk formed independently so as to divide the eccentric drive member 2 into two in the axial direction.
  • the eccentric drive member 2 is configured by combining the first disk member 24 and the second disk member 25 in the rotation axis direction.
  • the positive displacement pump according to the present embodiment is configured to be able to adjust the position of the first disk member 24 and the second disk member 25 in the rotation axis direction with respect to the rotation shaft 18 and the eccentric shaft 15.
  • the positive displacement pump according to this embodiment is configured in the same manner as the positive displacement pump according to the first embodiment in other aspects.
  • the rotary shaft 18 and the eccentric shaft 15 of the positive displacement pump include a drive-side rotary shaft portion 180 that transmits a rotation operation, and a rotary shaft on the tip side of the drive-side rotary shaft portion 180.
  • Rotating to the distal end side of the eccentric shaft 15 and the distal end side rotational shaft portion 181 that is coupled from the direction and the eccentric shaft 15 is integrally formed on the distal end side and the position of the rotational axis direction can be adjusted with respect to the drive side rotational shaft portion 180.
  • a cap member (attachment member) 191 that is coupled from the axial direction and can adjust the position of the eccentric shaft 15 in the rotational axis direction.
  • the drive-side rotary shaft portion 180 is a shaft that transmits a rotational driving force from a rotational driving source such as a motor (not shown), and is rotatably supported by the bearing portion 17 described above as shown in FIG.
  • the mechanical seal 14 is attached to the drive side rotation shaft portion 180.
  • a front portion of the drive side rotation shaft portion 180 is formed in a substantially cylindrical shape, and a front end side rotation shaft portion 181 is slidably inserted into the front portion.
  • the front end side rotation shaft portion 181 is a substantially cylindrical member that is coaxial with the front end portion of the drive side rotation shaft portion 180, for example, as shown in FIG.
  • the rear end of the eccentric shaft 15 protrudes in the outer circumferential direction with respect to the rotating shaft, and abuts against the back surface of the second disk member 25 via the bearing 16, thereby positioning the second disk member 25 in the rotating shaft direction.
  • a positioning portion 182 for performing the above is formed.
  • the rear end portion of the distal end side rotation shaft portion 181 is divided into a plurality of segments 184 by a plurality of slits 183, and the collet chuck is formed together with the collet 186 and the drawbar 188 formed in a tapered shape. It is composed.
  • the drawbar insertion hole 187 which penetrates these along the rotating shaft is formed in the front end side rotating shaft part 181 and the eccentric shaft 15. As shown in FIG.
  • the cap member 191 is a cap inserted from the front into the front portion of the eccentric shaft 15 as shown in FIG. Further, the front end of the cap member 191 protrudes in the outer circumferential direction with respect to the eccentric shaft 15 and abuts against the front surface of the first disk member 24 via the bearing 16, thereby rotating the first disk member 24 in the direction of the rotation axis.
  • a positioning portion 192 for performing positioning is formed.
  • the rear end portion of the cap member 191 is divided into a plurality of segments 194 by a plurality of slits 193, and constitutes a collet chuck together with the collet 196 and the drawbar 198 formed in a tapered shape. Yes.
  • the cap member 191 is formed with a draw bar insertion hole 197 that penetrates the cap member 191 along the rotation axis direction.
  • FIG. 15 is a side sectional view of the eccentric drive member 2 according to the present embodiment.
  • FIG. 16 is a front view of the first disk member 24 of the eccentric drive member 2
  • FIG. 17 is a rear view of the first disk member 24
  • FIG. 18 is a rear view of the second disk member 25.
  • the eccentric drive member 2 includes a first disk member 24 and a second disk member 25 that are formed independently of each other. At the center of the first disk member 24 and the second disk member 25, the first disk member 24 and the second disk member 25 are mounted on the eccentric shaft 15 via the bearing 16 (FIG. 13). Insertion holes 240 and 250 are formed.
  • the first disk member 24 and the second disk member 25 are provided with coupling base portions 201 and 206 projecting from each other on the opposing surface side, and these coupling base portions 201 and 206 are in a predetermined state. Opposite through an interval.
  • the coupling base portion 206 formed on the front surface of the second disk member 25 is formed with a guide pin locking hole 207 for locking the guide pin 26 and a spring locking hole 208 for locking the spring 27. .
  • a guide pin locking hole 202 for locking the guide pin 26 and a spring locking hole 203 for locking the spring 27 are also formed in the coupling base portion 201 formed on the back surface of the first disk member 24. Yes.
  • the inner diameter of the guide pin locking hole 202 is formed larger than the outer diameter of the guide pin 26. That is, the first disk member 24 and the second disk member 25 have a so-called backlash with respect to the rotation direction, and can rotate independently within a predetermined angle range. The angles of the first disk member 24 and the second disk member 25 are adjusted to a naturally suitable position during the operation of the eccentric disk pump. Note that, as shown in FIG. 17, the spring locking holes 203 and the guide spring locking holes 202 are provided approximately equally from the center of the insertion hole 240 for each predetermined angle.
  • the first disk member 24 according to the present embodiment is formed in the same manner as the first disk member 22 according to the first embodiment in other points.
  • the second disk member 25 according to the present embodiment is also formed in the same manner as the second disk member 23 according to the first embodiment in other points. That is, as shown in FIGS. 16 and 18, the first disk member 24 and the second disk member 25 are formed with insertion holes 240 and 250 at the center.
  • the axially outer surfaces of the first and second disk members 24, 25 function as pump chamber forming surfaces 243, 244, 253, 254, respectively.
  • first and second disk members 24, 25 have C-shaped or arc-shaped first partition walls 242 disposed on the outer surfaces in the axial direction of the first and second disk members 24, 25 with the positions of the open ends thereof being shifted by 180 °, respectively.
  • Each of the second partition walls 252 protrudes outward in the axial direction.
  • the first partition 242 and the second partition 252 are formed between the bearing cylinders 241 and 251 and the outer peripheral edges of the disk members 24 and 25 on the outer surfaces of the first and second disk members 24 and 25, respectively. Are formed coaxially with the insertion holes 240 and 250 at an intermediate position in the radial direction.
  • first disk member 24 and the second disk member 25 have disk members 24 at inner and outer positions sandwiching the partition walls 242 and 252, respectively, near the open ends of the first partition wall 242 and the second partition wall 252.
  • 25, inner pump chamber discharge ports 245 and 255 and outer pump chamber discharge ports 246 and 256 are respectively formed.
  • the discharge ports 245 and 246 formed in the first disk member 24 and the discharge ports 255 and 256 formed in the second disk member 25 are also formed at positions shifted from each other by 180 °.
  • the bearing 16 and the second disk member 25 are firmly attached to the eccentric shaft 15 so that the back surface of the second disk member 25 abuts the positioning portion 182.
  • the front end side rotary shaft portion 181 is inserted into the front end of the drive side rotary shaft portion 180 with the target clearance secured in advance between the second pump head 4 and the draw bar insertion hole 187.
  • the drawbar 188 is rotated, thereby tightening the collet 186 forward.
  • the segment 184 is pressed in the outer circumferential direction by the side surface of the collet 186 formed in a tapered shape, and the positional relationship between the front end side rotating shaft portion 181 and the front end portion of the driving side rotating shaft portion 180 is fixed.
  • a spacer of several tens of ⁇ m is inserted between the front surface of the opposing surface 415 of the second pump head 4 and the pump chamber forming surface 254 of the second disk member 25, and after positioning, The disc member 25 may be pulled out slightly forward to pull out the spacer.
  • the guide pin 26 and the spring 27 are assembled to the second disk member 25, and the bearing 16 and the first disk are mounted on the front portion of the eccentric shaft 15 to which the second disk member 25 is assembled.
  • the member 24 is assembled, and the third pump head 5 is assembled to the third frame 41.
  • the first frame is formed with a spacer or the like for securing a predetermined clearance between the first disk member 24 and the first frame 31 as described above.
  • the cap member 191 is inserted into the front portion of the eccentric shaft 15.
  • the draw bar 198 is rotated through the draw bar insertion hole 197 of the cap member 191, thereby tightening the collet 196 forward.
  • the segment 194 is pressed in the outer circumferential direction by the side surface of the collet 196 formed in a tapered shape, and the positional relationship between the cap member 191 and the front end portion of the eccentric shaft 15 is fixed.
  • the spacer is pulled out by removing the first frame 31 or the like.
  • the clearance between the first disk member 24 and the first frame 31 and the clearance between the second disk member 25 and the third frame 41 can be suitably adjusted.
  • the collet 196 may be tightened to some extent by the draw bar 198 in advance to adjust the frictional force of the cap member 191 with respect to the eccentric shaft 15. .
  • the eccentric drive member 2 according to the first embodiment is formed by integrally forming the first disk member 22 and the second disk member 23, and requires advanced processing technology for the formation. May be.
  • the distance between the first and second disk members 24 and 25 and the first and second cylinders 312 and 412 greatly affects the transfer performance of the positive displacement pump. For example, if this interval is too wide, the transfer capability may be reduced.
  • the first and second disk members 24 and 25 slide on the first and second cylinders 312 and 412, and the friction coefficient therebetween increases, and the eccentric drive member 2. This may hinder the movement of the material, leading to a decrease in transfer capability. In addition, contamination may occur in the sliding portion.
  • the preferred distance between the first and second disk members 24 and 25 and the first and second cylinders 312 and 412 may change.
  • the positive displacement pump is operated at a high temperature, it is necessary to consider the thermal expansion of the eccentric drive member 2 and the like.
  • the preferable interval varies depending on the viscosity of the liquid.
  • the positions of the positioning portions 182 and 192 with respect to the rotation axis direction are adjusted, and thereby the distance between the first disk member 24 and the second disk member 25 is adjusted. It is possible to do. Therefore, a highly versatile positive displacement pump capable of suitably adjusting the distance between the first and second disk members 24 and 25 and the first and second cylinders 312 and 412 according to conditions. Can be provided.
  • the angle between the two is larger than when the two are formed integrally.
  • Increased tolerance for directional errors For example, in the case of an integrated type, the positional accuracy of the open ends of the first partition 222 and the second partition 232 and the positional accuracy of the cylinder side coupling portions 316 and 414 that engage with the open ends are not secured. May cause contact, wear, noise, etc., which may affect the preferred operation of the positive displacement pump.
  • the positive displacement pump according to the present embodiment is configured such that the first disk member 24 and the second disk member 25 can be independently rotated within a predetermined angle range.
  • the rotation angles of the first and second disk members 24, 25 relative to the first and second cylinders 312 and 412 are suitably adjusted during operation. Therefore, the first disk member 24 and the second disk member 25 according to the present embodiment do not need to precisely adjust the rotation angle with respect to each other, and can be easily manufactured.
  • FIG. 21 is a cross-sectional view of the positive displacement pump according to the third embodiment of the present invention as seen from the side.
  • the first fluid path 321 communicates with the first pump chamber suction port 317 at the lower end
  • the second fluid path 461 is The lower end communicates with the second pump chamber suction port 457.
  • the first pump chamber suction port 317 and the second pump chamber suction port 457 are both positioned below the rotation shaft 18.
  • the discharge flow rates of the first pump chamber 6 and the second pump chamber 7 were opposite to each other, but in this embodiment, the first pump chamber 6 and the second pump The discharge flow rate in the chamber 7 is in phase.
  • the second pump head 4 is provided with a third frame 41 integrally formed.
  • the fourth frame 45 and the fifth frame 46 formed independently are provided for the convenience of processing.
  • the first frame 31 covers the entire back surface of the second frame 32, and the front cover 34 is attached to the front surface of the second frame 32.
  • the first frame 31 covers only the vicinity of the rotation axis on the back surface of the second frame 32, and the front surface of the second frame 32 is integrally formed.
  • the positive displacement pump according to the present embodiment is configured in substantially the same manner as the positive displacement pump according to the second embodiment in other aspects.
  • FIG. 22 is a front view of the state in which the eccentric drive member 2 is accommodated in the third pump head 5, and FIG. 23 is a rear view of the same.
  • the eccentric drive member 2 according to the present embodiment includes a first disk member 24 and a second disk member 25 that are formed independently of each other, like the eccentric drive member 2 according to the second embodiment. Yes.
  • the first disk member 24 and the second disk member 25 are formed in substantially the same manner as the first disk member 24 and the second disk member 25 according to the second embodiment. The difference is that the position of the open end is located directly below the insertion holes 240 and 250, respectively.
  • first disk member 24 and the second disk member 25 are formed by cutting out a part of a substantially circular shape, and these cutouts are used as outer pump chamber discharge ports 247 and 257. . Since the other configuration has been described with reference to FIGS. 15 to 18, the description thereof will be omitted.
  • FIG. 24 is a rear view of the first pump head 3.
  • the first pump chamber suction port 317 is located immediately below the center of the first bearing cylinder housing port 311.
  • the first frame 31 covers only the vicinity of the rotation axis on the back surface of the second frame 32.
  • the first pump head 3 is formed in substantially the same manner as the first pump head 3 according to the first embodiment in other points.
  • the first pump head 3 includes a first frame 31 and a second frame 32 (see FIG. 21).
  • the first frame 31 has a first bearing cylinder housing port 311 that penetrates the first frame 31 in the center and accommodates the bearing cylinder 241 (FIG. 22), and a first partition wall on the outside thereof.
  • a first cylinder 312 that accommodates 242 (FIG. 22) and forms a C-shaped or arc-shaped first pump chamber 6 is formed.
  • a facing surface 314 facing the pump chamber forming surface 244 (FIG. 22) is formed.
  • a frame portion 313 between the first bearing cylinder housing port 311 and the first cylinder 312 has a first frame 31 via a pump chamber forming surface 318 and a connecting portion 316 that form the first pump chamber 6. Are coupled to the opposite surface 314.
  • the position of the connecting portion 316 corresponds to the position of the open end of the first partition 242 of the eccentric drive member 2.
  • the pump chamber forming surface 318 has a suction port 317 that penetrates the first frame 31 in the vicinity of the connecting portion 316 and communicates with the first fluid path 321 (FIG. 21) in the second frame 32. Is formed.
  • the suction port 317 and the discharge ports 245 and 247 (FIG. 22) of the eccentric drive member 2 are disposed on the opposite sides with respect to the connecting portion 316.
  • a first fluid path 321 is formed in the second frame 32, and the first fluid path 321 and the suction port 317 communicate with each other.
  • the upper end of the first fluid channel 321 is closed by a cap 33 so as to be opened and closed.
  • an outer peripheral flange 325 is formed on the outer peripheral side of the second frame 32, and a bolt through hole 329 is formed in the outer peripheral flange 325.
  • FIG. 25 is a rear view of the second pump head 4.
  • the second pump chamber suction port 457 is located immediately below the center of the bearing cylinder housing port 451.
  • the fourth frame 45 covers only the vicinity of the rotation axis on the front surface of the fifth frame 46.
  • the second pump head 4 is formed in substantially the same manner as the second pump head 4 according to the first embodiment in other points.
  • the second pump head 4 includes a fourth frame 45 and a fifth frame 46 (see FIG. 21).
  • the fourth frame 45 has a bearing cylinder housing port 451 that penetrates the fourth frame 45 in the center and accommodates the bearing cylinder 251 (FIG. 23), and a second partition 252 (see FIG. 23) and a second cylinder 452 forming a C-shaped or arc-shaped second pump chamber 7 is formed. Further, on the outer periphery thereof, a facing surface 454 facing the pump chamber forming surface 254 (FIG. 23) is formed.
  • a frame portion 453 between the bearing cylinder housing port 451 and the second cylinder 452 is an opposing surface of the fourth frame 45 via a pump chamber forming surface 458 and a connecting portion 456 that form the second pump chamber 7. 454.
  • the position of the connecting portion 456 corresponds to the position of the open end of the second partition 252 of the eccentric drive member 2.
  • the pump chamber forming surface 458 has a suction port 457 that communicates with the fourth frame 45 in the vicinity of the connecting portion 456 and communicates with the second fluid path 461 (FIG. 21) in the fifth frame 46. Is formed.
  • the suction port 457 and the discharge ports 255 and 257 (FIG. 23) of the eccentric drive member 2 are disposed on the opposite sides with respect to the connecting portion 456.
  • a second fluid path 461 is formed in the fifth frame 46, and the second fluid path 461 and the suction port 457 communicate with each other.
  • the upper end of the second fluid channel 461 is closed by a cap 42 so as to be opened and closed.
  • an outer peripheral flange 465 is formed on the outer peripheral side of the fifth frame 46, and a bolt through hole 469 is formed in the outer peripheral flange 465.
  • the position communicating with the fluid path 461 substantially coincides with the rotational direction of the rotating shaft 18. Therefore, for example, by installing the positive displacement pump so that the first pump chamber suction port 317 and the second pump chamber suction port 457 are positioned below the rotation shaft 18, the first and second fluid paths
  • the transfer object can be sucked into the first and second pump chambers 6 and 7 from the lower ends of 321 and 461, and the transfer object can be suitably discharged from the first and second fluid paths 321 and 461.
  • the position where the first pump chamber suction port 317 communicates with the first fluid path 321 and the position where the second pump chamber suction port 457 communicates with the second fluid path 461 are: Since they substantially coincide with each other in the rotation direction of the rotary shaft 18, there is an advantage that the sealing structure is easy as compared with the case where these are different by 180 °. Further, since the discharge ports 255 and 257 of the eccentric drive member 2 are at the same position, there are advantages that the residual liquid can be easily discharged and the inside of the pump chamber can be easily cleaned.
  • SYMBOLS 1 Rotation driving force transmission part, 2 ... Eccentric drive member, 3 ... 1st pump head, 4 ... 2nd pump head, 5 ... 3rd pump head, 6 ... 1st pump chamber, 6a ... 1st Inner pump chamber, 6b ... first outer pump chamber, 7 ... second pump chamber, 7b ... first inner pump chamber, 7b ... second outer pump chamber, 11 ... rotating shaft, 18 ... rotating shaft, DESCRIPTION OF SYMBOLS 21 ... Connection part, 22 ... 1st disc member, 23 ... 2nd disc member, 24 ... 1st disc member, 25 ... 2nd disc member, 180 ... Drive side rotating shaft part, 181 ...

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une pompe volumétrique qui comprend : un arbre rotatif ; un élément d'entraînement excentrique qui est monté de manière excentrique sur l'arbre rotatif et qui se déplace le long d'une trajectoire annulaire circulaire lorque l'arbre rotatif tourne, la trajectoire annulaire circulaire étant centrée sur l'arbre rotatif ; un premier cylindre qui est installé d'un côté de l'élément d'entraînement excentrique en direction de l'axe de rotation de celui-ci et qui forme une première chambre de pompe en coopération avec l'élément d'entraînement excentrique ; un deuxième cylindre qui est installé de l'autre côté de l'arbre d'entraînement excentrique en direction de l'axe de rotation de celui-ci et qui forme une deuxième chambre de pompe en coopération avec l'élément d'entraînement excentrique ; et une tête de pompe qui présente une ouverture d'aspiration pour l'introduction de fluide dans la première chambre de pompe et la deuxième chambre de pompe et qui présente aussi une ouverture de refoulement pour refouler le fluide à partir des première et deuxième chambres de pompe.
PCT/JP2014/057354 2013-03-28 2014-03-18 Pompe volumétrique WO2014156842A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2015508370A JP6341908B2 (ja) 2013-03-28 2014-03-18 容積型ポンプ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013069389 2013-03-28
JP2013-069389 2013-03-28

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Publication Number Publication Date
WO2014156842A1 true WO2014156842A1 (fr) 2014-10-02

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61151090U (fr) * 1985-03-13 1986-09-18
JPH0693989A (ja) * 1992-09-09 1994-04-05 Aisin Seiki Co Ltd 圧縮機
WO2005108794A1 (fr) * 2004-05-11 2005-11-17 Daikin Industries, Ltd. Machine rotative à fluide
JP2005320929A (ja) * 2004-05-11 2005-11-17 Daikin Ind Ltd 回転式流体機械
JP2009197795A (ja) * 2008-01-24 2009-09-03 Daikin Ind Ltd 回転式流体機械
JP2010106754A (ja) * 2008-10-30 2010-05-13 Daikin Ind Ltd 圧縮機
JP2013024052A (ja) * 2011-07-15 2013-02-04 Daikin Industries Ltd 回転式圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61151090U (fr) * 1985-03-13 1986-09-18
JPH0693989A (ja) * 1992-09-09 1994-04-05 Aisin Seiki Co Ltd 圧縮機
WO2005108794A1 (fr) * 2004-05-11 2005-11-17 Daikin Industries, Ltd. Machine rotative à fluide
JP2005320929A (ja) * 2004-05-11 2005-11-17 Daikin Ind Ltd 回転式流体機械
JP2009197795A (ja) * 2008-01-24 2009-09-03 Daikin Ind Ltd 回転式流体機械
JP2010106754A (ja) * 2008-10-30 2010-05-13 Daikin Ind Ltd 圧縮機
JP2013024052A (ja) * 2011-07-15 2013-02-04 Daikin Industries Ltd 回転式圧縮機

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JP6341908B2 (ja) 2018-06-13
JPWO2014156842A1 (ja) 2017-02-16

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