WO2022219886A1 - Dispositif pompe - Google Patents

Dispositif pompe Download PDF

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Publication number
WO2022219886A1
WO2022219886A1 PCT/JP2022/003925 JP2022003925W WO2022219886A1 WO 2022219886 A1 WO2022219886 A1 WO 2022219886A1 JP 2022003925 W JP2022003925 W JP 2022003925W WO 2022219886 A1 WO2022219886 A1 WO 2022219886A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
pump device
wall
rotor
housing body
Prior art date
Application number
PCT/JP2022/003925
Other languages
English (en)
Japanese (ja)
Inventor
憲夫 竹花
匠 佐々木
Original Assignee
株式会社ミクニ
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 株式会社ミクニ filed Critical 株式会社ミクニ
Priority to US18/274,207 priority Critical patent/US20240084799A1/en
Priority to CN202280011123.8A priority patent/CN116745528A/zh
Priority to DE112022002136.5T priority patent/DE112022002136T5/de
Publication of WO2022219886A1 publication Critical patent/WO2022219886A1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides

Definitions

  • the present invention relates to a pump device that sucks, pressurizes, and discharges fluid, and more particularly to a pump device that is bonded and fixed to a joint surface of an application object such as a cylinder block of an internal combustion engine or fluid equipment.
  • a conventional pump device includes a pump body including an inner rotor and an outer rotor, a pump body defining a housing chamber that houses the pump body, a pump cover that covers the pump body housing the pump body, and a pump body that is coupled to the pump body.
  • An oil pump is known which has a pump shaft protruding from a pump cover through a shaft, the outer wall surface of the pump cover is joined to the joint surface of the transaxle case, and the pump cover is fixed to the case using bolts (for example, See Patent Document 1).
  • the pump body and the pump cover are only fixed to the case using bolts, they cannot be positioned with high accuracy in the direction perpendicular to the pump shaft, that is, in the direction along the joint surface.
  • the width dimension of the pump body and the pump cover is sufficiently larger than the width dimension of the pump body, and the structure causes an increase in the size of the oil pump in the axial direction of the pump shaft.
  • the pump shaft is supported by a single bearing provided in the pump cover, and after being assembled to the case, the tip side of the pump shaft is supported by the bearing inside the case. It is not a structure that reliably supports the pump shaft.
  • Another pump device includes a trochoid including an inner rotor and an outer rotor, a casing defining a trochoid housing recess for housing the trochoid, a cover closing the trochoid housing recess, and a cover coupled to the inner rotor and protruding from the cover.
  • An internal gear pump is known that includes a drive shaft that connects to a fixed plate of a device body, the outer wall surface of the cover is joined to the joint surface of the fixed plate of the device body, and is fixed to the fixed plate using screws (see, for example, Patent Document 2).
  • the cover since the cover has a spigot that fits into the fitting hole of the fixed plate, the casing and the cover can be positioned with respect to the fixed plate in the direction along the joint surface.
  • the plate thickness of the cover is reduced in order to reduce the thickness in the axial direction of the drive shaft, the surface rigidity of the cover around the spigot portion decreases, and there is a risk that desired positioning and mechanical strength cannot be secured.
  • the present invention has been made in view of the above circumstances, and its object is to solve the above-mentioned problems of the prior art, and to achieve thinning and miniaturization while ensuring mechanical strength. , to provide a pump device.
  • the pump device of the present invention comprises a rotor unit that pumps fluid, a housing that defines a suction port, a discharge port, and a storage chamber that stores the rotor unit, and a rotor unit that is coupled to the rotor unit and protrudes outside the housing.
  • the housing Equipped with a rotating shaft that rotates about a predetermined axis, the housing includes a joint wall that is joined to the object to be applied, an outer peripheral wall that cooperates with the joint wall to define a storage chamber, and a housing that projects axially outwardly from the joint wall.
  • the structure includes a bottomed cylindrical housing body integrally having a spigot fitted to an application object, and a flat housing cover coupled to the housing body to close the housing chamber. .
  • a configuration may be adopted in which the thickness dimension of the joint wall is smaller than the thickness dimension of the outer peripheral wall.
  • a configuration may be adopted in which the suction port and the discharge port are provided on the joint wall around the spigot portion.
  • the housing body and the housing cover each include a plurality of insertion holes through which bolts to be fixed to the object to be applied are inserted, and the peripheral wall of the outer peripheral wall is such that the thickness dimension of the peripheral regions of the insertion holes is equal to the thickness dimension of the other regions.
  • the thickness dimension of the housing cover may be larger than the thickness dimension of the joining wall of the housing body and smaller than the thickness dimension of the outer peripheral wall of the housing body.
  • the housing body includes a first bearing hole inside the spigot portion that rotatably supports the one end region of the rotating shaft, and the housing cover rotatably supports the other end region of the rotating shaft.
  • a configuration may be employed that includes a second bearing hole that supports the .
  • the housing cover may employ a configuration including an annular convex portion that protrudes axially outward around the second bearing hole.
  • the housing cover may employ a configuration including a fitting convex portion that fits into the fitting concave portion of the housing body.
  • a configuration may be adopted in which the fitting concave portion of the housing body is formed as part of the inner edge portion that defines the housing chamber.
  • the housing body includes screw holes into which screws are screwed
  • the housing cover includes circular holes through which the screws are passed
  • the housing cover is coupled to the housing body by screws. good too.
  • the rotor unit may employ a configuration including an inner rotor that rotates integrally with the rotating shaft and an outer rotor that rotates in conjunction with the inner rotor.
  • the pump device having the above configuration, it is possible to achieve thinness and miniaturization while ensuring mechanical strength.
  • FIG. 3 is an exploded perspective view of the pump device shown in FIG. 2;
  • FIG. 4 is an exploded perspective view of the pump device shown in FIG. 3; It is a sectional view which cut the pump device concerning one embodiment in the field which passes along the axis of the axis of rotation.
  • FIG. 3 is a perspective cross-sectional view of a housing body, which forms part of the pump device according to one embodiment, taken along a plane passing through the axis of the rotating shaft;
  • FIG. 3 is a cross-sectional view of a housing body, which forms part of the pump device according to one embodiment, taken along a plane passing through the axis of the rotating shaft; It is a front view showing the relationship between the rotor unit (inner rotor and outer rotor) included in the pump device according to one embodiment, the suction port and the discharge port, with the housing cover removed.
  • a pump device M is joined and fixed to a cylinder block CB of an internal combustion engine as an application object.
  • the cylinder block CB as an object to be applied includes a joint surface 1 for joining a pump device M, a cylindrical fitting recess 2, an outflow port 3 for hydraulic oil, and an inflow port for hydraulic oil. 4. It has three screw holes 5 into which bolts B are screwed.
  • the pump device M includes a housing body 10 and a housing cover 20 as a housing H, a rotating shaft 30 centered on a predetermined axis S, an inner rotor 40 and an outer rotor as a rotor unit Ru. 50, a screw b for fastening the housing cover 20 to the housing body 10;
  • the housing body 10 is formed in a cylindrical shape with a bottom using a metal material such as steel, cast iron, sintered steel, aluminum alloy, etc. As shown in FIGS. It has an accommodation chamber 13 , a spigot portion 14 , a suction port 15 , a discharge port 16 , a bearing hole 17 as a first bearing hole, three insertion holes 18 , and one screw hole 19 .
  • the joint wall 11 is formed in a flat plate shape with a thickness dimension T1 and perpendicular to the axis S, and includes an outer wall surface 11a that is joined to the joint surface 1 of the cylinder block CB, which is an object to which it is applied, and a rotor unit.
  • the Ru end surfaces 41, 51 define an inner wall surface 11b that slides in close contact therewith.
  • the outer peripheral wall 12 protrudes cylindrically from the outer edge region of the joint wall 11 in the direction of the axis S to define an annular end face 12a, and has a thickness in a region away from the insertion hole 18.
  • the thickness dimension T2 is formed larger than the thickness dimension T1 of the joint wall 11 .
  • the thickness dimension T3 of the peripheral region of the insertion hole 18 is formed larger than the thickness dimension T2 of the other region away from the insertion hole 18 .
  • the joining wall 11 having a flat plate shape and the outer peripheral wall 12 having a cylindrical shape are integrally formed. Therefore, the bending rigidity of the area where the joint wall 11 and the outer peripheral wall 12 are continuous can be increased compared to the conventional structure in which the joint wall is formed as a flat plate separate from the outer peripheral wall and joined. As a result, even if the joint wall 11 is formed thin, the mechanical strength of the housing body 10 as a whole and the surface rigidity of the joint wall 11 can be ensured. In particular, since the joint wall 11 is joined to the joint surface 1 of the cylinder block CB as an object to be applied, the deformation thereof can be further suppressed or prevented.
  • the housing chamber 13 is a space defined by the joint wall 11 and the outer peripheral wall 12, and rotatably houses the rotor unit Ru. 8 and 9, the storage chamber 13 has an arcuate surface 13a forming a part of a cylindrical surface centered on an axis S1 deviated parallel to the axis S. As shown in FIGS.
  • the circular arc surface 13a functions as an outer peripheral support surface that slidably supports the outer peripheral surface 53 of the outer rotor 50 forming a part of the rotor unit Ru.
  • the inner edge of the arcuate surface 13a is part of the inner edge that defines the housing chamber 13, and functions as a fitting recess into which the fitting protrusion 22 of the housing cover 20 is fitted.
  • the spigot portion 14 protrudes outward in the direction of the axis S from the joint wall 11 and is formed in a cylindrical shape centered on the axis S and having a thickness greater than the thickness dimension T1 of the joint wall 11 .
  • the driven rotating body for example, the gear 6 coupled to the rotating shaft 30
  • the driven rotating body for example, the gear 6
  • the spigot joint portion 14 is formed so as to protrude from the thin plate-like joint wall 11, since the joint wall 11 is formed integrally with the outer peripheral wall 12, the surface rigidity of the joint wall 11 can be ensured. , the rigidity of the spigot joint portion 14 can also be ensured. As a result, the spigot joint portion 14 can be reliably fitted into the fitting concave portion 2 .
  • the suction port 15 is formed penetrating from the outer wall surface 11a to the inner wall surface 11b in the joint wall 11 around the spigot portion 14 so as to form a contour that widens in the direction of rotation. Then, with the pump device M joined to the cylinder block CB, hydraulic oil guided from the outflow port 3 is drawn into the housing chamber 13 through the suction port 15 .
  • the discharge port 16 extends inward from the outer wall surface 11a so as to form a contour that tapers in the direction of rotation in a region of the joint wall 11 around the spigot portion 14 and opposite to the suction port 15 with the spigot portion 14 interposed therebetween. It is formed so as to penetrate to the wall surface 11b. Then, with the pump device M joined to the cylinder block CB, the hydraulic oil pressurized in the housing chamber 13 is discharged through the discharge port 16 toward the inlet 4 .
  • the bearing hole 17 is formed in a cylindrical shape about the axis S inside the spigot portion 14 so as to rotatably support the one end region 31 of the rotating shaft 30 .
  • the bearing hole 17 is formed coaxially (axis line S) inside the spigot portion 14 provided in the joint wall 11 with increased surface rigidity, so that the bearing hole 17 is sufficiently large to support the rotating shaft 30 . mechanical strength can be ensured.
  • the three insertion holes 18 are for inserting the bolts B to be screwed into the screw holes 5 of the cylinder block CB. is formed so as to penetrate the Here, since the thickness dimension T3 of the peripheral region of the three insertion holes 18 is formed to be larger than the thickness dimension T2 of the other regions, the mechanical strength is sufficient to withstand the tightening load (stress) of the bolt B. Strength can be secured.
  • One screw hole 19 is for screwing in a screw b that joins the housing cover 20 to the housing body 10, and is formed in the end face 12a in a thick region near one insertion hole 18. As shown in FIG.
  • the housing cover 20 is joined to the housing body 10 to close the housing chamber 13 of the housing body 10.
  • the housing cover 20 is made of a material such as steel, cast iron, sintered steel, aluminum alloy, etc. and is a flat plate having a thickness T4. formed in the shape of 4 and 5, the housing cover 20 includes a connecting wall 21, a fitting convex portion 22, a bearing hole 23 as a second bearing hole, an annular convex portion 24, three insertion holes 25, and one A circular hole 26 is provided.
  • the thickness T4 of the joint wall 21 region of the housing cover 20 is greater than the thickness T1 of the joint wall 11 of the housing body 10 and the thickness T1 of the outer peripheral wall 12 of the housing body 10. It is set to be smaller than the thickness dimension T2. As a result, the mechanical strength of the housing H as a whole can be ensured while reducing the width dimension W of the pump device M in the direction of the axis S.
  • the connecting wall 21 is formed as a flat surface perpendicular to the axis S and is closely connected to the end face 12a of the housing body 10 .
  • the fitting convex portion 22 is formed in a disc shape centering on the axis S1 and projecting in the direction of the axis S from the coupling wall 21 near the center of the housing cover 20, and defines an outer peripheral surface 22a and an inner wall surface 22b.
  • the outer peripheral surface 22a is fitted to the inner edge of the arcuate surface 13a of the housing body 10 as a fitting recess.
  • the inner wall surface 22b forms a flat surface perpendicular to the axis S so that the end surfaces 42, 52 of the rotor unit Ru can slide in close contact therewith.
  • the fitting projection 22 is slightly press-fitted into the fitting recess (arc surface 13a), so that when the pump device M is handled, the housing can be easily removed by a mere fitting operation.
  • the cover 20 can be connected to the housing body 10 so as not to fall off, and the mechanical strength and rigidity of the housing H as a whole can be increased.
  • the bearing hole 23 is formed in a cylindrical shape around the axis S so as to rotatably support the other end region 32 of the rotating shaft 30 .
  • the annular convex portion 24 is formed in a cylindrical shape that protrudes outward in the axis S direction around the bearing hole 23 .
  • the annular protrusion 24 serves to increase the mechanical strength around the bearing hole 23 .
  • the three insertion holes 25 are for inserting the bolts B to be screwed into the screw holes 5 of the cylinder block CB. formed.
  • One circular hole 26 is formed in the vicinity of one insertion hole 25 for passing a screw b for coupling the housing cover 20 to the housing body 10 .
  • the housing H is composed of the bottomed cylindrical housing body 10 integrally including the joint wall 11 and the outer peripheral wall 12, and the flat housing cover 20. Flexural rigidity and mechanical strength can be increased compared to the case where the is formed as a simple flat plate separately from the outer peripheral wall. Therefore, the thickness dimension T1 of the joint wall 11 can be formed thin, so that the width dimension W in the direction of the axis S of the pump device M can be reduced as shown in FIG. can do. Further, since the mechanical strength and surface rigidity can be ensured even if the thickness of the joint wall 11 is reduced, the rigidity of the spigot joint portion 14 integrally formed with the joint wall 11 can also be ensured.
  • the housing H is joined by fitting the fitting protrusion 22 of the housing cover 20 to the fitting recess (the inner edge of the arcuate surface 13a) of the housing body 10, the housing H as a whole is mechanically stable.
  • the strength and rigidity are increased, and the bearing holes 17 and 23 can be positioned coaxially (axis S) with high accuracy.
  • the rotary shaft 30 is formed of a steel material or the like into a columnar shape extending in the direction of the axis S.
  • One end region 31 is fitted into the bearing hole 17 of the housing body 10, and the other end region 32 is fitted into the housing cover. 20 is fitted in the bearing hole 23, and is rotatably supported around the axis S.
  • the rotation shaft 30 can be rotatably supported around the axis S with high accuracy without causing the axis S to tilt.
  • the rotating shaft 30 is shown in a simple form slightly protruding from the housing H in the direction of the axis S, and details of the end portion are omitted.
  • the drive force of the drive rotor of the internal combustion engine is transmitted to the other end region 32 where the rotary shaft 30 protrudes from the housing cover 20, for example, the driven rotation of the gear 6, sprocket, pulley, etc.
  • the driving force of the drive rotor e.g., rotor, drive shaft
  • the driving force of the driving rotor of the internal combustion engine is transmitted to the one end region 31 where the rotating shaft 30 protrudes from the joint wall 11 of the housing body 10, for example, it may be directly connected to the driving rotor. formed in
  • the rotor unit Ru is arranged in the housing chamber 13 so as to exert a pump action of sucking, pressurizing, and discharging working oil, and is composed of an inner rotor 40 and an outer rotor 50 .
  • the inner rotor 40 is made of a metal material such as steel or sintered steel and is formed as an external gear having a trochoid curve tooth profile. 4 and 5, the inner rotor 40 has an end surface 41 sliding on the inner wall surface 11b of the housing body 10, an end surface 42 sliding on the inner wall surface 22b of the housing cover 20, and the rotary shaft 30. It has a fitting hole 43 , four protrusions 44 and four recesses 45 . 9, the inner rotor 40 rotates about the axis S in the direction of the arrow R together with the rotating shaft 30. As shown in FIG.
  • the outer rotor 50 is made of a metal material such as steel or sintered steel, and is formed as an internal gear having a tooth profile that can mesh with the inner rotor 40 .
  • the outer rotor 50 has an end face 51 that slides on the inner wall surface 11b of the housing body 10, an end face 52 that slides on the inner wall surface 22b of the housing cover 20, and an axis S1. It has a cylindrical outer peripheral surface 53 , five protrusions 54 and five recesses 55 .
  • the outer peripheral surface 53 slidably contacts the arcuate surface 13 a of the housing body 10 .
  • the five protrusions 54 and the five recesses 55 are formed so as to partially mesh with the four protrusions 44 and the four recesses 45 of the inner rotor 40 .
  • the outer rotor 50 rotates in the same direction as the inner rotor 40 about the axis S ⁇ b>1 at a slower speed than the inner rotor 40 while interlocking with the rotation of the inner rotor 40 rotating about the axis S ⁇ b>1 .
  • the inner rotor 40 and the outer rotor 50 are partially meshed with each other, the suction, pressurization, and discharge pump actions are continuously generated between them.
  • the housing body 10, housing cover 20, rotating shaft 30, rotor unit Ru (inner rotor 40 and outer rotor 50), and one screw b are prepared in advance.
  • the rotating shaft 30 is press-fitted into the fitting hole 43 of the inner rotor 40 and fixed so as to rotate together with the inner rotor 40 .
  • a key groove, key, or the like may be employed to reliably restrict the relative rotation.
  • the inner rotor 40 and the outer rotor 50 are fitted into the housing chamber 13 of the housing body 10, and the one end region 31 of the rotating shaft 30 is rotatably inserted into the bearing hole 17 of the housing body 10.
  • the housing cover 20 is brought close to the housing body 10 in the direction of the axis S and joined to the housing body 10 so as to close the housing chamber 13 .
  • the other end region 32 of the rotating shaft 30 is rotatably inserted into the bearing hole 23 of the housing cover 20 , and the fitting convex portion 22 of the housing cover 20 is aligned with the fitting concave portion (arc surface) of the housing body 10 . 13a).
  • a screw b is screwed into the screw hole 19 of the housing body 10 through the circular hole 26 of the housing cover 20 .
  • the housing cover 20 is coupled to the housing body 10 while housing the rotor unit Ru to which the rotating shaft 30 is coupled, and the assembly of the pump device M is completed.
  • the above-described assembling procedure is an example, and assembling may be performed by other procedures.
  • the housing cover 20 is coupled to the housing body 10 by fitting the fitting protrusion 22 into the fitting recess (the inner edge of the arcuate surface 13a that is part of the inner edge defining the housing chamber 13). Therefore, the mechanical strength of the housing H can be increased, and the housing cover 20 can be prevented from coming off.
  • the housing cover 20 is fastened to the housing body 10 using the screw b, so that the housing cover 20 can be reliably prevented from coming off when the pump device M is handled during transport or the like. can be done.
  • a gear 6 is applied as an example of the driven rotating body connected to the rotating shaft 30 .
  • a pump device M as a product
  • a gear 6, three bolts B, and a packing (not shown) as a liquid or molded body are prepared.
  • the gear 6 is connected to the other end region 32 of the rotary shaft 30 of the pump device M. As shown in FIG.
  • the pump device M is brought closer to the cylinder block CB in the direction of the axis S, and with a packing (not shown) interposed between the joint wall 11 (outer wall surface 11a) and the joint surface 1, the spigot joint portion 14 is opened. It is fitted in the fitting recess 2 .
  • the pump device M is positioned on the joint surface 1 in the direction perpendicular to the axis S with high accuracy. Therefore, the gear 6 coupled to the rotary shaft 30 is positioned with high precision with respect to the drive rotor (not shown) of the internal combustion engine.
  • the housing H of the pump device M achieves a reduced thickness while ensuring mechanical strength and rigidity.
  • the fitting work can be easily performed without causing deformation or the like in the joint wall 11 around the portion 14 .
  • the outflow port 3 of the cylinder block CB communicates with the suction port 15 of the pump device M
  • the inflow port 4 of the cylinder block CB communicates with the discharge port 16 of the pump device M. communicates with
  • the housing H includes the joint wall 11 joined to the object to be applied, and the outer peripheral wall 12 defining the accommodation chamber 13 in cooperation with the joint wall 11. , and a bottomed cylindrical housing body 10 integrally having a spigot portion 14 projecting outward from the joint wall 11 in the direction of the axis S and fitted to an application object; Since the structure includes the flat plate-like housing cover 20 coupled to the axis S The width dimension W in the direction can be reduced, and thinning and miniaturization can be achieved.
  • the width W is reduced while ensuring the mechanical strength of the housing H as a whole. be able to.
  • the suction port 15 and the discharge port 16 in the joint wall 11 only by joining the pump device M to the joint surface 1 of the cylinder block CB as an application object, the suction port 15 and the hydraulic fluid outflow port 3 can be communicated, and the discharge port 16 and the hydraulic fluid inflow port 4 can be communicated. Therefore, the mounting work can be simplified compared to a configuration in which the suction port or the discharge port is arranged in another region.
  • the present invention is not limited to this, and bearings (including inner rings, rolling elements, and outer rings) may be used as necessary. ), or a configuration in which the rotating shaft 30 is supported via a cylindrical bush.
  • a configuration may be employed in which an annular seal member is arranged adjacent to the bearing.
  • the housing cover is fitted to the housing body as the fitting convex portion and the fitting concave portion. ) is shown, but it is not limited to this.
  • the housing cover is provided with an annular convex portion as a fitting convex portion
  • the housing body is provided with an annular convex portion as a fitting concave portion.
  • a configuration may be employed in which an annular groove is provided and the annular protrusion is fitted into the annular groove.
  • the screw b for fastening the housing cover 20 to the housing body 10 is used, but the present invention is not limited to this.
  • the screw b may be eliminated if the fitting with the inner edge of the circular arc surface 13a as a part of the defining inner edge can be press-fitted to reliably prevent falling off.
  • the rotor unit Ru including the inner rotor 40 and the outer rotor 50 having a trochoidal tooth profile was shown as the rotor unit exerting a pumping action, but it is not limited to this.
  • a rotor unit having an inner rotor and an outer rotor with an involute tooth profile, or an inner rotor and an outer rotor with other tooth profile, or the like may be employed.
  • a rotor unit including a vane type rotor or other positive displacement rotor may be employed.
  • the inner rotor 40 and the outer rotor 50 constituting the rotor unit Ru are shown to be composed of four trochoidal lobes and five nodes. may be adopted.
  • the cylinder block CB of an internal combustion engine mounted on an automobile or the like is shown as an object to which the pump device M according to the present invention is applied. It may be applied to lubricated equipment, and may be applied to fluid equipment that uses fluid other than hydraulic oil.
  • the pump device of the present invention can achieve thinness and miniaturization while ensuring mechanical strength. It can be applied not only to objects, but also to other lubricating devices, and is also useful in fluid devices that handle fluids other than hydraulic oil.

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

Abstract

Un dispositif pompe selon la présente invention comprend : une unité rotor (Ru) qui fournit un effet de pompage à du fluide ; un boîtier (H) permettant de délimiter un orifice d'aspiration (15), un orifice de refoulement (16), et une chambre de stockage (13) qui stocke l'unité rotor ; et un arbre rotatif (30) qui est combiné à l'unité rotor et dépasse à l'extérieur du boîtier et qui tourne par rapport à une ligne axiale prédéterminée (S). Le boîtier (H) comprend : un corps de boîtier cylindrique à fond (10) formé d'un seul tenant avec une paroi de jonction (11) qui est jointe à un objet à appliquer, une paroi périphérique extérieure (12) qui délimite la chambre de stockage en coopération avec la paroi de jonction, et une partie d'assemblage à emboîtement (14) qui dépasse de la paroi de jonction dans la direction de la ligne axiale et qui est adaptée à l'objet à appliquer ; et un couvercle de boîtier de type plaque (20) qui est combiné avec le corps de boîtier afin de fermer la chambre de stockage. Par conséquent, il est possible d'obtenir un amincissement et une réduction de taille tout en assurant la résistance mécanique.
PCT/JP2022/003925 2021-04-13 2022-02-02 Dispositif pompe WO2022219886A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18/274,207 US20240084799A1 (en) 2021-04-13 2022-02-02 Pump device
CN202280011123.8A CN116745528A (zh) 2021-04-13 2022-02-02 泵装置
DE112022002136.5T DE112022002136T5 (de) 2021-04-13 2022-02-02 Pumpvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021067626A JP2022162691A (ja) 2021-04-13 2021-04-13 ポンプ装置
JP2021-067626 2021-04-13

Publications (1)

Publication Number Publication Date
WO2022219886A1 true WO2022219886A1 (fr) 2022-10-20

Family

ID=83639553

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Application Number Title Priority Date Filing Date
PCT/JP2022/003925 WO2022219886A1 (fr) 2021-04-13 2022-02-02 Dispositif pompe

Country Status (5)

Country Link
US (1) US20240084799A1 (fr)
JP (1) JP2022162691A (fr)
CN (1) CN116745528A (fr)
DE (1) DE112022002136T5 (fr)
WO (1) WO2022219886A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001182669A (ja) * 1999-12-27 2001-07-06 Mikuni Adec Corp トロコイドポンプ
JP2018127978A (ja) * 2017-02-09 2018-08-16 アイシン精機株式会社 電動ポンプ
JP2019027432A (ja) * 2017-07-31 2019-02-21 日本電産トーソク株式会社 電動オイルポンプ
WO2019225425A1 (fr) * 2018-05-21 2019-11-28 Ntn株式会社 Pompe à huile électrique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6511730B2 (ja) * 2014-05-23 2019-05-15 株式会社ジェイテクト ポンプ
JP6649906B2 (ja) 2017-01-17 2020-02-19 株式会社オティックス オイルポンプ
US20190032657A1 (en) * 2017-07-31 2019-01-31 Nidec Tosok Corporation Electric oil pump
JP7144652B2 (ja) 2019-03-26 2022-09-30 豊田合成株式会社 オイルポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001182669A (ja) * 1999-12-27 2001-07-06 Mikuni Adec Corp トロコイドポンプ
JP2018127978A (ja) * 2017-02-09 2018-08-16 アイシン精機株式会社 電動ポンプ
JP2019027432A (ja) * 2017-07-31 2019-02-21 日本電産トーソク株式会社 電動オイルポンプ
WO2019225425A1 (fr) * 2018-05-21 2019-11-28 Ntn株式会社 Pompe à huile électrique

Also Published As

Publication number Publication date
CN116745528A (zh) 2023-09-12
JP2022162691A (ja) 2022-10-25
US20240084799A1 (en) 2024-03-14
DE112022002136T5 (de) 2024-04-11

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