WO2021130858A1 - Rotary pump - Google Patents
Rotary pump Download PDFInfo
- Publication number
- WO2021130858A1 WO2021130858A1 PCT/JP2019/050625 JP2019050625W WO2021130858A1 WO 2021130858 A1 WO2021130858 A1 WO 2021130858A1 JP 2019050625 W JP2019050625 W JP 2019050625W WO 2021130858 A1 WO2021130858 A1 WO 2021130858A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- cover
- sliding guide
- pump
- flat
- Prior art date
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Classifications
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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
- F04C2/08—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
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
- F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0088—Lubrication
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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
- F04C2/08—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
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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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
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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
- F04C2230/00—Manufacture
- F04C2230/10—Manufacture by removing material
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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
- F04C2230/00—Manufacture
- F04C2230/90—Improving properties of machine parts
- F04C2230/91—Coating
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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
- F04C2240/00—Components
- F04C2240/20—Rotors
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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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
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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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/802—Liners
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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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/805—Fastening means, e.g. bolts
Definitions
- This disclosure relates to a rotary pump.
- a rotary pump described in Patent Document 1 is known as a rotary pump that sucks and discharges a fluid by rotating a pump rotor.
- the rotary pump of Patent Document 1 has a pump rotor and a housing that rotatably accommodates the pump rotor.
- a clearance is set between the housing and the sliding surface of the pump rotor to allow the pump rotor to rotate. If this clearance is large, the amount of fluid leakage increases and the discharge amount of the pump decreases. Therefore, it is preferable that the clearance between the housing and the sliding surface of the pump rotor is small. However, if this clearance is made too small, there is a problem that seizure easily occurs between the housing and the pump rotor. Therefore, the clearance between the housing and the sliding surface of the pump rotor is usually set to a size of several tens of ⁇ m or more.
- the rotary pump of Patent Document 2 has a pump rotor and a housing for rotatably accommodating the pump rotor, and one or both of the housing and the pump rotor are coated with a crosslinked fluororesin. Since the crosslinked fluororesin has the characteristics of low friction coefficient and high wear resistance, when one or both of the housing and the pump rotor are coated with the crosslinked fluororesin, the sliding surface between the housing and the pump rotor is coated. Even when the clearance is set extremely small, seizure between the housing and the pump rotor can be prevented for a long period of time.
- the rotary pump is A pump rotor with a flat rotor side facing the axis, It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane.
- the housing body to be accommodated and A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
- the cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
- the metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
- the crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface. It is a rotary pump.
- FIG. 1 is an exploded perspective view of the rotary pump according to the first embodiment of the present disclosure.
- FIG. 2 is a front view of the rotary pump of FIG.
- FIG. 3 is a cross-sectional view taken along the line III-III of FIG.
- FIG. 4 is a cross-sectional view taken along the line IV-IV of FIG.
- FIG. 5 is an enlarged view of the vicinity of the pump rotor of FIG.
- FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG.
- FIG. 7 is an explanatory view of the manufacturing process of the side cover shown in FIG.
- FIG. 8 is an exploded perspective view of the rotary pump according to the second embodiment of the present disclosure.
- FIG. 9 is an enlarged cross-sectional view showing the rotary pump of FIG.
- FIG. 10 is an exploded perspective view of the rotary pump according to the third embodiment of the present disclosure.
- FIG. 11 is an enlarged cross-sectional view showing the rotary pump of FIG. 10 corresponding to FIG.
- FIG. 12 is a diagram showing a rotary pump according to a fourth embodiment of the present disclosure corresponding to FIG.
- FIG. 13 is a cross-sectional view taken along the line XIII-XIII of FIG.
- FIG. 14 is an enlarged view of the vicinity of the pump rotor of FIG.
- Patent Document 2 the inventors of the present application have in-house developed a rotary pump in which at least one of the housing and the pump rotor is coated with a crosslinked fluororesin, and as such a rotary pump, the housing is crosslinked with fluoropolymer. We considered mass-producing resin-coated products.
- the housing is composed of a housing body and a cover member fixed to the housing body with bolts.
- the housing body has an axial opening and a flat flange surface formed around the opening, in which the pump rotor is rotatably housed.
- the cover member is a flat mating surface that is fixed by pressing it against the flange surface around the opening of the housing body by tightening bolts, and a flat slide that slides and guides the flat axial side surface (rotor side surface) of the pump rotor. It has a dynamic guide surface.
- the mating surface and the sliding guide surface are continuous flat surfaces.
- the inventors crosslink one surface of the metal cover member (that is, a continuous flat surface including a mating surface with the housing body and a sliding guide surface for sliding guide the rotor side surface of the pump rotor).
- a prototype coated with a resin film was manufactured in-house, and the cover member of the prototype was fixed to the housing body containing the pump rotor with bolts, and when the pump performance was evaluated, the pump rotor was driven to rotate. It was found that the torque for this may be larger than expected.
- the cover member when the cover member is fixed to the housing body with a bolt, the tightening force of the bolt compresses and deforms the crosslinked fluororesin film provided on the mating surface of the cover member with the housing body.
- the thickness of the crosslinked fluororesin film is reduced by about 1 ⁇ m to about 10 ⁇ m, and the position of the sliding guide surface of the cover member is slightly displaced in the axial direction by that amount.
- the axial clearance between the cover member and the pump rotor is slightly smaller than the design value, and the pump rotor is rotationally driven, especially when the clearance size is set to an extremely small size of 20 ⁇ m or less. It was found that the torque for the pump tends to be larger than expected.
- the rotary pump according to one aspect of the present disclosure is A pump rotor with a flat rotor side facing the axis, It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane.
- the housing body to be accommodated and A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
- the cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
- the metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
- the crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface. It is a rotary pump.
- the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin, even when the clearance between the cover member and the pump rotor is set to be extremely small, the cover member and the pump rotor It is possible to prevent seizure during a long period of time. Since the mating surface of the cover member to the housing body is provided on the metal body constituting the cover member, the tightening force of the bolt can be supported by the metal body portion with rigidity, and the cover member slides. It is possible to prevent the position of the guide surface from being displaced in the axial direction due to the tightening force of the bolt.
- the cover member when the cover member is bolted to the housing body, it is possible to accurately manage the axial clearance between the cover member and the pump rotor.
- the cover member adopts a flat plate-shaped side cover that is sandwiched and fixed between the housing body and the cover body arranged so as to face the flange surface of the housing body.
- the rotary pump according to one aspect of the present disclosure can be obtained by additionally incorporating a flat plate-shaped side cover between the housing body and the cover member of the existing rotary pump.
- the recess also includes a region corresponding to a part of the mating surface so that the crosslinked fluororesin filled in the recess contacts the flange surface in a continuous annular region around the opening.
- the mating surface and the sliding guide surface can be a continuous finished surface having a surface roughness of 10-point average roughness Rz JIS 6.3 ⁇ m or less.
- the pump rotor has an inner rotor having a plurality of outer teeth on the outer circumference and a plurality of inner teeth rotatably supported around a position eccentric from the center of the inner rotor and meshing with the outer teeth. It can be configured with an annular outer rotor.
- the pump rotor can be composed of a rotor body having a plurality of vane accommodating grooves on the outer periphery and a plurality of vanes accommodated in the plurality of vane accommodating grooves so as to be slidable in the radial direction.
- the rotary pump includes a pump rotor 2 that is rotationally driven by a rotary shaft 1, a housing body 3 that houses the pump rotor 2, and a first cover body 4a and a first cover body 4a that are arranged on one side of the housing body 3 in the axial direction.
- the side cover 5a and the second cover main body 4b and the second side cover 5b arranged on the other side in the axial direction of the housing main body 3 are provided.
- the pump rotor 2 is an inner rotor 7 having a plurality of outer teeth 6 on the outer circumference and an annular outer rotor 9 having a plurality of inner teeth 8 meshing with the outer teeth 6 on the inner circumference. It is configured.
- the inner rotor 7 and the outer rotor 9 are rotatably housed in the axial opening 10 formed in the housing body 3.
- the inner rotor 7 is formed with a shaft hole 11 into which the rotating shaft 1 is inserted.
- the rotating shaft 1 and the shaft hole 11 are fitted so that the rotating shaft 1 and the inner rotor 7 rotate integrally.
- the fitting of the rotating shaft 1 and the shaft hole 11 includes a two-sided width fitting as shown in the figure, a spline fitting, a keyway fitting, and a fitting with a tightening allowance between cylindrical surfaces (hard fitting and fitting). Fitting by press fitting) may be adopted.
- the outer rotor 9 has an outer peripheral cylindrical surface 12.
- the outer peripheral cylindrical surface 12 is fitted to the inner circumference of the opening 10 of the housing body 3 with a gap, and the outer rotor 9 is rotatably supported by the fitting.
- the outer rotor 9 is rotatably supported around a position eccentric from the center position of the inner rotor 7 (that is, the rotation center position of the rotation shaft 1).
- the outer rotor 9 rotates together with the inner rotor 7 due to the meshing of the inner teeth 8 and the outer teeth 6.
- the rotation direction of the inner rotor 7 is clockwise in the figure.
- the number of internal teeth 8 of the outer rotor 9 is one more than the number of external teeth 6 of the inner rotor 7.
- a plurality of chambers 13 spaces for accommodating fluids partitioned by the outer teeth 6 and the inner teeth 8 are formed between the outer circumference of the inner rotor 7 and the inner circumference of the outer rotor 9.
- the plurality of chambers 13 are configured so that their volumes change as the inner rotor 7 and the outer rotor 9 rotate. That is, the volume of the chamber 13 is maximized at the angle position where the center of the inner rotor 7 and the center of the outer rotor 9 are farthest (upper position in the figure), and the center of the inner rotor 7 and the center of the outer rotor 9 are closest to each other.
- the volume of the chamber 13 is reduced to discharge the fluid, while the inner rotor 7 is located at the closest angle between the center of the inner rotor 7 and the center of the outer rotor 9.
- the volume of the chamber 13 gradually increases, so that a fluid suction action occurs.
- the inner rotor 7 has a flat first inner rotor side surface 14a facing one side in the axial direction (left side in the figure) and a flat first inner rotor 7 facing the other side in the axial direction (right side in the figure). It has 2 inner rotor side surfaces 14b.
- the first inner rotor side surface 14a and the second inner rotor side surface 14b are parallel planes facing opposite to each other in the axial direction.
- the outer rotor 9 has a flat first outer rotor side surface 15a facing one side in the axial direction and a flat second outer rotor side surface 15b facing the other side in the axial direction.
- the first outer rotor side surface 15a and the second outer rotor side surface 15b are parallel planes facing opposite to each other in the axial direction.
- the axial width dimension of the inner rotor 7 from the first inner rotor side surface 14a to the second inner rotor side surface 14b is the outer rotor 9 from the first outer rotor side surface 15a to the second outer rotor side surface 15b. It is the same as the axial width dimension of.
- the first inner rotor side surface 14a and the first outer rotor side surface 15a are located on the same plane, and the second inner rotor side surface 14b and the second outer rotor side surface 15b are also located on the same plane.
- Both the inner rotor 7 and the outer rotor 9 are sintered bodies.
- the sintered body is a member obtained by heating a powder molded body obtained by compression molding an iron-based powder material with a mold at a high temperature below the melting point.
- the shaft hole 11 into which the rotating shaft 1 is inserted is a through hole that penetrates the inner rotor 7 in the axial direction.
- the rotating shaft 1 has a portion protruding from the inner rotor 7 on one side in the axial direction (left side in the drawing) and a portion protruding from the inner rotor 7 on the other side in the axial direction (right side in the drawing). It is inserted in the hole 11.
- the portion of the rotating shaft 1 protruding from the inner rotor 7 to one side in the axial direction is rotatably supported by the first bearing 16a attached to the first cover body 4a, and is rotatably supported from the inner rotor 7 of the rotating shaft 1.
- the portion protruding to the other side in the direction is rotatably supported by a second bearing 16b attached to the second cover body 4b.
- a portion of the rotating shaft 1 protruding from the inner rotor 7 to the other side in the axial direction is connected to a rotary driving device (electric motor or the like) (not shown).
- the first cover body 4a, the first side cover 5a, the housing body 3, the second side cover 5b, and the second cover body 4b are formed in the bolt insertion holes 17 formed in each member.
- a common bolt 18 is inserted and tightened in the axial direction with the bolt 18 to fix each other.
- the first cover body 4a, the first side cover 5a, the housing body 3, the second side cover 5b, and the second cover body 4b have knock pins 20 common to the knock pin insertion holes 19 formed in the respective members. By inserting it, it is positioned in the direction perpendicular to the axis.
- the housing body 3 has an opening 10 that opens to one side (left side in the drawing) and the other side (right side in the figure) in the axial direction, and a flat first flange formed around one side in the axial direction of the opening 10. It has a surface 21a and a flat second flange surface 21b formed around the other side of the opening 10 in the axial direction.
- the first flange surface 21a and the second flange surface 21b are parallel planes facing opposite to each other in the axial direction.
- the first cover body 4a is arranged so as to face the first flange surface 21a of the housing body 3, and the first side cover 5a is sandwiched between the first cover body 4a and the housing body 3. .
- the second cover body 4b is also arranged so as to face the second flange surface 21b of the housing body 3, and the second side cover 5b is sandwiched between the second cover body 4b and the housing body 3. ..
- the first flange surface 21a is aligned with the first inner rotor side surface 14a and the first outer rotor side surface 15a. Further, the second flange surface 21b is aligned with the second inner rotor side surface 14b and the second outer rotor side surface 15b on the same plane.
- the axial width dimension of the inner rotor 7 and the outer rotor 9 is slightly smaller than the axial width dimension of the housing body 3, and the difference is set to 20 ⁇ m or less (preferably 15 ⁇ m or less, more preferably 10 ⁇ m or less). Has been done.
- the first side cover 5a and the second side cover 5b have a symmetrical configuration with the housing body 3 in between. Therefore, the first side cover 5a will be described, and the description of the second side cover 5b will be omitted by adding the same code or a code in which the last alphabet a is replaced with b in the corresponding portion.
- the first side cover 5a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening a bolt 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance.
- the first side cover 5a is a flat plate-like member having a uniform thickness of 5 mm or less (preferably 4 mm or less).
- the first side cover 5a is formed of a crosslinked fluororesin 24 and a metal body 25.
- a steel material or an aluminum alloy can be adopted.
- the metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22.
- the recess 26 is a flat recess having a constant depth over the entire area. The depth of the recess 26 can be set to 0.5 mm or less (preferably 0.3 mm or less, more preferably 0.2 mm or less).
- the recess 26 has a contour that includes the contour of the opening 10 of the housing body 3 inside (in the figure, a circular contour having a diameter larger than the circle forming the contour of the opening 10).
- the recess 26 is filled with a crosslinked fluororesin 24, and the crosslinked fluororesin 24 forms a sliding guide surface 23 on the same plane as the mating surface 22.
- the mating surface 22 and the sliding guide surface 23 are continuous finished surfaces having a surface roughness of 10-point average roughness Rz JIS 6.3 ⁇ m or less (preferably Rz JIS 3.2 ⁇ m or less).
- Ten-point average roughness is a parameter specified. That is, the ten-point average roughness Rz JIS extracts only the reference length from the roughness curve in the direction of the average line, and in this extracted portion, the average of the mountain heights from the highest mountain peak to the fifth mountain height and the highest. It is the sum of the average of the valley depths from the deepest valley bottom to the fifth in the deepest order.
- the crosslinked fluororesin 24 is obtained by cross-linking between the molecules of the chain polymer constituting the fluororesin, and has a low friction coefficient equivalent to that of a general fluororesin (non-crosslinked fluororesin), but is generally used. It has extremely high wear resistance compared to fluororesin.
- PTFE polytetrafluoroethylene
- FEP tetrafluoroethylene-hexafluoropropylene copolymer
- PFA tetrafluoroethylene-perfluoroalkyl vinyl ether copolymer
- the crosslinked PTFE has a particularly low coefficient of friction among the above-mentioned fluororesins and is excellent in wear resistance, so that the crosslinked PTFE hardly wears and the pump efficiency can be effectively improved.
- the first side cover 5a can be formed, for example, as follows.
- a recess 26 is formed on the surface of a plate-shaped metal body 25 having a constant thickness.
- a film of the crosslinked fluororesin 24 is formed on the surface of the metal body 25 on the side of the recess 26.
- the recess 26 is filled with the crosslinked fluororesin 24, and the periphery of the recess 26 is also covered with the crosslinked fluororesin 24.
- the crosslinked fluororesin 24 is ground until the metal around the recess 26 is exposed, and further, the metal around the recess 26 and the crosslinked fluororesin 24 in the recess 26 are ground.
- the surface of the metal around the recess 26 corresponds to the mating surface 22, and the surface of the crosslinked fluororesin 24 in the recess 26 corresponds to the sliding guide surface 23.
- the mating surface 22 and the sliding guide surface 23 formed in this way form a continuous finished surface having the same surface roughness.
- the film of the crosslinked fluororesin 24 shown in the middle figure of FIG. 7 can be formed, for example, as follows. First, a dispersion liquid in which fine particles of fluororesin (for example, PTFE) are dispersed in water is applied to the surface of the metal body 25 on the side of the recess 26. Next, the applied dispersion liquid is dried to form a layer of fine particle particles of fluororesin on the surface of the metal body 25 on the side of the recess 26. Subsequently, by heating the metal body 25 and the layer of the fluororesin fine particles to a temperature equal to or higher than the melting point of the fluororesin, the fluororesin fine particles are fired and the fluororesin fine particles are fused to each other.
- a dispersion liquid in which fine particles of fluororesin for example, PTFE
- the applied dispersion liquid is dried to form a layer of fine particle particles of fluororesin on the surface of the metal body 25 on the side of the recess 26.
- the radiation irradiated at this time also causes a chemical bond between the molecule of the chain polymer constituting the fluororesin and the surface of the metal body 25, and the chemical bond causes the film of the crosslinked fluororesin 24 to be formed. It adheres to the metal body 25 with extremely high adhesion. In this way, the film of the crosslinked fluororesin 24 shown in the middle figure of FIG. 7 can be formed.
- radiation for example, an electron beam
- the first side cover 5a includes a first suction port 30a that opens on a surface facing the first inner rotor side surface 14a and the first outer rotor side surface 15a, and a first suction port.
- a first discharge port 31a that opens from the port 30a at intervals in the circumferential direction is provided.
- the second side cover 5b has a second suction port 30b that opens on a surface facing the second inner rotor side surface 14b and the second outer rotor side surface 15b, and a circumference from the second suction port 30b.
- a second discharge port 31b that opens at intervals in the direction is provided.
- both the first suction port 30a and the first discharge port 31a are opened in an arc shape centered on the rotation shaft 1.
- both the second suction port 30b and the second discharge port 31b are opened in an arc shape centered on the rotation shaft 1.
- the first suction port 30a and the second suction port 30b are opened at symmetrical positions with the inner rotor 7 and the outer rotor 9 sandwiched between them in the same shape.
- the pressure received by the second outer rotor side surface 15b is balanced, and the inner rotor 7 and the outer rotor 9 are prevented from being tilted.
- first discharge port 31a and the second discharge port 31b are also opened at symmetrical positions with the inner rotor 7 and the outer rotor 9 sandwiched between them in the same shape.
- the pressure received by the rotor side surface 14b and the second outer rotor side surface 15b is balanced to prevent the inner rotor 7 and the outer rotor 9 from being tilted.
- the first suction port 30a and the second suction port 30b pass through a communication passage 32 formed at a position separated from the opening 10 accommodating the pump rotor 2 of the housing body 3. Communicate with each other. Further, as shown in FIGS. 2 and 6, the first suction port 30a communicates with the suction port 33 opening on the outer surface of the first cover body 4a, and the first discharge port 31a is the first cover. It communicates with the discharge port 34 that opens on the outer surface of the main body 4a.
- the first side cover 5a and the second side cover 5b is formed of the crosslinked fluororesin 24, the first side cover 5a And the clearance between the second side cover 5b and the pump rotor 2 (that is, the inner width dimension between the sliding guide surface 23 of the first side cover 5a and the sliding guide surface 23 of the second side cover 5b). And the first side even when the size (difference from the axial width dimension of the inner rotor 7 or the outer rotor 9) is set to an extremely small size (20 ⁇ m or less, preferably 15 ⁇ m or less, more preferably 10 ⁇ m or less). It is possible to prevent seizure between the cover 5a and the second side cover 5b and the pump rotor 2 for a long period of time.
- the first side cover 5a and the second side cover 5b shown in FIG. 5 are attached to the entire one surface of the metal body 25 (that is, the sliding guide surface between the mating surface 22 to the housing body 3 and the pump rotor 2).
- the side cover is attached to the housing body 3 with a bolt 18.
- the tightening force of the bolt 18 compresses and deforms the cross-linked fluororesin film provided on the mating surface 22 of the side cover to the housing body 3, and the compressive deformation causes the thickness of the cross-linked fluororesin film.
- a crosslinked fluororesin film having a thickness of 50 ⁇ m becomes thinner by about 1.6 ⁇ m due to compressive deformation due to the tightening force of the bolts 18 and becomes 150 ⁇ m.
- a film of crosslinked fluororesin having a thickness of about 4.8 ⁇ m is thin, and a film of crosslinked fluororesin with a thickness of 250 ⁇ m is thinned by about 8.0 ⁇ m.
- the axial clearance between the side cover and the pump rotor 2 becomes slightly smaller than the design value, and especially when the clearance size is set to an extremely small size of 20 ⁇ m or less, the pump rotor 2 is operated. There is a problem that the torque for rotationally driving becomes larger than expected.
- the mating surfaces 22 of the first side cover 5a and the second side cover 5b to the housing body 3 have the first side cover 5a and the second side cover 5a and the second side cover 5a. Since it is provided on the metal body 25 constituting the side cover 5b, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the first side cover 5a and the second side cover 5b can be supported. It is possible to prevent the position of the sliding guide surface 23 from being displaced in the axial direction due to the tightening force of the bolt 18.
- this rotary pump can obtain the rotary pump of the embodiment by adding the first side cover 5a and the second side cover 5b to the existing rotary pump, and is low cost.
- the recess 26 filled with the crosslinked fluororesin 24 is provided not in the first cover body 4a to which the first bearing 16a is attached, but in a metal body 25 separate from the first cover body 4a. Therefore, rather than providing the recess 26 for directly filling the crosslinked fluororesin 24 on the surface of the first cover body 4a and filling the crosslinked fluororesin 24, the recess 26 is processed and the crosslinked fluororesin 24 is filled. Is easy. Similarly, since the recess 26 filled with the crosslinked fluororesin 24 is provided not in the second cover body 4b to which the second bearing 16b is attached, but in the metal body 25 separate from the second cover body 4b.
- the mating surface 22 and the sliding guide surface 23 are finished at the same time, so that the mating surface 22 and the sliding guide surface 23 are made to have a ten-point average roughness Rz JIS 6.3 ⁇ m or less (preferably Rz). Since it is a continuous finished surface with a surface roughness of JIS 3.2 ⁇ m or less), the cost is low.
- the surface roughness of the mating surface 22 and the sliding guide surface 23 is Rz JIS 6.3 ⁇ m or less (preferably Rz JIS 3.2 ⁇ m or less)
- the first side cover 5a, the second side cover 5b, and the pump rotor Clearance between 2 that is, the inner width dimension between the sliding guide surface 23 of the first side cover 5a and the sliding guide surface 23 of the second side cover 5b, and the inner rotor 7 or the outer rotor 9 It is possible to manage the difference from the width dimension in the axial direction) with extremely high accuracy.
- the first side cover 5a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening a bolt 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance.
- the metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22.
- the recess 26 is formed on the mating surface 22 so that the crosslinked fluororesin 24 filled in the recess 26 comes into contact with the first flange surface 21a in a continuous annular region around the opening 10 of the housing body 3.
- the second side cover 5b is also configured in the same manner as the first side cover 5a.
- the crosslinked fluororesin 24 filled in the recess 26 contacts the first flange surface 21a and the second flange surface 21b in an annular region that is continuous without interruption around the opening 10 of the housing body 3. Therefore, it is possible to seal the contact surfaces between the first side cover 5a and the second side cover 5b and the housing body 3 with the crosslinked fluororesin 24 to prevent fluid leakage. Moreover, since the crosslinked fluororesin 24 constituting the mating surface 22 is continuous with the crosslinked fluororesin 24 forming the sliding guide surface 23, the manufacturing cost can be kept low.
- the rotary pump includes a pump rotor 2 that is rotationally driven by a rotary shaft 1, a housing body 3 that houses the pump rotor 2, and a first cover that is arranged on one side (left side in the figure) of the housing body 3 in the axial direction. It has a main body 4a and a second cover main body 4b arranged on the other side (right side in the drawing) of the housing main body 3 in the axial direction.
- a common bolt 18 is inserted into a bolt insertion hole 17 formed in each member, and the bolt 18 is used in the axial direction. They are fixed to each other by tightening. Further, the first cover body 4a, the housing body 3, and the second cover body 4b are positioned in the direction perpendicular to the axis by inserting a common knock pin 20 into the knock pin insertion holes 19 formed in each member.
- the first cover body 4a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening bolts 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance.
- the first cover body 4a is formed of a crosslinked fluororesin 24 and a metal body 25.
- a steel material or an aluminum alloy can be adopted as the material of the metal body 25.
- the metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22.
- the recess 26 is filled with a crosslinked fluororesin 24, and the crosslinked fluororesin 24 forms a sliding guide surface 23 on the same plane as the mating surface 22.
- the second cover body 4b is also configured in the same manner as the first cover body 4a.
- the sliding guide surface 23 of the first cover body 4a and the second cover body 4b is formed of the crosslinked fluororesin 24, so that the first cover body 4a And the clearance between the second cover body 4b and the pump rotor 2 (that is, the inner width dimension between the sliding guide surface 23 of the first cover body 4a and the sliding guide surface 23 of the second cover body 4b).
- the first cover main body It is possible to prevent seizure between the 4a and the second cover body 4b and the pump rotor 2 for a long period of time.
- the mating surface 22 of the first cover body 4a and the second cover body 4b to the housing body 3 constitutes the first cover body 4a and the second cover body 4b. Since it is provided in, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the position of the sliding guide surface 23 of the first cover body 4a and the second cover body 4b is the bolt. The tightening force of 18 can prevent the displacement in the axial direction. Therefore, when the first cover body 4a and the second cover body 4b are fixed to the housing body 3 with bolts 18, the axial direction between the first cover body 4a and the second cover body 4b and the pump rotor 2 It is possible to manage the clearance of the housing accurately.
- the pump rotor 2 has a rotor main body 36 having a plurality of vane accommodating grooves 35 on the outer periphery, and a plurality of vanes slidably accommodated in the plurality of vane accommodating grooves 35, respectively. It is composed of 37.
- the radial outer end of the vane 37 is in sliding contact with the inner circumference of the cam ring 38 provided in the housing body 3.
- an opening 10 for rotatably accommodating the pump rotor 2 is formed inside the cam ring 38.
- a plurality of chambers 39 (spaces for accommodating fluids) partitioned by vanes 37 are formed between the outer circumference of the rotor body 36 and the inner circumference of the cam ring 38.
- the inner circumference of the cam ring 38 is configured so that the volume of each chamber 39 changes as the rotor body 36 rotates, and the fluid discharge action due to the volume reduction of the chamber 39 and the volume of the chamber 39 gradually increase. As a result, the inhalation action of the fluid occurs.
- the first side cover 5a has a flat mating surface 22 that is pressed and fixed to the first flange surface 21a by tightening a bolt 18 (see FIG. 12), a rotor body 36, and a vane. It has a flat sliding guide surface 23 that slides and guides a flat side surface of 37 that faces the axial direction.
- the second side cover 5b is also configured in the same manner as the first side cover 5a.
- the inner circumference of the cam ring 38 is coated with a crosslinked fluororesin film 40.
- the axial width dimension of the rotor body 36 is the same as the axial width dimension of the vane 37.
- the first side cover 5a It is possible to prevent seizure between the second side cover 5b and the pump rotor 2 for a long period of time.
- the mating surface 22 of the first side cover 5a and the second side cover 5b with respect to the housing body 3 constitutes the first side cover 5a and the second side cover 5b. Since it is provided in, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the position of the sliding guide surface 23 of the first side cover 5a and the second side cover 5b is the bolt. The tightening force of 18 can prevent the displacement in the axial direction. Therefore, when the first side cover 5a and the second side cover 5b are fixed to the housing body 3 with bolts 18, the shaft between the first side cover 5a and the second side cover 5b and the pump rotor 2 It is possible to accurately manage the clearance in the direction.
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Abstract
A rotary pump equipped with a pump rotor which has a flat lateral rotor surface facing the axial direction, also equipped with a housing main body which has an axial-direction opening and a flat flange surface formed around the opening, and rotatably houses the pump rotor in the opening in a manner such that the lateral rotor surface and the flange surface are aligned in the same plane, and also equipped with a cover member which has a flat contact surface pressed against and secured to the flange surface by being bolted thereto and a flat sliding guide surface which slides on and guides the lateral rotor surface, wherein the cover member is formed from a crosslinked fluorine resin and a metal body, the metal body is provided with the contact surface and a recess which recesses in the axial direction relative to the contact surface in a region which corresponds to the sliding guide surface, and the crosslinked fluorine resin fills the recess interior in a manner such that the sliding guide surface is formed in the same plane as is the contact surface.
Description
本開示は、回転ポンプに関する。
This disclosure relates to a rotary pump.
ポンプロータを回転させることで流体の吸入と吐出を行なう回転ポンプとして、特許文献1に記載のものが知られている。特許文献1の回転ポンプは、ポンプロータと、ポンプロータを回転可能に収容するハウジングとを有する。
A rotary pump described in Patent Document 1 is known as a rotary pump that sucks and discharges a fluid by rotating a pump rotor. The rotary pump of Patent Document 1 has a pump rotor and a housing that rotatably accommodates the pump rotor.
ハウジングとポンプロータの摺動面間には、一般に、ポンプロータの回転を許容するためのクリアランスが設定される。このクリアランスが大きいと、流体のリーク量が大きくなってポンプの吐出量が減少するため、ハウジングとポンプロータの摺動面間のクリアランスは小さい方が好ましい。しかしながら、このクリアランスを小さくしすぎると、ハウジングとポンプロータの間の焼き付きが生じやすくなるという問題がある。そのため、ハウジングとポンプロータの摺動面間のクリアランスは、通常、数十μm以上の大きさに設定される。
Generally, a clearance is set between the housing and the sliding surface of the pump rotor to allow the pump rotor to rotate. If this clearance is large, the amount of fluid leakage increases and the discharge amount of the pump decreases. Therefore, it is preferable that the clearance between the housing and the sliding surface of the pump rotor is small. However, if this clearance is made too small, there is a problem that seizure easily occurs between the housing and the pump rotor. Therefore, the clearance between the housing and the sliding surface of the pump rotor is usually set to a size of several tens of μm or more.
ここで、本願の出願人は、ハウジングとポンプロータの間の焼き付きを防止しながら、ハウジングとポンプロータの摺動面間のクリアランスをきわめて小さく設定することが可能な回転ポンプの開発を行ない、そのような回転ポンプとして、特許文献2のものを提案している。
Here, the applicant of the present application has developed a rotary pump capable of setting the clearance between the housing and the sliding surface of the pump rotor to be extremely small while preventing seizure between the housing and the pump rotor. As such a rotary pump, the one of Patent Document 2 is proposed.
特許文献2の回転ポンプは、ポンプロータと、ポンプロータを回転可能に収容するハウジングとを有し、ハウジングとポンプロータの一方または両方に架橋フッ素樹脂をコーティングしている。架橋フッ素樹脂は、摩擦係数が低く、かつ、耐摩耗性が高いという特性を有するため、ハウジングとポンプロータの一方または両方に、架橋フッ素樹脂をコーティングすると、ハウジングとポンプロータの摺動面間のクリアランスをきわめて小さく設定したときにも、ハウジングとポンプロータの間の焼き付きを長期にわたって防止することが可能となる。
The rotary pump of Patent Document 2 has a pump rotor and a housing for rotatably accommodating the pump rotor, and one or both of the housing and the pump rotor are coated with a crosslinked fluororesin. Since the crosslinked fluororesin has the characteristics of low friction coefficient and high wear resistance, when one or both of the housing and the pump rotor are coated with the crosslinked fluororesin, the sliding surface between the housing and the pump rotor is coated. Even when the clearance is set extremely small, seizure between the housing and the pump rotor can be prevented for a long period of time.
本開示の一態様に係る回転ポンプは、
軸方向を向く平らなロータ側面をもつポンプロータと、
軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、前記ロータ側面と前記フランジ面とが同一平面上に揃うように前記ポンプロータを前記開口内に回転可能に収容するハウジング本体と、
ボルトの締め付けにより前記フランジ面に押して付けて固定される平らな合わせ面と、前記ロータ側面を摺動案内する平らな摺動案内面とを有するカバー部材と、を備える回転ポンプであって、
前記カバー部材が、架橋フッ素樹脂と金属体とで形成され、
前記金属体には、前記合わせ面と、前記摺動案内面に対応する領域を前記合わせ面に対して軸方向に凹ませた凹部とが設けられ、
前記架橋フッ素樹脂は、前記合わせ面と同一平面上に前記摺動案内面を形成するように前記凹部内に充填して設けられている、
回転ポンプである。 The rotary pump according to one aspect of the present disclosure is
A pump rotor with a flat rotor side facing the axis,
It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane. The housing body to be accommodated and
A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
The cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
The metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
The crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface.
It is a rotary pump.
軸方向を向く平らなロータ側面をもつポンプロータと、
軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、前記ロータ側面と前記フランジ面とが同一平面上に揃うように前記ポンプロータを前記開口内に回転可能に収容するハウジング本体と、
ボルトの締め付けにより前記フランジ面に押して付けて固定される平らな合わせ面と、前記ロータ側面を摺動案内する平らな摺動案内面とを有するカバー部材と、を備える回転ポンプであって、
前記カバー部材が、架橋フッ素樹脂と金属体とで形成され、
前記金属体には、前記合わせ面と、前記摺動案内面に対応する領域を前記合わせ面に対して軸方向に凹ませた凹部とが設けられ、
前記架橋フッ素樹脂は、前記合わせ面と同一平面上に前記摺動案内面を形成するように前記凹部内に充填して設けられている、
回転ポンプである。 The rotary pump according to one aspect of the present disclosure is
A pump rotor with a flat rotor side facing the axis,
It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane. The housing body to be accommodated and
A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
The cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
The metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
The crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface.
It is a rotary pump.
[本開示が解決しようとする課題]
本願の発明者らは、特許文献2のように、ハウジングとポンプロータのうちの少なくとも一方に架橋フッ素樹脂をコーティングした回転ポンプの開発を社内で進め、そのような回転ポンプとして、ハウジングに架橋フッ素樹脂をコーティングしたものを量産化することを検討した。 [Issues to be solved by this disclosure]
As inPatent Document 2, the inventors of the present application have in-house developed a rotary pump in which at least one of the housing and the pump rotor is coated with a crosslinked fluororesin, and as such a rotary pump, the housing is crosslinked with fluoropolymer. We considered mass-producing resin-coated products.
本願の発明者らは、特許文献2のように、ハウジングとポンプロータのうちの少なくとも一方に架橋フッ素樹脂をコーティングした回転ポンプの開発を社内で進め、そのような回転ポンプとして、ハウジングに架橋フッ素樹脂をコーティングしたものを量産化することを検討した。 [Issues to be solved by this disclosure]
As in
ここで、ハウジングは、ハウジング本体と、ハウジング本体にボルトで固定されるカバー部材とで構成されている。ハウジング本体は、軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、その開口内にポンプロータを回転可能に収容している。カバー部材は、ボルトの締め付けによりハウジング本体の開口の周囲のフランジ面に押し付けて固定される平らな合わせ面と、ポンプロータの平らな軸方向の側面(ロータ側面)を摺動案内する平らな摺動案内面とを有する。合わせ面と摺動案内面は、一続きの平面である。
Here, the housing is composed of a housing body and a cover member fixed to the housing body with bolts. The housing body has an axial opening and a flat flange surface formed around the opening, in which the pump rotor is rotatably housed. The cover member is a flat mating surface that is fixed by pressing it against the flange surface around the opening of the housing body by tightening bolts, and a flat slide that slides and guides the flat axial side surface (rotor side surface) of the pump rotor. It has a dynamic guide surface. The mating surface and the sliding guide surface are continuous flat surfaces.
そして、発明者らは、金属製のカバー部材の片面(すなわち、ハウジング本体への合わせ面と、ポンプロータのロータ側面を摺動案内する摺動案内面とを含む一続きの平面)を架橋フッ素樹脂の皮膜でコーティングした試作品を社内で製作し、その試作品のカバー部材を、ポンプロータを収容したハウジング本体にボルトで固定し、ポンプ性能の評価を行なったところ、ポンプロータを回転駆動するためのトルクが想定よりも大きくなる場合があることが分かった。
Then, the inventors crosslink one surface of the metal cover member (that is, a continuous flat surface including a mating surface with the housing body and a sliding guide surface for sliding guide the rotor side surface of the pump rotor). A prototype coated with a resin film was manufactured in-house, and the cover member of the prototype was fixed to the housing body containing the pump rotor with bolts, and when the pump performance was evaluated, the pump rotor was driven to rotate. It was found that the torque for this may be larger than expected.
そこで、発明者らが、ポンプロータを回転駆動するためのトルクが想定よりも大きくなる原因を調査した結果、以下のことが分かった。すなわち、カバー部材をハウジング本体にボルトで固定するときに、そのボルトの締め付け力によって、カバー部材のハウジング本体への合わせ面に設けられた架橋フッ素樹脂の皮膜が圧縮変形し、その圧縮変形によって、架橋フッ素樹脂の皮膜の厚さが1μm前後~10μm前後小さくなり、その分、カバー部材の摺動案内面の位置が軸方向にわずかにずれる。その結果、カバー部材とポンプロータの間の軸方向のクリアランスが設計値よりもわずかに小さくなり、特に、クリアランスの大きさを20μm以下のきわめて小さい大きさに設定したときに、ポンプロータを回転駆動するためのトルクが、想定よりも大きくなりやすいことが分かった。
Therefore, as a result of the inventors investigating the cause of the torque for rotationally driving the pump rotor becoming larger than expected, the following was found. That is, when the cover member is fixed to the housing body with a bolt, the tightening force of the bolt compresses and deforms the crosslinked fluororesin film provided on the mating surface of the cover member with the housing body. The thickness of the crosslinked fluororesin film is reduced by about 1 μm to about 10 μm, and the position of the sliding guide surface of the cover member is slightly displaced in the axial direction by that amount. As a result, the axial clearance between the cover member and the pump rotor is slightly smaller than the design value, and the pump rotor is rotationally driven, especially when the clearance size is set to an extremely small size of 20 μm or less. It was found that the torque for the pump tends to be larger than expected.
そこで、カバー部材のポンプロータに対する摺動案内面を架橋フッ素樹脂で形成し、そのカバー部材をハウジング本体にボルトで固定したときに、カバー部材とポンプロータの間の軸方向のクリアランスを精度よく管理することが可能な回転ポンプを提供することを目的とする。
Therefore, when the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin and the cover member is fixed to the housing body with bolts, the axial clearance between the cover member and the pump rotor is accurately controlled. It is an object of the present invention to provide a rotary pump capable of providing a rotary pump.
[本開示の効果]
本開示によれば、カバー部材のポンプロータに対する摺動案内面を架橋フッ素樹脂で形成し、そのカバー部材をハウジング本体にボルトで固定したときに、カバー部材とポンプロータの間の軸方向のクリアランスを精度よく管理することが可能となる。 [Effect of the present disclosure]
According to the present disclosure, when the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin and the cover member is bolted to the housing body, the axial clearance between the cover member and the pump rotor Can be managed accurately.
本開示によれば、カバー部材のポンプロータに対する摺動案内面を架橋フッ素樹脂で形成し、そのカバー部材をハウジング本体にボルトで固定したときに、カバー部材とポンプロータの間の軸方向のクリアランスを精度よく管理することが可能となる。 [Effect of the present disclosure]
According to the present disclosure, when the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin and the cover member is bolted to the housing body, the axial clearance between the cover member and the pump rotor Can be managed accurately.
[本開示の実施形態の説明]
(1)本開示の一態様に係る回転ポンプは、
軸方向を向く平らなロータ側面をもつポンプロータと、
軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、前記ロータ側面と前記フランジ面とが同一平面上に揃うように前記ポンプロータを前記開口内に回転可能に収容するハウジング本体と、
ボルトの締め付けにより前記フランジ面に押して付けて固定される平らな合わせ面と、前記ロータ側面を摺動案内する平らな摺動案内面とを有するカバー部材と、を備える回転ポンプであって、
前記カバー部材が、架橋フッ素樹脂と金属体とで形成され、
前記金属体には、前記合わせ面と、前記摺動案内面に対応する領域を前記合わせ面に対して軸方向に凹ませた凹部とが設けられ、
前記架橋フッ素樹脂は、前記合わせ面と同一平面上に前記摺動案内面を形成するように前記凹部内に充填して設けられている、
回転ポンプである。
このようにすると、カバー部材のポンプロータに対する摺動案内面が、架橋フッ素樹脂で形成されているので、カバー部材とポンプロータの間のクリアランスをきわめて小さく設定したときにも、カバー部材とポンプロータの間の焼き付きを長期にわたって防止することが可能となる。そして、カバー部材のハウジング本体への合わせ面が、カバー部材を構成する金属体に設けられているので、ボルトの締め付け力を金属体の部分で剛性をもって支持することができ、カバー部材の摺動案内面の位置がボルトの締め付け力で軸方向にずれるのを防止することができる。そのため、カバー部材をハウジング本体にボルトで固定したときに、カバー部材とポンプロータの間の軸方向のクリアランスを精度よく管理することが可能である。
(2)前記カバー部材は、前記ハウジング本体と、前記ハウジング本体の前記フランジ面と対向して配置されるカバー本体との間に挟み込んで固定される平板状のサイドカバーを採用すると好ましい。
このようにすると、既存の回転ポンプのハウジング本体とカバー部材の間に、平板状のサイドカバーを追加して組み込むことで、本開示の一態様に係る回転ポンプを得ることが可能となる。
(3)前記凹部は、凹部に充填された架橋フッ素樹脂が前記開口の周囲を途切れずに連続する環状の領域で前記フランジ面に接触するように、前記合わせ面の一部に対応する領域も含めて軸方向に凹ませた形状をもつものを採用すると好ましい。
このようにすると、凹部に充填された架橋フッ素樹脂が、ハウジング本体の開口の周囲を途切れずに連続する環状の領域でフランジ面に接触するため、カバー部材とハウジング本体の接触面間を架橋フッ素樹脂でシールし、流体の漏れを防止することが可能となる。しかも、合わせ面を構成する架橋フッ素樹脂は、摺動案内面を構成する架橋フッ素樹脂と一続きであることから、製造コストが低く抑えられる。
(4)前記合わせ面と前記摺動案内面は、十点平均粗さRzJIS6.3μm以下の面粗さをもつ一続きの仕上げ面とすることができる。
このようにすると、合わせ面と摺動案内面を同時に仕上げ加工することができるので、低コストである。また、合わせ面と摺動案内面の面粗さがRzJIS6.3μm以下なので、カバー部材とポンプロータの間の軸方向のクリアランスをきわめて精度よく管理することが可能である。
(5)前記ポンプロータは、複数の外歯を外周にもつインナーロータと、前記インナーロータの中心から偏心した位置を中心に回転可能に支持され、前記外歯に噛み合う複数の内歯を内周にもつ環状のアウターロータとで構成することができる。
(6)前記ポンプロータは、複数のベーン収容溝を外周にもつロータ本体と、前記複数のベーン収容溝にそれぞれ径方向にスライド可能に収容された複数のベーンとで構成することができる。 [Explanation of Embodiments of the present disclosure]
(1) The rotary pump according to one aspect of the present disclosure is
A pump rotor with a flat rotor side facing the axis,
It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane. The housing body to be accommodated and
A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
The cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
The metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
The crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface.
It is a rotary pump.
In this way, since the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin, even when the clearance between the cover member and the pump rotor is set to be extremely small, the cover member and the pump rotor It is possible to prevent seizure during a long period of time. Since the mating surface of the cover member to the housing body is provided on the metal body constituting the cover member, the tightening force of the bolt can be supported by the metal body portion with rigidity, and the cover member slides. It is possible to prevent the position of the guide surface from being displaced in the axial direction due to the tightening force of the bolt. Therefore, when the cover member is bolted to the housing body, it is possible to accurately manage the axial clearance between the cover member and the pump rotor.
(2) It is preferable that the cover member adopts a flat plate-shaped side cover that is sandwiched and fixed between the housing body and the cover body arranged so as to face the flange surface of the housing body.
In this way, the rotary pump according to one aspect of the present disclosure can be obtained by additionally incorporating a flat plate-shaped side cover between the housing body and the cover member of the existing rotary pump.
(3) The recess also includes a region corresponding to a part of the mating surface so that the crosslinked fluororesin filled in the recess contacts the flange surface in a continuous annular region around the opening. It is preferable to use one having a shape recessed in the axial direction including the one.
In this way, the crosslinked fluororesin filled in the recesses comes into contact with the flange surface in a continuous annular region around the opening of the housing body, so that the crosslinked fluororesin between the cover member and the contact surface of the housing body is crosslinked. It is possible to prevent fluid leakage by sealing with resin. Moreover, since the crosslinked fluororesin constituting the mating surface is continuous with the crosslinked fluororesin constituting the sliding guide surface, the manufacturing cost can be kept low.
(4) The mating surface and the sliding guide surface can be a continuous finished surface having a surface roughness of 10-point average roughness Rz JIS 6.3 μm or less.
In this way, the mating surface and the sliding guide surface can be finished at the same time, so that the cost is low. Further, since the surface roughness of the mating surface and the sliding guide surface is Rz JIS 6.3 μm or less, it is possible to control the axial clearance between the cover member and the pump rotor with extremely high accuracy.
(5) The pump rotor has an inner rotor having a plurality of outer teeth on the outer circumference and a plurality of inner teeth rotatably supported around a position eccentric from the center of the inner rotor and meshing with the outer teeth. It can be configured with an annular outer rotor.
(6) The pump rotor can be composed of a rotor body having a plurality of vane accommodating grooves on the outer periphery and a plurality of vanes accommodated in the plurality of vane accommodating grooves so as to be slidable in the radial direction.
(1)本開示の一態様に係る回転ポンプは、
軸方向を向く平らなロータ側面をもつポンプロータと、
軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、前記ロータ側面と前記フランジ面とが同一平面上に揃うように前記ポンプロータを前記開口内に回転可能に収容するハウジング本体と、
ボルトの締め付けにより前記フランジ面に押して付けて固定される平らな合わせ面と、前記ロータ側面を摺動案内する平らな摺動案内面とを有するカバー部材と、を備える回転ポンプであって、
前記カバー部材が、架橋フッ素樹脂と金属体とで形成され、
前記金属体には、前記合わせ面と、前記摺動案内面に対応する領域を前記合わせ面に対して軸方向に凹ませた凹部とが設けられ、
前記架橋フッ素樹脂は、前記合わせ面と同一平面上に前記摺動案内面を形成するように前記凹部内に充填して設けられている、
回転ポンプである。
このようにすると、カバー部材のポンプロータに対する摺動案内面が、架橋フッ素樹脂で形成されているので、カバー部材とポンプロータの間のクリアランスをきわめて小さく設定したときにも、カバー部材とポンプロータの間の焼き付きを長期にわたって防止することが可能となる。そして、カバー部材のハウジング本体への合わせ面が、カバー部材を構成する金属体に設けられているので、ボルトの締め付け力を金属体の部分で剛性をもって支持することができ、カバー部材の摺動案内面の位置がボルトの締め付け力で軸方向にずれるのを防止することができる。そのため、カバー部材をハウジング本体にボルトで固定したときに、カバー部材とポンプロータの間の軸方向のクリアランスを精度よく管理することが可能である。
(2)前記カバー部材は、前記ハウジング本体と、前記ハウジング本体の前記フランジ面と対向して配置されるカバー本体との間に挟み込んで固定される平板状のサイドカバーを採用すると好ましい。
このようにすると、既存の回転ポンプのハウジング本体とカバー部材の間に、平板状のサイドカバーを追加して組み込むことで、本開示の一態様に係る回転ポンプを得ることが可能となる。
(3)前記凹部は、凹部に充填された架橋フッ素樹脂が前記開口の周囲を途切れずに連続する環状の領域で前記フランジ面に接触するように、前記合わせ面の一部に対応する領域も含めて軸方向に凹ませた形状をもつものを採用すると好ましい。
このようにすると、凹部に充填された架橋フッ素樹脂が、ハウジング本体の開口の周囲を途切れずに連続する環状の領域でフランジ面に接触するため、カバー部材とハウジング本体の接触面間を架橋フッ素樹脂でシールし、流体の漏れを防止することが可能となる。しかも、合わせ面を構成する架橋フッ素樹脂は、摺動案内面を構成する架橋フッ素樹脂と一続きであることから、製造コストが低く抑えられる。
(4)前記合わせ面と前記摺動案内面は、十点平均粗さRzJIS6.3μm以下の面粗さをもつ一続きの仕上げ面とすることができる。
このようにすると、合わせ面と摺動案内面を同時に仕上げ加工することができるので、低コストである。また、合わせ面と摺動案内面の面粗さがRzJIS6.3μm以下なので、カバー部材とポンプロータの間の軸方向のクリアランスをきわめて精度よく管理することが可能である。
(5)前記ポンプロータは、複数の外歯を外周にもつインナーロータと、前記インナーロータの中心から偏心した位置を中心に回転可能に支持され、前記外歯に噛み合う複数の内歯を内周にもつ環状のアウターロータとで構成することができる。
(6)前記ポンプロータは、複数のベーン収容溝を外周にもつロータ本体と、前記複数のベーン収容溝にそれぞれ径方向にスライド可能に収容された複数のベーンとで構成することができる。 [Explanation of Embodiments of the present disclosure]
(1) The rotary pump according to one aspect of the present disclosure is
A pump rotor with a flat rotor side facing the axis,
It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane. The housing body to be accommodated and
A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
The cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
The metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
The crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface.
It is a rotary pump.
In this way, since the sliding guide surface of the cover member with respect to the pump rotor is formed of crosslinked fluororesin, even when the clearance between the cover member and the pump rotor is set to be extremely small, the cover member and the pump rotor It is possible to prevent seizure during a long period of time. Since the mating surface of the cover member to the housing body is provided on the metal body constituting the cover member, the tightening force of the bolt can be supported by the metal body portion with rigidity, and the cover member slides. It is possible to prevent the position of the guide surface from being displaced in the axial direction due to the tightening force of the bolt. Therefore, when the cover member is bolted to the housing body, it is possible to accurately manage the axial clearance between the cover member and the pump rotor.
(2) It is preferable that the cover member adopts a flat plate-shaped side cover that is sandwiched and fixed between the housing body and the cover body arranged so as to face the flange surface of the housing body.
In this way, the rotary pump according to one aspect of the present disclosure can be obtained by additionally incorporating a flat plate-shaped side cover between the housing body and the cover member of the existing rotary pump.
(3) The recess also includes a region corresponding to a part of the mating surface so that the crosslinked fluororesin filled in the recess contacts the flange surface in a continuous annular region around the opening. It is preferable to use one having a shape recessed in the axial direction including the one.
In this way, the crosslinked fluororesin filled in the recesses comes into contact with the flange surface in a continuous annular region around the opening of the housing body, so that the crosslinked fluororesin between the cover member and the contact surface of the housing body is crosslinked. It is possible to prevent fluid leakage by sealing with resin. Moreover, since the crosslinked fluororesin constituting the mating surface is continuous with the crosslinked fluororesin constituting the sliding guide surface, the manufacturing cost can be kept low.
(4) The mating surface and the sliding guide surface can be a continuous finished surface having a surface roughness of 10-point average roughness Rz JIS 6.3 μm or less.
In this way, the mating surface and the sliding guide surface can be finished at the same time, so that the cost is low. Further, since the surface roughness of the mating surface and the sliding guide surface is Rz JIS 6.3 μm or less, it is possible to control the axial clearance between the cover member and the pump rotor with extremely high accuracy.
(5) The pump rotor has an inner rotor having a plurality of outer teeth on the outer circumference and a plurality of inner teeth rotatably supported around a position eccentric from the center of the inner rotor and meshing with the outer teeth. It can be configured with an annular outer rotor.
(6) The pump rotor can be composed of a rotor body having a plurality of vane accommodating grooves on the outer periphery and a plurality of vanes accommodated in the plurality of vane accommodating grooves so as to be slidable in the radial direction.
[本開示の実施形態の詳細]
本開示の実施形態にかかる回転ポンプの具体例を、以下に図面を参照しつつ説明する。なお、本発明はこれらの例示に限定されるものではなく、請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 [Details of Embodiments of the present disclosure]
Specific examples of the rotary pump according to the embodiment of the present disclosure will be described below with reference to the drawings. It should be noted that the present invention is not limited to these examples, and is indicated by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.
本開示の実施形態にかかる回転ポンプの具体例を、以下に図面を参照しつつ説明する。なお、本発明はこれらの例示に限定されるものではなく、請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 [Details of Embodiments of the present disclosure]
Specific examples of the rotary pump according to the embodiment of the present disclosure will be described below with reference to the drawings. It should be noted that the present invention is not limited to these examples, and is indicated by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.
図1から図6に、本開示の第1実施形態にかかる回転ポンプを示す。回転ポンプは、回転軸1で回転駆動されるポンプロータ2と、ポンプロータ2を収容するハウジング本体3と、ハウジング本体3の軸方向の一方側に配置される第1のカバー本体4aおよび第1のサイドカバー5aと、ハウジング本体3の軸方向の他方側に配置される第2のカバー本体4bおよび第2のサイドカバー5bとを有する。
1 to 6 show the rotary pump according to the first embodiment of the present disclosure. The rotary pump includes a pump rotor 2 that is rotationally driven by a rotary shaft 1, a housing body 3 that houses the pump rotor 2, and a first cover body 4a and a first cover body 4a that are arranged on one side of the housing body 3 in the axial direction. The side cover 5a and the second cover main body 4b and the second side cover 5b arranged on the other side in the axial direction of the housing main body 3 are provided.
図1、図4に示すように、ポンプロータ2は、複数の外歯6を外周にもつインナーロータ7と、外歯6に噛み合う複数の内歯8を内周にもつ環状のアウターロータ9で構成されている。インナーロータ7およびアウターロータ9は、ハウジング本体3に形成された軸方向の開口10に回転可能に収容されている。
As shown in FIGS. 1 and 4, the pump rotor 2 is an inner rotor 7 having a plurality of outer teeth 6 on the outer circumference and an annular outer rotor 9 having a plurality of inner teeth 8 meshing with the outer teeth 6 on the inner circumference. It is configured. The inner rotor 7 and the outer rotor 9 are rotatably housed in the axial opening 10 formed in the housing body 3.
図3に示すように、インナーロータ7には、回転軸1が挿入される軸穴11が形成されている。回転軸1と軸穴11は、回転軸1とインナーロータ7が一体回転するように嵌合している。回転軸1と軸穴11の嵌合は、図に示すような二面幅の嵌合のほか、スプライン嵌合、キー溝嵌合、円筒面同士の締め代をもった嵌合(焼嵌めや圧入による嵌合)を採用してもよい。
As shown in FIG. 3, the inner rotor 7 is formed with a shaft hole 11 into which the rotating shaft 1 is inserted. The rotating shaft 1 and the shaft hole 11 are fitted so that the rotating shaft 1 and the inner rotor 7 rotate integrally. The fitting of the rotating shaft 1 and the shaft hole 11 includes a two-sided width fitting as shown in the figure, a spline fitting, a keyway fitting, and a fitting with a tightening allowance between cylindrical surfaces (hard fitting and fitting). Fitting by press fitting) may be adopted.
図4に示すように、アウターロータ9は、外周円筒面12を有する。外周円筒面12は、ハウジング本体3の開口10の内周に隙間をもって嵌合し、その嵌合によって、アウターロータ9が回転可能に支持されている。ここで、アウターロータ9は、インナーロータ7の中心位置(すなわち回転軸1の回転中心位置)から偏心した位置を中心に回転可能に支持されている。インナーロータ7を回転させると、アウターロータ9は、内歯8と外歯6の噛み合いによってインナーロータ7と共に回転する。インナーロータ7の回転方向は、図では時計回りである。
As shown in FIG. 4, the outer rotor 9 has an outer peripheral cylindrical surface 12. The outer peripheral cylindrical surface 12 is fitted to the inner circumference of the opening 10 of the housing body 3 with a gap, and the outer rotor 9 is rotatably supported by the fitting. Here, the outer rotor 9 is rotatably supported around a position eccentric from the center position of the inner rotor 7 (that is, the rotation center position of the rotation shaft 1). When the inner rotor 7 is rotated, the outer rotor 9 rotates together with the inner rotor 7 due to the meshing of the inner teeth 8 and the outer teeth 6. The rotation direction of the inner rotor 7 is clockwise in the figure.
アウターロータ9の内歯8の数は、インナーロータ7の外歯6の数よりも1つ多い。インナーロータ7の外周とアウターロータ9の内周の間には、各外歯6および各内歯8で区画される複数のチャンバ13(流体を収容する空間)が形成されている。ここで、複数のチャンバ13は、インナーロータ7およびアウターロータ9の回転に伴い、容積が変化するように構成されている。すなわち、チャンバ13の容積は、インナーロータ7の中心とアウターロータ9の中心が最も遠い角度位置(図では上側位置)で最大となり、インナーロータ7の中心とアウターロータ9の中心が最も近い角度位置(図では下側位置)に近づくにつれて小さくなっている。そのため、インナーロータ7およびアウターロータ9が回転するとき、インナーロータ7の中心とアウターロータ9の中心が最も遠い角度位置から、インナーロータ7の中心とアウターロータ9の中心が最も近い角度位置に向かって移動する側(図では右側)では、チャンバ13の容積が縮小することによる流体の吐出作用が生じ、一方、インナーロータ7の中心とアウターロータ9の中心が最も近い角度位置から、インナーロータ7の中心とアウターロータ9の中心が最も遠い角度位置に向かって移動する側(図では左側)では、チャンバ13の容積が次第に拡大することによる流体の吸入作用が生じる。
The number of internal teeth 8 of the outer rotor 9 is one more than the number of external teeth 6 of the inner rotor 7. A plurality of chambers 13 (spaces for accommodating fluids) partitioned by the outer teeth 6 and the inner teeth 8 are formed between the outer circumference of the inner rotor 7 and the inner circumference of the outer rotor 9. Here, the plurality of chambers 13 are configured so that their volumes change as the inner rotor 7 and the outer rotor 9 rotate. That is, the volume of the chamber 13 is maximized at the angle position where the center of the inner rotor 7 and the center of the outer rotor 9 are farthest (upper position in the figure), and the center of the inner rotor 7 and the center of the outer rotor 9 are closest to each other. It becomes smaller as it approaches (lower position in the figure). Therefore, when the inner rotor 7 and the outer rotor 9 rotate, the center of the inner rotor 7 and the center of the outer rotor 9 move from the farthest angle position to the closest angle position between the center of the inner rotor 7 and the center of the outer rotor 9. On the moving side (on the right side in the figure), the volume of the chamber 13 is reduced to discharge the fluid, while the inner rotor 7 is located at the closest angle between the center of the inner rotor 7 and the center of the outer rotor 9. On the side where the center of the outer rotor 9 and the center of the outer rotor 9 move toward the farthest angular position (on the left side in the figure), the volume of the chamber 13 gradually increases, so that a fluid suction action occurs.
図5に示すように、インナーロータ7は、軸方向の一方側(図では左側)を向く平らな第1のインナーロータ側面14aと、軸方向の他方側(図では右側)を向く平らな第2のインナーロータ側面14bとを有する。第1のインナーロータ側面14aと第2のインナーロータ側面14bは、軸方向に互いに反対を向く平行な平面である。また、アウターロータ9は、軸方向の一方側を向く平らな第1のアウターロータ側面15aと、軸方向の他方側を向く平らな第2のアウターロータ側面15bとを有する。第1のアウターロータ側面15aと第2のアウターロータ側面15bは、軸方向に互いに反対を向く平行な平面である。
As shown in FIG. 5, the inner rotor 7 has a flat first inner rotor side surface 14a facing one side in the axial direction (left side in the figure) and a flat first inner rotor 7 facing the other side in the axial direction (right side in the figure). It has 2 inner rotor side surfaces 14b. The first inner rotor side surface 14a and the second inner rotor side surface 14b are parallel planes facing opposite to each other in the axial direction. Further, the outer rotor 9 has a flat first outer rotor side surface 15a facing one side in the axial direction and a flat second outer rotor side surface 15b facing the other side in the axial direction. The first outer rotor side surface 15a and the second outer rotor side surface 15b are parallel planes facing opposite to each other in the axial direction.
ここで、第1のインナーロータ側面14aから第2のインナーロータ側面14bまでのインナーロータ7の軸方向幅寸法は、第1のアウターロータ側面15aから第2のアウターロータ側面15bまでのアウターロータ9の軸方向幅寸法と同一である。第1のインナーロータ側面14aと第1のアウターロータ側面15aは同一平面上に位置し、第2のインナーロータ側面14bと第2のアウターロータ側面15bも同一平面上に位置する。インナーロータ7とアウターロータ9は、いずれも焼結体である。焼結体は、鉄系の粉末材料を金型で圧縮成形した粉末成形体を融点以下の高温で加熱して得られる部材である。
Here, the axial width dimension of the inner rotor 7 from the first inner rotor side surface 14a to the second inner rotor side surface 14b is the outer rotor 9 from the first outer rotor side surface 15a to the second outer rotor side surface 15b. It is the same as the axial width dimension of. The first inner rotor side surface 14a and the first outer rotor side surface 15a are located on the same plane, and the second inner rotor side surface 14b and the second outer rotor side surface 15b are also located on the same plane. Both the inner rotor 7 and the outer rotor 9 are sintered bodies. The sintered body is a member obtained by heating a powder molded body obtained by compression molding an iron-based powder material with a mold at a high temperature below the melting point.
図3に示すように、回転軸1が挿入される軸穴11は、インナーロータ7を軸方向に貫通する貫通穴である。そして、回転軸1は、インナーロータ7から軸方向の一方側(図では左側)に突出した部分と、インナーロータ7から軸方向の他方側(図では右側)に突出した部分を有するように軸穴11に挿入されている。回転軸1のインナーロータ7から軸方向の一方側に突出した部分は、第1のカバー本体4aに取り付けられた第1の軸受16aで回転可能に支持され、回転軸1のインナーロータ7から軸方向の他方側に突出した部分は、第2のカバー本体4bに取り付けられた第2の軸受16bで回転可能に支持されている。回転軸1のインナーロータ7から軸方向の他方側に突出した部分(第2の軸受16bで支持される側の部分)は、図示しない回転駆動装置(電動モータ等)に接続されている。
As shown in FIG. 3, the shaft hole 11 into which the rotating shaft 1 is inserted is a through hole that penetrates the inner rotor 7 in the axial direction. The rotating shaft 1 has a portion protruding from the inner rotor 7 on one side in the axial direction (left side in the drawing) and a portion protruding from the inner rotor 7 on the other side in the axial direction (right side in the drawing). It is inserted in the hole 11. The portion of the rotating shaft 1 protruding from the inner rotor 7 to one side in the axial direction is rotatably supported by the first bearing 16a attached to the first cover body 4a, and is rotatably supported from the inner rotor 7 of the rotating shaft 1. The portion protruding to the other side in the direction is rotatably supported by a second bearing 16b attached to the second cover body 4b. A portion of the rotating shaft 1 protruding from the inner rotor 7 to the other side in the axial direction (a portion supported by the second bearing 16b) is connected to a rotary driving device (electric motor or the like) (not shown).
図5に示すように、第1のカバー本体4a、第1のサイドカバー5a、ハウジング本体3、第2のサイドカバー5b、第2のカバー本体4bは、各部材に形成したボルト挿入穴17に共通のボルト18を挿入し、そのボルト18で軸方向に締め付けることで互いに固定されている。また、第1のカバー本体4a、第1のサイドカバー5a、ハウジング本体3、第2のサイドカバー5b、第2のカバー本体4bは、各部材に形成したノックピン挿入穴19に共通のノックピン20を挿入することで軸直角方向に位置決めされている。
As shown in FIG. 5, the first cover body 4a, the first side cover 5a, the housing body 3, the second side cover 5b, and the second cover body 4b are formed in the bolt insertion holes 17 formed in each member. A common bolt 18 is inserted and tightened in the axial direction with the bolt 18 to fix each other. Further, the first cover body 4a, the first side cover 5a, the housing body 3, the second side cover 5b, and the second cover body 4b have knock pins 20 common to the knock pin insertion holes 19 formed in the respective members. By inserting it, it is positioned in the direction perpendicular to the axis.
ハウジング本体3は、軸方向の一方側(図では左側)および他方側(図では右側)に開放する開口10と、開口10の軸方向の一方側の周囲に形成された平らな第1のフランジ面21aと、開口10の軸方向の他方側の周囲に形成された平らな第2のフランジ面21bとを有する。第1のフランジ面21aと第2のフランジ面21bは、軸方向に互いに反対を向く平行な平面である。
The housing body 3 has an opening 10 that opens to one side (left side in the drawing) and the other side (right side in the figure) in the axial direction, and a flat first flange formed around one side in the axial direction of the opening 10. It has a surface 21a and a flat second flange surface 21b formed around the other side of the opening 10 in the axial direction. The first flange surface 21a and the second flange surface 21b are parallel planes facing opposite to each other in the axial direction.
第1のカバー本体4aは、ハウジング本体3の第1のフランジ面21aと対向して配置され、その第1のカバー本体4aとハウジング本体3の間に第1のサイドカバー5aが挟み込まれている。第2のカバー本体4bも、ハウジング本体3の第2のフランジ面21bと対向して配置され、その第2のカバー本体4bとハウジング本体3の間に第2のサイドカバー5bが挟み込まれている。
The first cover body 4a is arranged so as to face the first flange surface 21a of the housing body 3, and the first side cover 5a is sandwiched between the first cover body 4a and the housing body 3. .. The second cover body 4b is also arranged so as to face the second flange surface 21b of the housing body 3, and the second side cover 5b is sandwiched between the second cover body 4b and the housing body 3. ..
第1のフランジ面21aは、第1のインナーロータ側面14aおよび第1のアウターロータ側面15aと同一平面上に揃っている。また、第2のフランジ面21bは、第2のインナーロータ側面14bおよび第2のアウターロータ側面15bと同一平面上に揃っている。ここで、インナーロータ7およびアウターロータ9の軸方向幅寸法は、ハウジング本体3の軸方向幅寸法よりもわずかに小さく、その差は20μm以下(好ましくは15μm以下、より好ましくは10μm以下)に設定されている。
The first flange surface 21a is aligned with the first inner rotor side surface 14a and the first outer rotor side surface 15a. Further, the second flange surface 21b is aligned with the second inner rotor side surface 14b and the second outer rotor side surface 15b on the same plane. Here, the axial width dimension of the inner rotor 7 and the outer rotor 9 is slightly smaller than the axial width dimension of the housing body 3, and the difference is set to 20 μm or less (preferably 15 μm or less, more preferably 10 μm or less). Has been done.
第1のサイドカバー5aと第2のサイドカバー5bは、ハウジング本体3を間にして対称の構成である。そのため、第1のサイドカバー5aについて説明し、第2のサイドカバー5bについては、対応する部分に同一の符号または末尾のアルファベットaをbに置き換えた符号を付して説明を省略する。
The first side cover 5a and the second side cover 5b have a symmetrical configuration with the housing body 3 in between. Therefore, the first side cover 5a will be described, and the description of the second side cover 5b will be omitted by adding the same code or a code in which the last alphabet a is replaced with b in the corresponding portion.
第1のサイドカバー5aは、ボルト18の締め付けにより第1のフランジ面21aに押して付けて固定される平らな合わせ面22と、第1のインナーロータ側面14aおよび第1のアウターロータ側面15aを摺動案内する平らな摺動案内面23とを有する。
The first side cover 5a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening a bolt 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance.
第1のサイドカバー5aは、5mm以下(好ましくは4mm以下)の均一な厚みをもつ平板状の部材である。第1のサイドカバー5aは、架橋フッ素樹脂24と金属体25とで形成されている。金属体25の材質としては、鋼材やアルミ合金を採用することができる。金属体25には、金属で形成された合わせ面22と、摺動案内面23に対応する領域を合わせ面22に対して軸方向に凹ませた凹部26とが設けられている。凹部26は、全域にわたって深さが一定の扁平な凹部とされている。凹部26の深さは、0.5mm以下(好ましくは0.3mm以下、より好ましくは0.2mm以下)に設定することができる。凹部26は、ハウジング本体3の開口10の輪郭を内側に包含する輪郭(図では、開口10の輪郭をなす円よりも大径の円形状の輪郭)を有する。凹部26には架橋フッ素樹脂24が充填され、この架橋フッ素樹脂24によって、合わせ面22と同一平面上に摺動案内面23が形成されている。合わせ面22と摺動案内面23は、十点平均粗さRzJIS6.3μm以下(好ましくはRzJIS3.2μm以下)の面粗さをもつ一続きの仕上げ面とされている。
The first side cover 5a is a flat plate-like member having a uniform thickness of 5 mm or less (preferably 4 mm or less). The first side cover 5a is formed of a crosslinked fluororesin 24 and a metal body 25. As the material of the metal body 25, a steel material or an aluminum alloy can be adopted. The metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22. The recess 26 is a flat recess having a constant depth over the entire area. The depth of the recess 26 can be set to 0.5 mm or less (preferably 0.3 mm or less, more preferably 0.2 mm or less). The recess 26 has a contour that includes the contour of the opening 10 of the housing body 3 inside (in the figure, a circular contour having a diameter larger than the circle forming the contour of the opening 10). The recess 26 is filled with a crosslinked fluororesin 24, and the crosslinked fluororesin 24 forms a sliding guide surface 23 on the same plane as the mating surface 22. The mating surface 22 and the sliding guide surface 23 are continuous finished surfaces having a surface roughness of 10-point average roughness Rz JIS 6.3 μm or less (preferably Rz JIS 3.2 μm or less).
ここで、十点平均粗さRzJISは、日本産業規格JISB0601:2013「製品の幾何特性仕様(GPS)-表面性状:輪郭曲線方式-用語,定義及び表面性状パラメータ」の「附属書JA(参考)十点平均粗さ」に規定されたパラメータである。すなわち、十点平均粗さRzJISは、粗さ曲線からその平均線の方向に基準長さだけを抜き取り、この抜き取り部分において、最も高い山頂から高い順に5番目までの山高さの平均と、最も深い谷底から深い順に5番目までの谷深さの平均との和である。
Here, the ten-point average roughness Rz JIS is referred to as "Annex JA (Reference)" of Japanese Industrial Standard JIS B0601: 2013 "Geometric characteristic specifications (GPS) of products-Surface texture: Contour curve method-Terms, definitions and surface texture parameters". ) Ten-point average roughness ”is a parameter specified. That is, the ten-point average roughness Rz JIS extracts only the reference length from the roughness curve in the direction of the average line, and in this extracted portion, the average of the mountain heights from the highest mountain peak to the fifth mountain height and the highest. It is the sum of the average of the valley depths from the deepest valley bottom to the fifth in the deepest order.
架橋フッ素樹脂24は、フッ素樹脂を構成する鎖状高分子の分子間を架橋結合したものであり、一般的なフッ素樹脂(非架橋フッ素樹脂)と同等の低い摩擦係数を有しながら、一般的なフッ素樹脂よりも、きわめて高い耐摩耗性を有する。
The crosslinked fluororesin 24 is obtained by cross-linking between the molecules of the chain polymer constituting the fluororesin, and has a low friction coefficient equivalent to that of a general fluororesin (non-crosslinked fluororesin), but is generally used. It has extremely high wear resistance compared to fluororesin.
架橋するフッ素樹脂としては、ポリテトラフルオロエチレン(PTFE)、テトラフルオロエチレン-ヘキサフルオロプロピレン共重合体(FEP)、テトラフルオロエチレン-パーフルオロアルキルビニルエーテル共重合体(PFA)等を採用することができる。架橋フッ素樹脂24として、架橋PTFEを採用すると好ましい。架橋PTFEを採用すると、架橋PTFEは上記のフッ素樹脂の中でも特に低い摩擦係数をもち、かつ耐摩耗性に優れるため、ほとんど摩耗することがなく、ポンプ効率を効果的に高めることが可能となる。
As the fluororesin to be crosslinked, polytetrafluoroethylene (PTFE), tetrafluoroethylene-hexafluoropropylene copolymer (FEP), tetrafluoroethylene-perfluoroalkyl vinyl ether copolymer (PFA) and the like can be adopted. .. It is preferable to use crosslinked PTFE as the crosslinked fluororesin 24. When the crosslinked PTFE is adopted, the crosslinked PTFE has a particularly low coefficient of friction among the above-mentioned fluororesins and is excellent in wear resistance, so that the crosslinked PTFE hardly wears and the pump efficiency can be effectively improved.
第1のサイドカバー5aは、例えば、次のようにして形成することができる。
The first side cover 5a can be formed, for example, as follows.
図7の上図に示すように、まず、厚みが一定の板状の金属体25の表面に凹部26を形成する。次に、図7の中図に示すように、金属体25の凹部26の側の面に、架橋フッ素樹脂24の皮膜を形成する。このとき、凹部26が架橋フッ素樹脂24で充填されるとともに、凹部26の周囲も架橋フッ素樹脂24で覆われた状態となっている。その後、図7の下図に示すように、凹部26の周囲の金属が露出するまで架橋フッ素樹脂24を研削加工し、さらに、凹部26の周囲の金属および凹部26内の架橋フッ素樹脂24を研削加工する。ここで、凹部26の周囲の金属の表面が合わせ面22に対応し、凹部26内の架橋フッ素樹脂24の表面が摺動案内面23に対応する。このようにして形成された合わせ面22と摺動案内面23は、同じ面粗さをもつ一続きの仕上げ面となる。
As shown in the upper part of FIG. 7, first, a recess 26 is formed on the surface of a plate-shaped metal body 25 having a constant thickness. Next, as shown in the middle figure of FIG. 7, a film of the crosslinked fluororesin 24 is formed on the surface of the metal body 25 on the side of the recess 26. At this time, the recess 26 is filled with the crosslinked fluororesin 24, and the periphery of the recess 26 is also covered with the crosslinked fluororesin 24. After that, as shown in the lower figure of FIG. 7, the crosslinked fluororesin 24 is ground until the metal around the recess 26 is exposed, and further, the metal around the recess 26 and the crosslinked fluororesin 24 in the recess 26 are ground. To do. Here, the surface of the metal around the recess 26 corresponds to the mating surface 22, and the surface of the crosslinked fluororesin 24 in the recess 26 corresponds to the sliding guide surface 23. The mating surface 22 and the sliding guide surface 23 formed in this way form a continuous finished surface having the same surface roughness.
ここで、図7の中図に示す架橋フッ素樹脂24の皮膜の形成は、例えば、以下のようにして行なうことができる。まず、金属体25の凹部26の側の表面に、フッ素樹脂(例えばPTFE)の微粒子を水に分散させた分散液を塗布する。次に、塗布した分散液を乾燥させることで、金属体25の凹部26の側の表面に、フッ素樹脂の微粒子の層を形成する。続いて、金属体25およびフッ素樹脂の微粒子の層を、フッ素樹脂の融点以上の温度に加熱することで、フッ素樹脂の微粒子を焼成し、フッ素樹脂の微粒子同士を融着させる。その後、所定の高温の無酸素雰囲気中において放射線(例えば、電子線)を照射することで、フッ素樹脂を構成する鎖状高分子同士の間に共有結合を生じさせ、鎖状高分子の分子間を架橋する。また、このとき照射される放射線によって、フッ素樹脂を構成する鎖状高分子の分子と、金属体25の表面との間でも化学結合が生じ、その化学結合によって、架橋フッ素樹脂24の皮膜が、きわめて高い密着性をもって金属体25に接着する。このようにして、図7の中図に示す架橋フッ素樹脂24の皮膜を形成することができる。
Here, the film of the crosslinked fluororesin 24 shown in the middle figure of FIG. 7 can be formed, for example, as follows. First, a dispersion liquid in which fine particles of fluororesin (for example, PTFE) are dispersed in water is applied to the surface of the metal body 25 on the side of the recess 26. Next, the applied dispersion liquid is dried to form a layer of fine particle particles of fluororesin on the surface of the metal body 25 on the side of the recess 26. Subsequently, by heating the metal body 25 and the layer of the fluororesin fine particles to a temperature equal to or higher than the melting point of the fluororesin, the fluororesin fine particles are fired and the fluororesin fine particles are fused to each other. After that, by irradiating radiation (for example, an electron beam) in a predetermined high-temperature anoxic atmosphere, a covalent bond is generated between the chain polymers constituting the fluororesin, and the molecules of the chain polymer are intermolecular. To bridge. Further, the radiation irradiated at this time also causes a chemical bond between the molecule of the chain polymer constituting the fluororesin and the surface of the metal body 25, and the chemical bond causes the film of the crosslinked fluororesin 24 to be formed. It adheres to the metal body 25 with extremely high adhesion. In this way, the film of the crosslinked fluororesin 24 shown in the middle figure of FIG. 7 can be formed.
図6に示すように、第1のサイドカバー5aには、第1のインナーロータ側面14aおよび第1のアウターロータ側面15aと対向する面に開口する第1の吸入ポート30aと、第1の吸入ポート30aから周方向に間隔をおいて開口する第1の吐出ポート31aとが設けられている。
As shown in FIG. 6, the first side cover 5a includes a first suction port 30a that opens on a surface facing the first inner rotor side surface 14a and the first outer rotor side surface 15a, and a first suction port. A first discharge port 31a that opens from the port 30a at intervals in the circumferential direction is provided.
同様に、第2のサイドカバー5bには、第2のインナーロータ側面14bおよび第2のアウターロータ側面15bと対向する面に開口する第2の吸入ポート30bと、第2の吸入ポート30bから周方向に間隔をおいて開口する第2の吐出ポート31bとが設けられている。
Similarly, the second side cover 5b has a second suction port 30b that opens on a surface facing the second inner rotor side surface 14b and the second outer rotor side surface 15b, and a circumference from the second suction port 30b. A second discharge port 31b that opens at intervals in the direction is provided.
図1に示すように、第1の吸入ポート30aと第1の吐出ポート31aは、いずれも、回転軸1を中心とする円弧状に開口している。同様に、第2の吸入ポート30bと第2の吐出ポート31bも、いずれも、回転軸1を中心とする円弧状に開口している。
As shown in FIG. 1, both the first suction port 30a and the first discharge port 31a are opened in an arc shape centered on the rotation shaft 1. Similarly, both the second suction port 30b and the second discharge port 31b are opened in an arc shape centered on the rotation shaft 1.
第1の吸入ポート30aと第2の吸入ポート30bは、インナーロータ7およびアウターロータ9を間に挟んで対称の位置に同じ形状で開口している。これにより、第1の吸入ポート30a内の流体から第1のインナーロータ側面14aおよび第1のアウターロータ側面15aが受ける圧力と、第2の吸入ポート30b内の流体から第2のインナーロータ側面14bおよび第2のアウターロータ側面15bが受ける圧力とをバランスさせ、インナーロータ7およびアウターロータ9に傾きが生じるのを防止している。
The first suction port 30a and the second suction port 30b are opened at symmetrical positions with the inner rotor 7 and the outer rotor 9 sandwiched between them in the same shape. As a result, the pressure received by the first inner rotor side surface 14a and the first outer rotor side surface 15a from the fluid in the first suction port 30a and the second inner rotor side surface 14b from the fluid in the second suction port 30b. The pressure received by the second outer rotor side surface 15b is balanced, and the inner rotor 7 and the outer rotor 9 are prevented from being tilted.
同様に、第1の吐出ポート31aと第2の吐出ポート31bも、インナーロータ7およびアウターロータ9を間に挟んで対称の位置に同じ形状で開口している。これにより、これにより、第1の吐出ポート31a内の流体から第1のインナーロータ側面14aおよび第1のアウターロータ側面15aが受ける圧力と、第2の吐出ポート31b内の流体から第2のインナーロータ側面14bおよび第2のアウターロータ側面15bが受ける圧力とをバランスさせ、インナーロータ7およびアウターロータ9に傾きが生じるのを防止している。
Similarly, the first discharge port 31a and the second discharge port 31b are also opened at symmetrical positions with the inner rotor 7 and the outer rotor 9 sandwiched between them in the same shape. As a result, the pressure received by the first inner rotor side surface 14a and the first outer rotor side surface 15a from the fluid in the first discharge port 31a and the second inner from the fluid in the second discharge port 31b. The pressure received by the rotor side surface 14b and the second outer rotor side surface 15b is balanced to prevent the inner rotor 7 and the outer rotor 9 from being tilted.
図4、図6に示すように、第1の吸入ポート30aと第2の吸入ポート30bは、ハウジング本体3のポンプロータ2を収容する開口10から離間した位置に形成された連通路32を介して連通している。また、図2、図6に示すように、第1の吸入ポート30aは、第1のカバー本体4aの外面に開口する吸入口33に連通し、第1の吐出ポート31aは、第1のカバー本体4aの外面に開口する吐出口34に連通している。
As shown in FIGS. 4 and 6, the first suction port 30a and the second suction port 30b pass through a communication passage 32 formed at a position separated from the opening 10 accommodating the pump rotor 2 of the housing body 3. Communicate with each other. Further, as shown in FIGS. 2 and 6, the first suction port 30a communicates with the suction port 33 opening on the outer surface of the first cover body 4a, and the first discharge port 31a is the first cover. It communicates with the discharge port 34 that opens on the outer surface of the main body 4a.
上記の回転ポンプは、図5に示すように、第1のサイドカバー5aおよび第2のサイドカバー5bの摺動案内面23が架橋フッ素樹脂24で形成されているので、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間のクリアランス(すなわち、第1のサイドカバー5aの摺動案内面23と第2のサイドカバー5bの摺動案内面23の間の内幅寸法と、インナーロータ7またはアウターロータ9の軸方向の幅寸法との差)をきわめて小さい大きさ(20μm以下、好ましくは15μm以下、より好ましくは10μm以下)に設定したときにも、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間の焼き付きを長期にわたって防止することが可能である。
In the above rotary pump, as shown in FIG. 5, since the sliding guide surface 23 of the first side cover 5a and the second side cover 5b is formed of the crosslinked fluororesin 24, the first side cover 5a And the clearance between the second side cover 5b and the pump rotor 2 (that is, the inner width dimension between the sliding guide surface 23 of the first side cover 5a and the sliding guide surface 23 of the second side cover 5b). And the first side even when the size (difference from the axial width dimension of the inner rotor 7 or the outer rotor 9) is set to an extremely small size (20 μm or less, preferably 15 μm or less, more preferably 10 μm or less). It is possible to prevent seizure between the cover 5a and the second side cover 5b and the pump rotor 2 for a long period of time.
また、この回転ポンプは、第1のサイドカバー5aおよび第2のサイドカバー5bをハウジング本体3にボルト18で固定したときに、ボルト18の締め付け力による摺動案内面23の位置ずれが生じにくく、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2(インナーロータ7またはアウターロータ9)の間の軸方向のクリアランスを精度よく管理することが可能である。
Further, in this rotary pump, when the first side cover 5a and the second side cover 5b are fixed to the housing body 3 with bolts 18, the sliding guide surface 23 is less likely to be displaced due to the tightening force of the bolts 18. , It is possible to accurately manage the axial clearance between the first side cover 5a and the second side cover 5b and the pump rotor 2 (inner rotor 7 or outer rotor 9).
すなわち、仮に、図5に示す第1のサイドカバー5aおよび第2のサイドカバー5bを、金属体25の片面全体(すなわち、ハウジング本体3への合わせ面22とポンプロータ2との摺動案内面23とを含む一続きの平面全体。このとき金属体25に凹部26は設けない)を架橋フッ素樹脂でコーティングしたサイドカバーに置き換えることを想定した場合、そのサイドカバーをハウジング本体3にボルト18で固定するときに、ボルト18の締め付け力によって、サイドカバーのハウジング本体3への合わせ面22に設けられた架橋フッ素樹脂の皮膜が圧縮変形し、その圧縮変形によって、架橋フッ素樹脂の皮膜の厚さが1μm前後~10μm前後小さくなり、その分、サイドカバーの摺動案内面23の位置が軸方向にわずかにずれる。例えば、4本のボルト18をそれぞれ11Nmのトルクで締め付けた場合、50μmの厚さの架橋フッ素樹脂の皮膜であれば、ボルト18の締め付け力に伴う圧縮変形によって1.6μm程度薄くなり、150μmの厚さの架橋フッ素樹脂の皮膜であれば、4.8μm程度薄くなり、250μmの厚さの架橋フッ素樹脂の皮膜であれば、8.0μm程度薄くなる。その結果、サイドカバーとポンプロータ2の間の軸方向のクリアランスが設計値よりもわずかに小さくなり、特に、クリアランスの大きさを20μm以下のきわめて小さい大きさに設定したときに、ポンプロータ2を回転駆動するためのトルクが、想定よりも大きくなるという問題がある。
That is, tentatively, the first side cover 5a and the second side cover 5b shown in FIG. 5 are attached to the entire one surface of the metal body 25 (that is, the sliding guide surface between the mating surface 22 to the housing body 3 and the pump rotor 2). Assuming that the entire continuous flat surface including the 23 is replaced with a side cover coated with a crosslinked fluororesin (at this time, the metal body 25 is not provided with the recess 26), the side cover is attached to the housing body 3 with a bolt 18. When fixing, the tightening force of the bolt 18 compresses and deforms the cross-linked fluororesin film provided on the mating surface 22 of the side cover to the housing body 3, and the compressive deformation causes the thickness of the cross-linked fluororesin film. Is reduced by about 1 μm to about 10 μm, and the position of the sliding guide surface 23 of the side cover is slightly displaced in the axial direction by that amount. For example, when four bolts 18 are tightened with a torque of 11 Nm each, a crosslinked fluororesin film having a thickness of 50 μm becomes thinner by about 1.6 μm due to compressive deformation due to the tightening force of the bolts 18 and becomes 150 μm. A film of crosslinked fluororesin having a thickness of about 4.8 μm is thin, and a film of crosslinked fluororesin with a thickness of 250 μm is thinned by about 8.0 μm. As a result, the axial clearance between the side cover and the pump rotor 2 becomes slightly smaller than the design value, and especially when the clearance size is set to an extremely small size of 20 μm or less, the pump rotor 2 is operated. There is a problem that the torque for rotationally driving becomes larger than expected.
この問題に対し、本開示の実施形態にかかる回転ポンプは、第1のサイドカバー5aおよび第2のサイドカバー5bのハウジング本体3への合わせ面22が、第1のサイドカバー5aおよび第2のサイドカバー5bを構成する金属体25に設けられているので、ボルト18の締め付け力を金属体25の部分で剛性をもって支持することができ、第1のサイドカバー5aおよび第2のサイドカバー5bの摺動案内面23の位置がボルト18の締め付け力で軸方向にずれるのを防止することができる。そのため、第1のサイドカバー5aおよび第2のサイドカバー5bをハウジング本体3にボルト18で固定したときに、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2の間の軸方向のクリアランスを精度よく管理することが可能である。
In response to this problem, in the rotary pump according to the embodiment of the present disclosure, the mating surfaces 22 of the first side cover 5a and the second side cover 5b to the housing body 3 have the first side cover 5a and the second side cover 5a and the second side cover 5a. Since it is provided on the metal body 25 constituting the side cover 5b, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the first side cover 5a and the second side cover 5b can be supported. It is possible to prevent the position of the sliding guide surface 23 from being displaced in the axial direction due to the tightening force of the bolt 18. Therefore, when the first side cover 5a and the second side cover 5b are fixed to the housing body 3 with bolts 18, the axial direction between the first side cover 5a and the second side cover 5b and the pump rotor 2 It is possible to manage the clearance of the housing accurately.
また、この回転ポンプは、既存の回転ポンプに第1のサイドカバー5aおよび第2のサイドカバー5bを追加して組み込むことで実施形態の回転ポンプを得ることが可能であり、低コストである。
Further, this rotary pump can obtain the rotary pump of the embodiment by adding the first side cover 5a and the second side cover 5b to the existing rotary pump, and is low cost.
また、この回転ポンプは、架橋フッ素樹脂24を充填する凹部26が、第1の軸受16aを取り付ける第1のカバー本体4aではなく、第1のカバー本体4aとは別体の金属体25に設けられているので、第1のカバー本体4aの表面に、直接に架橋フッ素樹脂24を充填する凹部26を設けて架橋フッ素樹脂24を充填するよりも、凹部26の加工および架橋フッ素樹脂24の充填が容易となっている。同様に、架橋フッ素樹脂24を充填する凹部26が、第2の軸受16bを取り付ける第2のカバー本体4bではなく、第2のカバー本体4bとは別体の金属体25に設けられているので、第2のカバー本体4bの表面に、直接に架橋フッ素樹脂24を充填する凹部26を設けて架橋フッ素樹脂24を充填するよりも、凹部26の加工および架橋フッ素樹脂24の充填が容易となっている。
Further, in this rotary pump, the recess 26 filled with the crosslinked fluororesin 24 is provided not in the first cover body 4a to which the first bearing 16a is attached, but in a metal body 25 separate from the first cover body 4a. Therefore, rather than providing the recess 26 for directly filling the crosslinked fluororesin 24 on the surface of the first cover body 4a and filling the crosslinked fluororesin 24, the recess 26 is processed and the crosslinked fluororesin 24 is filled. Is easy. Similarly, since the recess 26 filled with the crosslinked fluororesin 24 is provided not in the second cover body 4b to which the second bearing 16b is attached, but in the metal body 25 separate from the second cover body 4b. , It is easier to process the recess 26 and fill the crosslinked fluororesin 24 than to directly provide the recess 26 for filling the crosslinked fluororesin 24 on the surface of the second cover body 4b and fill the crosslinked fluororesin 24. ing.
また、この回転ポンプは、合わせ面22と摺動案内面23を同時に仕上げ加工することで、合わせ面22と摺動案内面23を、十点平均粗さRzJIS6.3μm以下(好ましくはRzJIS3.2μm以下)の面粗さをもつ一続きの仕上げ面としているので、低コストである。また、合わせ面22と摺動案内面23の面粗さがRzJIS6.3μm以下(好ましくはRzJIS3.2μm以下)なので、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間のクリアランス(すなわち、第1のサイドカバー5aの摺動案内面23と第2のサイドカバー5bの摺動案内面23の間の内幅寸法と、インナーロータ7またはアウターロータ9の軸方向の幅寸法との差)をきわめて精度よく管理することが可能である。
Further, in this rotary pump, the mating surface 22 and the sliding guide surface 23 are finished at the same time, so that the mating surface 22 and the sliding guide surface 23 are made to have a ten-point average roughness Rz JIS 6.3 μm or less (preferably Rz). Since it is a continuous finished surface with a surface roughness of JIS 3.2 μm or less), the cost is low. Further, since the surface roughness of the mating surface 22 and the sliding guide surface 23 is Rz JIS 6.3 μm or less (preferably Rz JIS 3.2 μm or less), the first side cover 5a, the second side cover 5b, and the pump rotor Clearance between 2 (that is, the inner width dimension between the sliding guide surface 23 of the first side cover 5a and the sliding guide surface 23 of the second side cover 5b, and the inner rotor 7 or the outer rotor 9 It is possible to manage the difference from the width dimension in the axial direction) with extremely high accuracy.
図8、図9に、本開示の第2実施形態にかかる回転ポンプを示す。第2実施形態は、第1のサイドカバー5aおよび第2のサイドカバー5bの構成のみが第1実施形態と異なり、他の構成は第1実施形態と同じである。そのため、第1実施形態に対応する部分は同一の符号を付して説明を省略する。
8 and 9 show the rotary pump according to the second embodiment of the present disclosure. In the second embodiment, only the configurations of the first side cover 5a and the second side cover 5b are different from those of the first embodiment, and the other configurations are the same as those of the first embodiment. Therefore, the parts corresponding to the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
第1のサイドカバー5aは、ボルト18の締め付けにより第1のフランジ面21aに押して付けて固定される平らな合わせ面22と、第1のインナーロータ側面14aおよび第1のアウターロータ側面15aを摺動案内する平らな摺動案内面23とを有する。金属体25には、金属で形成された合わせ面22と、摺動案内面23に対応する領域を合わせ面22に対して軸方向に凹ませた凹部26とが設けられている。凹部26は、凹部26に充填された架橋フッ素樹脂24が、ハウジング本体3の開口10の周囲を途切れずに連続する環状の領域で第1のフランジ面21aに接触するように、合わせ面22の一部に対応する領域も含めて軸方向に凹ませた形状を有する。すなわち、第1のサイドカバー5aは、合わせ面22の一部(ボルト挿入穴17の周囲を囲む部分)が金属体25に形成され、合わせ面22の残りの部分が凹部26に充填された架橋フッ素樹脂24で形成されている。第2のサイドカバー5bも、第1のサイドカバー5aと同様に構成されている。
The first side cover 5a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening a bolt 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance. The metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22. The recess 26 is formed on the mating surface 22 so that the crosslinked fluororesin 24 filled in the recess 26 comes into contact with the first flange surface 21a in a continuous annular region around the opening 10 of the housing body 3. It has a shape recessed in the axial direction including a part corresponding to the region. That is, in the first side cover 5a, a part of the mating surface 22 (a portion surrounding the periphery of the bolt insertion hole 17) is formed in the metal body 25, and the remaining portion of the mating surface 22 is filled in the recess 26. It is made of fluororesin 24. The second side cover 5b is also configured in the same manner as the first side cover 5a.
この回転ポンプは、凹部26に充填された架橋フッ素樹脂24が、ハウジング本体3の開口10の周囲を途切れずに連続する環状の領域で第1のフランジ面21aおよび第2のフランジ面21bに接触するため、第1のサイドカバー5aおよび第2のサイドカバー5bとハウジング本体3との接触面間を架橋フッ素樹脂24でシールし、流体の漏れを防止することが可能である。しかも、合わせ面22を構成する架橋フッ素樹脂24は、摺動案内面23を構成する架橋フッ素樹脂24と一続きであることから、製造コストが低く抑えられる。
In this rotary pump, the crosslinked fluororesin 24 filled in the recess 26 contacts the first flange surface 21a and the second flange surface 21b in an annular region that is continuous without interruption around the opening 10 of the housing body 3. Therefore, it is possible to seal the contact surfaces between the first side cover 5a and the second side cover 5b and the housing body 3 with the crosslinked fluororesin 24 to prevent fluid leakage. Moreover, since the crosslinked fluororesin 24 constituting the mating surface 22 is continuous with the crosslinked fluororesin 24 forming the sliding guide surface 23, the manufacturing cost can be kept low.
図10、図11に、本開示の第3実施形態にかかる回転ポンプを示す。上記各実施形態に対応する部分は同一の符号を付して説明を省略する。
10 and 11 show the rotary pump according to the third embodiment of the present disclosure. The parts corresponding to the above embodiments are designated by the same reference numerals, and the description thereof will be omitted.
回転ポンプは、回転軸1で回転駆動されるポンプロータ2と、ポンプロータ2を収容するハウジング本体3と、ハウジング本体3の軸方向の一方側(図では左側)に配置される第1のカバー本体4aと、ハウジング本体3の軸方向の他方側(図では右側)に配置される第2のカバー本体4bとを有する。
The rotary pump includes a pump rotor 2 that is rotationally driven by a rotary shaft 1, a housing body 3 that houses the pump rotor 2, and a first cover that is arranged on one side (left side in the figure) of the housing body 3 in the axial direction. It has a main body 4a and a second cover main body 4b arranged on the other side (right side in the drawing) of the housing main body 3 in the axial direction.
図11に示すように、第1のカバー本体4a、ハウジング本体3、第2のカバー本体4bは、各部材に形成したボルト挿入穴17に共通のボルト18を挿入し、そのボルト18で軸方向に締め付けることで互いに固定されている。また、第1のカバー本体4a、ハウジング本体3、第2のカバー本体4bは、各部材に形成したノックピン挿入穴19に共通のノックピン20を挿入することで軸直角方向に位置決めされている。
As shown in FIG. 11, in the first cover body 4a, the housing body 3, and the second cover body 4b, a common bolt 18 is inserted into a bolt insertion hole 17 formed in each member, and the bolt 18 is used in the axial direction. They are fixed to each other by tightening. Further, the first cover body 4a, the housing body 3, and the second cover body 4b are positioned in the direction perpendicular to the axis by inserting a common knock pin 20 into the knock pin insertion holes 19 formed in each member.
第1のカバー本体4aは、ボルト18の締め付けにより第1のフランジ面21aに押して付けて固定される平らな合わせ面22と、第1のインナーロータ側面14aおよび第1のアウターロータ側面15aを摺動案内する平らな摺動案内面23とを有する。
The first cover body 4a slides a flat mating surface 22 fixed by pressing against the first flange surface 21a by tightening bolts 18, a first inner rotor side surface 14a, and a first outer rotor side surface 15a. It has a flat sliding guide surface 23 for dynamic guidance.
第1のカバー本体4aは、架橋フッ素樹脂24と金属体25とで形成されている。金属体25の材質としては、鋼材やアルミ合金を採用することができる。金属体25には、金属で形成された合わせ面22と、摺動案内面23に対応する領域を合わせ面22に対して軸方向に凹ませた凹部26とが設けられている。凹部26には架橋フッ素樹脂24が充填され、この架橋フッ素樹脂24によって、合わせ面22と同一平面上に摺動案内面23が形成されている。第2のカバー本体4bも、第1のカバー本体4aと同様に構成されている。
The first cover body 4a is formed of a crosslinked fluororesin 24 and a metal body 25. As the material of the metal body 25, a steel material or an aluminum alloy can be adopted. The metal body 25 is provided with a mating surface 22 made of metal and a recess 26 having a region corresponding to the sliding guide surface 23 recessed in the axial direction with respect to the mating surface 22. The recess 26 is filled with a crosslinked fluororesin 24, and the crosslinked fluororesin 24 forms a sliding guide surface 23 on the same plane as the mating surface 22. The second cover body 4b is also configured in the same manner as the first cover body 4a.
この回転ポンプも、上記各実施形態と同様に、第1のカバー本体4aおよび第2のカバー本体4bの摺動案内面23が架橋フッ素樹脂24で形成されているので、第1のカバー本体4aおよび第2のカバー本体4bとポンプロータ2との間のクリアランス(すなわち、第1のカバー本体4aの摺動案内面23と第2のカバー本体4bの摺動案内面23の間の内幅寸法と、インナーロータ7またはアウターロータ9の軸方向の幅寸法との差)をきわめて小さい大きさ(20μm以下、好ましくは15μm以下、より好ましくは10μm以下)に設定したときに、第1のカバー本体4aおよび第2のカバー本体4bとポンプロータ2との間の焼き付きを長期にわたって防止することが可能である。
In this rotary pump as well, as in each of the above embodiments, the sliding guide surface 23 of the first cover body 4a and the second cover body 4b is formed of the crosslinked fluororesin 24, so that the first cover body 4a And the clearance between the second cover body 4b and the pump rotor 2 (that is, the inner width dimension between the sliding guide surface 23 of the first cover body 4a and the sliding guide surface 23 of the second cover body 4b). When the difference between the inner rotor 7 and the outer rotor 9 in the axial width dimension) is set to an extremely small size (20 μm or less, preferably 15 μm or less, more preferably 10 μm or less), the first cover main body It is possible to prevent seizure between the 4a and the second cover body 4b and the pump rotor 2 for a long period of time.
また、この回転ポンプは、第1のカバー本体4aおよび第2のカバー本体4bのハウジング本体3への合わせ面22が、第1のカバー本体4aおよび第2のカバー本体4bを構成する金属体25に設けられているので、ボルト18の締め付け力を金属体25の部分で剛性をもって支持することができ、第1のカバー本体4aおよび第2のカバー本体4bの摺動案内面23の位置がボルト18の締め付け力で軸方向にずれるのを防止することができる。そのため、第1のカバー本体4aおよび第2のカバー本体4bをハウジング本体3にボルト18で固定したときに、第1のカバー本体4aおよび第2のカバー本体4bとポンプロータ2の間の軸方向のクリアランスを精度よく管理することが可能である。
Further, in this rotary pump, the mating surface 22 of the first cover body 4a and the second cover body 4b to the housing body 3 constitutes the first cover body 4a and the second cover body 4b. Since it is provided in, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the position of the sliding guide surface 23 of the first cover body 4a and the second cover body 4b is the bolt. The tightening force of 18 can prevent the displacement in the axial direction. Therefore, when the first cover body 4a and the second cover body 4b are fixed to the housing body 3 with bolts 18, the axial direction between the first cover body 4a and the second cover body 4b and the pump rotor 2 It is possible to manage the clearance of the housing accurately.
図12~図14に、本開示の第4実施形態にかかる回転ポンプを示す。第4実施形態は、ポンプロータ2の構成のみが第1実施形態と異なり、他の構成は第1実施形態と同じである。そのため、第1実施形態に対応する部分は同一の符号を付して説明を省略する。
12 to 14 show the rotary pump according to the fourth embodiment of the present disclosure. In the fourth embodiment, only the configuration of the pump rotor 2 is different from the first embodiment, and the other configurations are the same as those in the first embodiment. Therefore, the parts corresponding to the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
図12、図13に示すように、ポンプロータ2は、複数のベーン収容溝35を外周にもつロータ本体36と、複数のベーン収容溝35にそれぞれ径方向にスライド可能に収容された複数のベーン37とで構成されている。ベーン37の径方向外端は、ハウジング本体3に設けられたカムリング38の内周に摺接している。カムリング38の内部には、ポンプロータ2を回転可能に収容する開口10が形成されている。ロータ本体36の外周とカムリング38の内周との間には、ベーン37で区画される複数のチャンバ39(流体を収容する空間)が形成されている。カムリング38の内周は、ロータ本体36の回転に伴い各チャンバ39の容積が変化するように構成され、チャンバ39の容積が縮小することによる流体の吐出作用と、チャンバ39の容積が次第に拡大することによる流体の吸入作用とが生じるようになっている。
As shown in FIGS. 12 and 13, the pump rotor 2 has a rotor main body 36 having a plurality of vane accommodating grooves 35 on the outer periphery, and a plurality of vanes slidably accommodated in the plurality of vane accommodating grooves 35, respectively. It is composed of 37. The radial outer end of the vane 37 is in sliding contact with the inner circumference of the cam ring 38 provided in the housing body 3. Inside the cam ring 38, an opening 10 for rotatably accommodating the pump rotor 2 is formed. A plurality of chambers 39 (spaces for accommodating fluids) partitioned by vanes 37 are formed between the outer circumference of the rotor body 36 and the inner circumference of the cam ring 38. The inner circumference of the cam ring 38 is configured so that the volume of each chamber 39 changes as the rotor body 36 rotates, and the fluid discharge action due to the volume reduction of the chamber 39 and the volume of the chamber 39 gradually increase. As a result, the inhalation action of the fluid occurs.
図14に示すように、第1のサイドカバー5aは、ボルト18(図12参照)の締め付けにより第1のフランジ面21aに押して付けて固定される平らな合わせ面22と、ロータ本体36およびベーン37の軸方向を向く平らな側面を摺動案内する平らな摺動案内面23とを有する。第2のサイドカバー5bも、第1のサイドカバー5aと同様に構成されている。
As shown in FIG. 14, the first side cover 5a has a flat mating surface 22 that is pressed and fixed to the first flange surface 21a by tightening a bolt 18 (see FIG. 12), a rotor body 36, and a vane. It has a flat sliding guide surface 23 that slides and guides a flat side surface of 37 that faces the axial direction. The second side cover 5b is also configured in the same manner as the first side cover 5a.
また、カムリング38の内周に、架橋フッ素樹脂皮膜40がコーティングされている。ロータ本体36の軸方向幅寸法は、ベーン37の軸方向幅寸法と同一である。
Further, the inner circumference of the cam ring 38 is coated with a crosslinked fluororesin film 40. The axial width dimension of the rotor body 36 is the same as the axial width dimension of the vane 37.
この回転ポンプは、図12に示すように、第1のサイドカバー5aおよび第2のサイドカバー5bの摺動案内面23が架橋フッ素樹脂24で形成されているので、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間のクリアランス(すなわち、第1のサイドカバー5aの摺動案内面23と第2のサイドカバー5bの摺動案内面23の間の内幅寸法と、ロータ本体36およびベーン37の軸方向の幅寸法との差)をきわめて小さい大きさ(20μm以下、好ましくは15μm以下、より好ましくは10μm以下)に設定したときにも、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間の焼き付きを長期にわたって防止することが可能である。
In this rotary pump, as shown in FIG. 12, since the sliding guide surface 23 of the first side cover 5a and the second side cover 5b is formed of the crosslinked fluororesin 24, the first side cover 5a and the second side cover 5b The clearance between the second side cover 5b and the pump rotor 2 (that is, the inner width dimension between the sliding guide surface 23 of the first side cover 5a and the sliding guide surface 23 of the second side cover 5b). Even when the rotor body 36 and the vane 37 (difference from the axial width dimension) are set to an extremely small size (20 μm or less, preferably 15 μm or less, more preferably 10 μm or less), the first side cover 5a It is possible to prevent seizure between the second side cover 5b and the pump rotor 2 for a long period of time.
また、この回転ポンプは、第1のサイドカバー5aおよび第2のサイドカバー5bのハウジング本体3への合わせ面22が、第1のサイドカバー5aおよび第2のサイドカバー5bを構成する金属体25に設けられているので、ボルト18の締め付け力を金属体25の部分で剛性をもって支持することができ、第1のサイドカバー5aおよび第2のサイドカバー5bの摺動案内面23の位置がボルト18の締め付け力で軸方向にずれるのを防止することができる。そのため、第1のサイドカバー5aおよび第2のサイドカバー5bをハウジング本体3にボルト18で固定したときに、第1のサイドカバー5aおよび第2のサイドカバー5bとポンプロータ2との間の軸方向のクリアランスを精度よく管理することが可能である。
Further, in this rotary pump, the mating surface 22 of the first side cover 5a and the second side cover 5b with respect to the housing body 3 constitutes the first side cover 5a and the second side cover 5b. Since it is provided in, the tightening force of the bolt 18 can be supported by the portion of the metal body 25 with rigidity, and the position of the sliding guide surface 23 of the first side cover 5a and the second side cover 5b is the bolt. The tightening force of 18 can prevent the displacement in the axial direction. Therefore, when the first side cover 5a and the second side cover 5b are fixed to the housing body 3 with bolts 18, the shaft between the first side cover 5a and the second side cover 5b and the pump rotor 2 It is possible to accurately manage the clearance in the direction.
1 回転軸
2 ポンプロータ
3 ハウジング本体
4a 第1のカバー本体
4b 第2のカバー本体
5a 第1のサイドカバー
5b 第2のサイドカバー
6 外歯
7 インナーロータ
8 内歯
9 アウターロータ
10 開口
11 軸穴
12 外周円筒面
13 チャンバ
14a 第1のインナーロータ側面
14b 第2のインナーロータ側面
15a 第1のアウターロータ側面
15b 第2のアウターロータ側面
16a 第1の軸受
16b 第2の軸受
17 ボルト挿入穴
18 ボルト
19 ノックピン挿入穴
20 ノックピン
21a 第1のフランジ面
21b 第2のフランジ面
22 合わせ面
23 摺動案内面
24 架橋フッ素樹脂
25 金属体
26 凹部
30a 第1の吸入ポート
30b 第2の吸入ポート
31a 第1の吐出ポート
31b 第2の吐出ポート
32 連通路
33 吸入口
34 吐出口
35 ベーン収容溝
36 ロータ本体
37 ベーン
38 カムリング
39 チャンバ
40 架橋フッ素樹脂皮膜 1 Rotatingshaft 2 Pump rotor 3 Housing body 4a First cover body 4b Second cover body 5a First side cover 5b Second side cover 6 External teeth 7 Inner rotor 8 Internal teeth 9 Outer rotor 10 Opening 11 Shaft hole 12 Outer cylindrical surface 13 Chamber 14a First inner rotor side surface 14b Second inner rotor side surface 15a First outer rotor side surface 15b Second outer rotor side surface 16a First bearing 16b Second bearing 17 Bolt insertion hole 18 bolt 19 Knock pin insertion hole 20 Knock pin 21a First flange surface 21b Second flange surface 22 Alignment surface 23 Sliding guide surface 24 Cross-linked fluororesin 25 Metal body 26 Recess 30a First suction port 30b Second suction port 31a First Discharge port 31b Second discharge port 32 Continuous passage 33 Suction port 34 Discharge port 35 Vane accommodation groove 36 Rotor body 37 Vane 38 Cam ring 39 Chamber 40 Cross-linked fluororesin film
2 ポンプロータ
3 ハウジング本体
4a 第1のカバー本体
4b 第2のカバー本体
5a 第1のサイドカバー
5b 第2のサイドカバー
6 外歯
7 インナーロータ
8 内歯
9 アウターロータ
10 開口
11 軸穴
12 外周円筒面
13 チャンバ
14a 第1のインナーロータ側面
14b 第2のインナーロータ側面
15a 第1のアウターロータ側面
15b 第2のアウターロータ側面
16a 第1の軸受
16b 第2の軸受
17 ボルト挿入穴
18 ボルト
19 ノックピン挿入穴
20 ノックピン
21a 第1のフランジ面
21b 第2のフランジ面
22 合わせ面
23 摺動案内面
24 架橋フッ素樹脂
25 金属体
26 凹部
30a 第1の吸入ポート
30b 第2の吸入ポート
31a 第1の吐出ポート
31b 第2の吐出ポート
32 連通路
33 吸入口
34 吐出口
35 ベーン収容溝
36 ロータ本体
37 ベーン
38 カムリング
39 チャンバ
40 架橋フッ素樹脂皮膜 1 Rotating
Claims (6)
- 軸方向を向く平らなロータ側面をもつポンプロータと、
軸方向の開口と、その開口の周囲に形成された平らなフランジ面とを有し、前記ロータ側面と前記フランジ面とが同一平面上に揃うように前記ポンプロータを前記開口内に回転可能に収容するハウジング本体と、
ボルトの締め付けにより前記フランジ面に押して付けて固定される平らな合わせ面と、前記ロータ側面を摺動案内する平らな摺動案内面とを有するカバー部材と、を備える回転ポンプであって、
前記カバー部材が、架橋フッ素樹脂と金属体とで形成され、
前記金属体には、前記合わせ面と、前記摺動案内面に対応する領域を前記合わせ面に対して軸方向に凹ませた凹部とが設けられ、
前記架橋フッ素樹脂は、前記合わせ面と同一平面上に前記摺動案内面を形成するように前記凹部内に充填して設けられている、
回転ポンプ。 A pump rotor with a flat rotor side facing the axis,
It has an axial opening and a flat flange surface formed around the opening, and the pump rotor can be rotated into the opening so that the rotor side surface and the flange surface are aligned on the same plane. The housing body to be accommodated and
A rotary pump including a flat mating surface that is pressed and fixed to the flange surface by tightening a bolt, and a cover member having a flat sliding guide surface that slides and guides the side surface of the rotor.
The cover member is formed of a crosslinked fluororesin and a metal body, and is formed of a crosslinked fluororesin and a metal body.
The metal body is provided with the mating surface and a recess in which a region corresponding to the sliding guide surface is recessed in the axial direction with respect to the mating surface.
The crosslinked fluororesin is provided by filling the recess so as to form the sliding guide surface on the same plane as the mating surface.
Rotary pump. - 前記カバー部材は、前記ハウジング本体と、前記ハウジング本体の前記フランジ面と対向して配置されるカバー本体との間に挟み込んで固定される平板状のサイドカバーである請求項1に記載の回転ポンプ。 The rotary pump according to claim 1, wherein the cover member is a flat plate-shaped side cover that is sandwiched and fixed between the housing body and the cover body arranged so as to face the flange surface of the housing body. ..
- 前記凹部は、凹部に充填された架橋フッ素樹脂が前記開口の周囲を途切れずに連続する環状の領域で前記フランジ面に接触するように、前記合わせ面の一部に対応する領域も含めて軸方向に凹ませた形状をもつ請求項1または2に記載の回転ポンプ。 The recess includes a region corresponding to a part of the mating surface so that the crosslinked fluororesin filled in the recess contacts the flange surface in a continuous annular region around the opening. The rotary pump according to claim 1 or 2, which has a shape recessed in the direction.
- 前記合わせ面と前記摺動案内面は、十点平均粗さRzJIS6.3μm以下の面粗さをもつ一続きの仕上げ面とされている請求項1から3のいずれか1項に記載の回転ポンプ。 The aspect according to any one of claims 1 to 3, wherein the mating surface and the sliding guide surface are continuous finished surfaces having a surface roughness of 10-point average roughness Rz JIS 6.3 μm or less. Rotary pump.
- 前記ポンプロータが、複数の外歯を外周にもつインナーロータと、前記インナーロータの中心から偏心した位置を中心に回転可能に支持され、前記外歯に噛み合う複数の内歯を内周にもつ環状のアウターロータとで構成されている請求項1から4のいずれか1項に記載の回転ポンプ。 The pump rotor is rotatably supported around an inner rotor having a plurality of outer teeth on the outer circumference and a position eccentric from the center of the inner rotor, and has a plurality of internal teeth meshing with the outer teeth on the inner circumference. The rotary pump according to any one of claims 1 to 4, which is composed of the outer rotor of the above.
- 前記ポンプロータが、複数のベーン収容溝を外周にもつロータ本体と、前記複数のベーン収容溝にそれぞれ径方向にスライド可能に収容された複数のベーンとで構成されている請求項1から4のいずれか1項に記載の回転ポンプ。 Claims 1 to 4 wherein the pump rotor is composed of a rotor main body having a plurality of vane accommodating grooves on the outer periphery and a plurality of vanes slidably accommodated in the plurality of vane accommodating grooves. The rotary pump according to any one item.
Priority Applications (5)
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US17/774,151 US20220403841A1 (en) | 2019-12-24 | 2019-12-24 | Rotary pump |
JP2021566601A JPWO2021130858A1 (en) | 2019-12-24 | 2019-12-24 | |
DE112019008001.6T DE112019008001T5 (en) | 2019-12-24 | 2019-12-24 | rotary pump |
CN201980101633.2A CN114585815A (en) | 2019-12-24 | 2019-12-24 | Rotary pump |
PCT/JP2019/050625 WO2021130858A1 (en) | 2019-12-24 | 2019-12-24 | Rotary pump |
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PCT/JP2019/050625 WO2021130858A1 (en) | 2019-12-24 | 2019-12-24 | Rotary pump |
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PCT/JP2019/050625 WO2021130858A1 (en) | 2019-12-24 | 2019-12-24 | Rotary pump |
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JP (1) | JPWO2021130858A1 (en) |
CN (1) | CN114585815A (en) |
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Citations (3)
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JPS5622486U (en) * | 1979-07-27 | 1981-02-27 | ||
JP2014227899A (en) * | 2013-05-22 | 2014-12-08 | 住友電工焼結合金株式会社 | Oil pump |
JP2015137567A (en) * | 2014-01-21 | 2015-07-30 | 株式会社ショーワ | vane pump unit |
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US2754050A (en) * | 1950-04-22 | 1956-07-10 | Gen Motors Corp | Rotary blower |
JP2012062763A (en) * | 2010-09-14 | 2012-03-29 | Taiho Kogyo Co Ltd | Rotary type compressor |
JP6115817B2 (en) * | 2013-06-11 | 2017-04-19 | 住友電工ファインポリマー株式会社 | Positive displacement pump |
JP6413312B2 (en) * | 2014-04-16 | 2018-10-31 | 住友ベークライト株式会社 | Pump and resin composition |
DE112016004484T5 (en) * | 2015-09-30 | 2018-06-14 | Ntn Corporation | INTERNAL GEAR PUMP |
DE202018004820U1 (en) * | 2018-10-18 | 2018-11-19 | Doris Korthaus | Rotary lobe pump with wear elements for pumping solid media |
DE112019007997T5 (en) * | 2019-12-24 | 2022-10-13 | Sumitomo Electric Industries, Ltd. | rotary pump |
-
2019
- 2019-12-24 US US17/774,151 patent/US20220403841A1/en not_active Abandoned
- 2019-12-24 WO PCT/JP2019/050625 patent/WO2021130858A1/en active Application Filing
- 2019-12-24 JP JP2021566601A patent/JPWO2021130858A1/ja active Pending
- 2019-12-24 CN CN201980101633.2A patent/CN114585815A/en active Pending
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Publication number | Priority date | Publication date | Assignee | Title |
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JPS5622486U (en) * | 1979-07-27 | 1981-02-27 | ||
JP2014227899A (en) * | 2013-05-22 | 2014-12-08 | 住友電工焼結合金株式会社 | Oil pump |
JP2015137567A (en) * | 2014-01-21 | 2015-07-30 | 株式会社ショーワ | vane pump unit |
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JPWO2021130858A1 (en) | 2021-07-01 |
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