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WO2016006357A1 - Pompe à eau et procédé d'assemblage pour pompe à eau - Google Patents

Pompe à eau et procédé d'assemblage pour pompe à eau Download PDF

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Publication number
WO2016006357A1
WO2016006357A1 PCT/JP2015/065359 JP2015065359W WO2016006357A1 WO 2016006357 A1 WO2016006357 A1 WO 2016006357A1 JP 2015065359 W JP2015065359 W JP 2015065359W WO 2016006357 A1 WO2016006357 A1 WO 2016006357A1
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WO
WIPO (PCT)
Prior art keywords
drive shaft
water pump
impeller
cross
shape
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/065359
Other languages
English (en)
Japanese (ja)
Inventor
雄介 古澤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Priority to JP2016532494A priority Critical patent/JP6188942B2/ja
Priority to US15/316,938 priority patent/US20170114792A1/en
Priority to DE112015003163.4T priority patent/DE112015003163T5/de
Priority to CN201580033592.XA priority patent/CN106471255A/zh
Publication of WO2016006357A1 publication Critical patent/WO2016006357A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/36—Retaining components in desired mutual position by a form fit connection, e.g. by interlocking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/44—Resins

Definitions

  • the present invention relates to a water pump which is applied to, for example, an engine cooling system of a motor vehicle and is provided to circulate cooling water in the cooling system, and a method of assembling the water pump.
  • Patent Document 1 As a conventional water pump of this type, one described in Patent Document 1 below is known.
  • this water pump includes a pump housing having a pump chamber therein, a cylindrical drive shaft formed of a synthetic resin material, and rotatably supported in the pump chamber, and one end of the drive shaft.
  • a synthetic resin impeller provided at the other end of the drive shaft; and a mechanical seal interposed between the pump housing and the drive shaft to seal between the pump chamber and the ball bearing And.
  • the impeller and the drive shaft are the vibration of the inner peripheral surface of the insertion hole formed in a substantially circular shape in a horizontal cross section at the central position of the impeller and the outer peripheral surface of the other end of the drive shaft inserted in the insertion hole. It is integrally rotatably coupled by welding.
  • the impeller and the drive shaft are integrally rotatably coupled by vibration welding as described above, when the vibration welding is insufficient, the bonding strength of the welding surface is reduced. When the cooling water is pumped, the connection is separated, which may cause slippage or slippage between the impeller and the drive shaft.
  • the present invention has been made in view of the circumstances of the conventional water pump, and provides a water pump that can control slippage of the impeller relative to the drive shaft and dropout from the drive shaft.
  • a drive shaft is disposed in a pump housing and is formed by a synthetic resin material, and a pulley rotatably provided integrally with one end of the drive shaft and transmitting power from a drive source to rotate the drive shaft;
  • An impeller formed of a synthetic resin material and fitted to the other end of the drive shaft through a fitting hole, and the impeller is interposed between the other end of the drive shaft and the fitting hole of the impeller
  • a restricting portion is provided which restricts the axial maximum engagement position of the impeller, and the axial movement of the impeller in the maximum engagement position cooperates with the restriction portion on the tip end side of the other end of the drive shaft
  • the cross-sectional shape of the portion fitted to the impeller as a rotation restricting portion
  • the cross-sectional shape of the fitting hole is the other end It was formed as a rotation regulation part as well as the part of It is characterized.
  • the coupling force between the impeller and the drive shaft can be improved, and slippage of the impeller relative to the drive shaft and detachment from the drive shaft can be restricted.
  • FIG. 1 is a longitudinal cross-sectional view of the water pump in the 1st Embodiment of this invention. It is an exploded perspective view of a water pump in a 1st embodiment. It is an A arrow line view of FIG. (A) is an enlarged perspective view of a drive shaft provided in the first embodiment, and (B) is a sectional view taken along the line AA of (A).
  • A) is a perspective view which shows and shows the principal part of 1st Embodiment
  • (B) is an enlarged view of (A).
  • FIG. 1 It is a disassembled perspective view which shows the operation process at the time of assembling
  • (A) is an enlarged perspective view of a drive shaft provided in a second embodiment of the present invention, and (B) is a cross-sectional view taken along the line BB of (A).
  • (A) is an enlarged perspective view of a drive shaft provided in a third embodiment of the present invention, and (B) is a cross-sectional view taken along the line CC of (A).
  • (A) is an enlarged perspective view of a drive shaft provided in a fourth embodiment of the present invention, and (B) is a cross-sectional view taken along the line DD of (A).
  • (A) is an enlarged perspective view of a drive shaft provided in a fifth embodiment of the present invention, and (B) is a cross-sectional view taken along the line EE of (A).
  • the water pump 1 is applied to a cooling device for circulating antifreeze liquid (ethylene glycol), which is cooling water, between a radiator of an automobile and an internal combustion engine.
  • antifreeze liquid ethylene glycol
  • the water pump 1 is directly attached by bolting or the like to the side of a cylinder block of an internal combustion engine (not shown) and has a pump housing 3 having a pump chamber 3 in the front end on the cylinder block side.
  • a pulley 5 rotatably supported by a single ball bearing 4 as a bearing on the front end side of the pump housing 2, and a metal insert interposed between the pulley 5 and the ball bearing 4 6 and a drive shaft 7 which is disposed through the inside of the pump housing 2 and has one end side integrally formed with the pulley 5 and is fixed to the other end side of the drive shaft 7 so as to be rotatable in the pump chamber 3
  • a mechanical shaft that is interposed between the pump housing 2 and the drive shaft 7 to seal between the pump chamber 3 and the ball bearing 4.
  • the pump housing 2 is integrally formed of an aluminum alloy material, and the housing body 10 on the side of the pump chamber 3 is formed in a deformed annular ring, and a cylindrical portion with a step diameter on the rear end side of the housing body 10 It has 11 in one.
  • the housing body 10 is provided at its front end with a flat annular mounting surface 10a that abuts on a flat portion of the side of the cylinder block, and a mounting bolt screwed to the cylinder block is inserted around the outer periphery.
  • a plurality of bosses 10c in which the bolt holes 10b are formed are provided in a projecting manner.
  • a discharge port 10d for discharging the cooling water flowing into the pump chamber 3 from the suction port on the radiator side (not shown) into the water jacket in the cylinder block as the impeller 8 rotates. It is formed.
  • the cylindrical portion 11 has a large diameter cylindrical portion 11a on the side of the pump chamber 3, and a medium diameter cylindrical portion 11b extending in the direction of the ball bearing 4 from the large diameter cylindrical portion 11a. And a small diameter cylindrical portion 11c extending from the middle diameter cylindrical portion 11b to one end side of the drive shaft 7.
  • the middle diameter cylindrical portion 11 b is vertically formed with a drain hole 12 through which water droplets of cooling water leaked from the mechanical seal 9 flow downward on the lower side in the direction of gravity.
  • a drain chamber 13 for collecting and storing water droplets dropped from the drain hole 12 is formed across the inside of the large diameter cylindrical portion 11a.
  • a lower end opening of the drain chamber 13 is sealed in a liquid tight manner by a drain cap 14.
  • the ball bearing 4 is general, and as shown in FIG. 1 and FIG. 2, the inner ring 4a press-fitted into the small diameter cylindrical portion 11c, the outer ring 4b press-fitted into the insert 6, and the inner ring A plurality of balls 4c are provided so as to be rollable between a ring 4a and an outer ring 4b via a cage.
  • the maximum press-fit position of the inner ring 4 a in the axial direction is regulated by the front end face of the medium-diameter cylindrical portion 11 b of the cylindrical portion 11.
  • the axial position of the outer ring 4 b is set in advance by the press-fit length into the insert 6.
  • first and second seal members 15 and 16 are provided at the axial direction front and rear ends of the ball bearing 4 for preventing intrusion of dust etc. into the ball bearing 4.
  • the two seal members 15 and 16 are formed in a substantially annular shape, and are disposed to face each other in the axial direction of the ball bearing 4.
  • the first seal member 15 is fixed in a sandwiched state between the middle diameter cylindrical portion 11b and one end surface of the inner ring 4a.
  • the second seal member 16 is fixed in a sandwiched state between the second seal member 16 and the other end surface of the inner ring 4a by a retainer 17 which is a holding member.
  • the pulley 5 is integrally formed with the drive shaft 7 by a synthetic resin material containing a glass fiber 26 described later, as shown in FIGS. 1 and 2, from the one end side of the drive shaft 7 in the radial direction.
  • a flange wall 5a which is a disk-shaped end wall extending, a large diameter cylindrical base 5b bent in the axial direction of the drive shaft 7 from the outer peripheral edge of the flange wall 5a, and the cylindrical base 5b
  • the belt mounting portion 5c is provided to project from the outer peripheral surface.
  • through holes 18 for inserting a jig at the time of assembly are axially formed at substantially equally spaced positions in the circumferential direction.
  • the reinforcing rib 19 is integrally provided on the outer surface along the radial direction from the central position.
  • the cylindrical base 5 b is provided with the metal cylindrical insert 6 on the inner peripheral side.
  • the insert 6 comprises a cylindrical main body 6a and a flange portion 6b integrally formed at the end of the main body 6a, and the flange portion 6b is embedded in the cylindrical base portion 5b at the time of resin molding of the pulley 5 Fixed.
  • the belt mounting portion 5c is configured such that a rotational force is transmitted to the outer periphery formed in the shape of a corrugated tooth by a transmission belt wound around a drive pulley fixed to the tip end portion of a crankshaft not shown. .
  • the drive shaft 7 is formed in a cylindrical shape and a step shape by a synthetic resin material into which glass fibers 26 described later are compounded, and is integrally integrated with the center of the flange wall 5 a of the pulley 5 from the axial direction.
  • a large diameter shaft portion 7a which is one end coupled to the middle diameter shaft portion 7b which is the other end portion axially extended from the other end edge of the large diameter shaft portion 7a, and the middle diameter shaft portion It is comprised from the small diameter axial part 7c which is the other end similarly extended axially from the other end edge of 7b.
  • the drive shaft 7 has a tapered shape in which the diameter gradually decreases from the large diameter shaft portion 7a to the tip of the small diameter shaft portion 7c, that is, the rigidity of the large diameter shaft portion 7a which is a connecting portion with the pulley 5 is secured. It is formed in a shape that takes into consideration the draft when drawing out from the mold after injection molding.
  • the impeller 8 is fitted to the medium diameter shaft portion 7 b so as to straddle the small diameter shaft portion 7 c via a fitting hole 23 described later.
  • a part of the middle diameter shaft portion 7b (fitting portion 20), which is a fitting range with the fitting hole 23, has a cross section as a rotation restricting portion that restricts the relative rotation of the impeller 8 with respect to the drive shaft 7. It is formed in the non-perfect circle shape.
  • the fitting portion 20 of the outer peripheral surface from the substantially central position in the axial direction of the medium diameter shaft portion 7b to the end edge on the small diameter shaft portion 7c side.
  • a pair of recesses 21 is formed at a position of 180 ° in the circumferential direction.
  • the outer circumferential surface of each of the recesses 21 is formed as a curved surface, and the circumferential side edges thereof are connected to the outer circumferential surface of the middle diameter shaft portion 7 b with a gentle curved surface.
  • the fitting portion 20 of the middle diameter shaft portion 7b which is a fitting range with the fitting hole 23 has a non-perfect circle shape having a cross-sectional shape that is point-symmetrical and has a smooth uneven shape. It has a shape.
  • the small diameter shaft portion 7c has a role as a guide portion when the impeller 8 is assembled, and the tip end portion is formed to project from the front end side of the impeller 8 and the protruding portion 7d is formed.
  • a tapered surface 7e is formed at the tip end edge.
  • annular first step 22 that constitutes a part of the restricting portion is formed so as to be orthogonal to the axial direction at the connection point between the medium diameter shaft 7b and the small diameter shaft 7c. .
  • the impeller 8 is integrally formed of a synthetic resin material and, as shown in FIG. 1 to FIG. 3 and FIG. 6, has a substantially disc-like base 8a and a central portion of the base 8a It is comprised from the axial part 8b and the eight blade parts 8c radially formed from the outer peripheral surface of the axial part 8b in the front side of the said base 8a.
  • the base 8a is formed to a predetermined thickness and rotates with a gap on the back of the pump chamber 3, and as shown in FIG. 2, FIG. 3 and FIG. A pair of small diameter through holes 8d are bored at approximately the middle position, and the mechanical seal 9 is cooled by flowing cooling water to the back surface of the base 8a through the small diameter through holes 8d, 8d. The seizure due to the sliding friction between the mechanical seal 9 and the drive shaft 7 is suppressed.
  • a fitting hole 23 into which the other end of the drive shaft 7 is fitted is formed in a penetrating manner in the inner axial direction of the shaft portion 8b, and the fitting hole 23 is fitted to the drive shaft 7 A position corresponding to the fitting portion 20 of the medium diameter shaft portion 7b is formed in the large diameter fitting hole portion 23a as a rotation restricting portion having a cross sectional shape substantially the same as the cross sectional shape of the fitting portion 20 There is.
  • the inner peripheral surface shape of the large diameter fitting hole portion 23a is formed in the same cross section wedge shape
  • the impeller 8 is fitted across the medium diameter shaft 7 b and the small diameter shaft 7 c of the drive shaft 7.
  • the small diameter fitting hole 23b through which the small diameter shaft portion 7c of the fitting hole 23 is inserted is formed in a cylindrical shape following the outer peripheral surface shape of the small diameter shaft portion 7c.
  • the large diameter fitting hole portion 23a is formed to have a slightly larger diameter and a uniform inner diameter with respect to the maximum diameter of the fitting portion 20 having a downward tapered shape toward the tip end side of the drive shaft 7
  • the small diameter fitting hole 23b is formed to have a slightly larger diameter and a uniform inner diameter with respect to the maximum diameter of the small diameter shaft portion 7c, and the impeller 8 and the drive shaft 7 are separated It is designed to be mated.
  • annular second step portion 24 which constitutes a part of the regulating portion is formed.
  • the second step portion 24 is formed to be orthogonal to the axial direction, and when the impeller 8 is inserted into the drive shaft 7, the drive formed to be orthogonal to the axial direction as well. It abuts on the first step portion 22 on the side of the shaft 7 so that the axial movement on the side of the large diameter shaft portion 7a beyond that is restricted.
  • the impeller 8 is determined by the first stepped portion 22 and the second stepped portion 24 to determine the maximum fitting position with respect to the drive shaft 7, and the axial movement from here to the large diameter shaft portion 7a is performed. It is supposed to be regulated.
  • the small diameter shaft portion 7c is formed to project from the front surface side of the impeller 8, but it is fixed to the projecting portion 7d.
  • a metal push nut 25 which is a member is engaged.
  • the push nut 25 is formed in a thin disc shape, and an insertion hole 25a smaller in diameter than the small diameter shaft portion 7c of the drive shaft 7 is formed at the center position. It is done.
  • a plurality of claws 25c are formed on the push nut 25 via a plurality of cut-outs 25b cut out in the direction of the insertion hole 25a from the outer peripheral part, and the push nut 25 is disposed at the maximum push-in position. It fixes by making each tip edge of each nail
  • the mechanical seal 9 is a general one as shown in FIG. 1 and FIG. 2, and the cartridge portion 9 a is fixed to the inner peripheral surface of the medium diameter cylindrical portion 11 b of the cylindrical portion 11; A sleeve portion 9b supported on the outer peripheral surface of the medium diameter shaft portion 7b of the shaft 7, and a seal portion 9c provided between the inner peripheral side of the cartridge portion 9a and the outer peripheral side of the sleeve portion 9b It consists of
  • the said pulley 5 and the drive shaft 7 are integrally resin-molded by the metal mold
  • This synthetic resin material is injected from a position corresponding to the end face of the small diameter shaft 7c of the drive shaft 7 of the mold, and is axially inserted into the flange wall 5a of the pulley 5 of the large diameter shaft 7a. When it flows to the coupled position, it flows radially to the position of the outer peripheral edge of the belt mounting portion 5c of the pulley 5 in this radial direction, whereby the entire mold is filled.
  • the glass fiber 26 is oriented in the flow direction of the synthetic resin material in the vicinity of the portion which was in contact with the mold at the time of resin molding, that is, in the vicinity of the outer peripheral surface of the pulley 5 and the drive shaft 7
  • the glass fiber 26a inside is oriented along the circumferential direction, whereas the glass near the outer peripheral surface is The fibers 26b are oriented along the axial direction (see the arrow in FIG. 5 (B)).
  • the impeller 8 is moved from the tip end side of the small diameter shaft portion 7c of the drive shaft 7 along the axial direction while being fitted to the large diameter shaft portion 7a side.
  • the first step 22 on the seventh side and the second step 24 on the impeller 8 abut against each other (a maximum fitting position).
  • the impeller 8 is rotated with respect to the drive shaft 7, the impeller 8 is further pushed toward the large diameter shaft portion 7a, and it is confirmed whether the fitting between the fitting portion 20 and the large diameter fitting hole 23a is secure. .
  • the push nut 25 is engaged with each of the claws 25c at the projecting portion 7d of the small diameter shaft 7c which protrudes from the front side of the shaft 8b of the impeller 8 while maintaining the impeller 8 in the maximum fitting position. Is inserted while being elastically deformed in the radial direction, and pushed into the front end surface position of the shaft portion 8b of the protruding portion 7d.
  • the push nut 25 is engaged with the outer peripheral surface of the projecting portion 7d while the claws 25c are elastically deformed in the radial direction. Then, the tip end edge of each claw 25c bites into the outer peripheral surface of the projecting portion 7d by elastic force (restoration force) in the diameter reducing direction, so that the push nut 25 is fixed in axial position. ing.
  • the impeller 8 is fitted with a large diameter fitting portion of the impeller 8 with the fitting portion 20 of the medium diameter shaft portion 7b of the drive shaft 7 formed in a substantially wedge shape in cross section.
  • the relative rotation is restricted by the foraminous part 23 a, and the axial movement is restricted by the restricting part consisting of the first and second step parts 22 and 24 and the push nut 25. It is firmly assembled.
  • the impeller 8 is rotated via the drive shaft 7 integrally formed with the pulley 5.
  • the pump action is performed, and cooling water is pumped from the discharge port 10d to the water jacket of the engine to cool the entire internal combustion engine.
  • the impeller is formed by fitting the fitting portion 20 of the medium diameter shaft portion 7b formed in substantially the same cross section wedge shape with the large diameter fitting hole portion 23a of the impeller 8
  • the relative rotation with respect to the drive shaft 7 was restricted to improve the coupling strength to the force in the rotational direction, that is, the rotation stopping force.
  • the coupling strength between the drive shaft 7 and the impeller 8 is improved, the idle rotation of the impeller 8 with respect to the drive shaft 7 and the dropout from the drive shaft 7 can be reliably suppressed. .
  • the push nut 25 is made of metal and the drive shaft 7 is made of synthetic resin, the small diameter shaft portion 7c is in contact with the tip edge of each claw 25c of the push nut 25. It is necessary to take into consideration the possibility that the part is corroded by resin creep (aging deterioration), the push nut 25 is detached from the drive shaft 7, and the connection between the drive shaft 7 and the impeller 8 is released.
  • the push nut 25 and the small diameter shaft portion are formed by using the push nut 25 which is formed in a thin disk shape and is fixed in line contact or point contact with the small diameter shaft portion 7c.
  • the contact range with 7c was made very small. That is, even if the resin creep occurs on the contact surface of the small diameter shaft portion 7c with the push nut 25 and the push nut 25 moves to the tip end side of the drive shaft 7, the range is extremely narrow. Can be reduced to maintain the connection between the drive shaft 7 and the impeller 8.
  • the small diameter shaft portion 7c of the drive shaft 7 is formed to project from the front end side of the impeller 8, and the push nut 25 is positioned at the front end surface of the shaft portion 8b of the impeller 8 at the projecting portion 7d. Therefore, even if the resin creep occurs and the push nut 25 moves to the tip side of the small diameter shaft portion 7c, it is bitten into the moved end and fixed again, and the drive shaft 7 and the impeller 8 and Connection is maintained.
  • the cross-sectional shape (wedge shape) of the fitting portion 20 is formed into a smooth uneven shape having no corner portion (edge), stress compared to a shape having a corner portion Concentration is less likely to occur.
  • the cross-sectional shape of the fitting portion 20 is also point-symmetrical, stress concentration is unlikely to occur regardless of the rotational direction, and, for example, it flows by inertia immediately after the operation of the water pump 1 is stopped. Even in the case of receiving a rotational force in a direction reverse to the normal direction from the cooling water, stress concentration is less likely to occur in the fitting portion 20.
  • the fitting portion 20 is formed in a shape that avoids stress concentration, it is possible to effectively suppress the deformation, breakage or the like of the drive shaft 7 (the fitting portion 20).
  • the glass fiber 26 is contained in the inside of the drive shaft 7, but the glass fiber 26 has an effect of improving the rigidity against the force orthogonal to the oriented direction. There is. That is, since the glass fibers 26b in the vicinity of the outer peripheral surface of the drive shaft 7 are oriented along the axial direction, the rigidity (torsional rigidity) with respect to the rotation direction which is the orthogonal direction is improved.
  • the outer peripheral surface of the fitting portion 20 is all formed by a curved surface and the surface area is larger than the shape including the linear portion, the glass oriented in the direction orthogonal to the rotation direction Since the proportion of the fibers 26 b is increased, the torsional rigidity of the fitting portion 20 is further improved.
  • the assembly of the impeller 8 to the drive shaft 7 is entirely performed in the axial direction, the assembling workability is improved and the tip of the drive shaft 7 is stronger in the radial direction. Since no load is applied, the assembly operation can be performed without deforming the drive shaft 7.
  • FIG. 9 shows the second embodiment, and the basic configuration is the same as that of the first embodiment, but the fitting portion 20 of the medium diameter shaft portion 7b of the drive shaft 7 and the large diameter fitting hole of the impeller 8 The difference is that 23a is formed in a substantially elliptical shape in cross section.
  • FIG. 10 shows the third embodiment, and the basic configuration is the same as that of the first embodiment, but the fitting portion 20 of the medium diameter shaft portion 7b of the drive shaft 7 and the large diameter fitting hole of the impeller 8 The difference is that the cross section 23a is formed in a substantially oval shape in cross section.
  • fourth and fifth embodiments 11 and 12 show the fourth and fifth embodiments of the present invention, in which the fitting portion 20 of the medium diameter shaft portion 7b of the drive shaft 7 and the large diameter fitting hole portion 23a of the impeller 8 are cross sections. It is formed in a polygonal shape.
  • the fitting portion 20 and the large diameter fitting hole 23a are formed in a substantially hexagonal cross section.
  • the fitting portion 20 and the large diameter fitting hole 23a are formed in a substantially rectangular shape in cross section.
  • corner portions 27 edges
  • stress concentration is likely to occur in the vicinity of the corner portions 27 as compared with the first embodiment and the like. Since the corner portions 27 firmly engage with the inner peripheral surface of the large diameter fitting hole portion 23a, the idle rotation of the impeller 8 with respect to the drive shaft 7 can be further suppressed (FIG. 11 (B), FIG. 12 (B )reference). Each corner 27 is rounded to avoid excessive stress concentration.
  • the drive shaft 7 and the pulley 5 are described as being integrally formed, but they may be separately formed.
  • the first and second step portions 22 and 24 are used as the restricting portions for restricting the maximum fitting position of the impeller 8 with respect to the drive shaft 7.
  • the restricting portions are limited to the step portions. It is not something that can be done.
  • a fixing member is not restricted to this, For example, it is also possible to apply a snap ring.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention comprend un arbre d'entraînement (7) constitué en un matériau en résine synthétique, une poulie (5) disposée de façon à pouvoir tourner d'un seul tenant avec un côté partie d'arbre de grand diamètre (7a) de l'arbre d'entraînement, et une hélice (8) constituée en un matériau de résine synthétique et adaptée de façon à chevaucher une partie d'arbre intermédiaire (7b) et une partie d'arbre de petit diamètre (7c) à l'aide d'un trou d'adaptation (23), des première et seconde parties d'épaulement (22, 24) qui délimitent la position d'adaptation maximale de l'hélice dans la direction axiale étant disposées entre l'autre extrémité de l'arbre d'entraînement et le trou d'adaptation, un écrou capuchon (25), qui, de concert avec les première et seconde parties d'épaulement, restreint le mouvement de l'hélice (8) dans la direction axiale dans la position d'adaptation maximale étant disposé sur une saillie (7d) sur le côté de la surface avant d'hélice de l'arbre d'entraînement, la section transversale d'une partie d'adaptation (20) de la partie d'arbre intermédiaire présentant une forme de cocon, et la section transversale d'une partie d'ouverture d'adaptation de grand diamètre (23a) présentant la même forme de cocon que la partie d'adaptation (20). Par conséquent, la force d'accouplement entre l'hélice et l'arbre l'entraînement est améliorée, et il est possible de restreindre le glissement de l'hélice par rapport à l'arbre d'entraînement et son désaccouplement de l'arbre d'entraînement.
PCT/JP2015/065359 2014-07-09 2015-05-28 Pompe à eau et procédé d'assemblage pour pompe à eau Ceased WO2016006357A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2016532494A JP6188942B2 (ja) 2014-07-09 2015-05-28 ウォータポンプ及び該ウォータポンプの組立方法
US15/316,938 US20170114792A1 (en) 2014-07-09 2015-05-28 Water pump and assembly method for water pump
DE112015003163.4T DE112015003163T5 (de) 2014-07-09 2015-05-28 Wasserpumpe und Montageverfahren für eine Wasserpumpe
CN201580033592.XA CN106471255A (zh) 2014-07-09 2015-05-28 水泵以及该水泵的组装方法

Applications Claiming Priority (2)

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JP2014-140974 2014-07-09
JP2014140974 2014-07-09

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WO2016006357A1 true WO2016006357A1 (fr) 2016-01-14

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PCT/JP2015/065359 Ceased WO2016006357A1 (fr) 2014-07-09 2015-05-28 Pompe à eau et procédé d'assemblage pour pompe à eau

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JP (1) JP6188942B2 (fr)
CN (1) CN106471255A (fr)
DE (1) DE112015003163T5 (fr)
WO (1) WO2016006357A1 (fr)

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IT201800007110A1 (it) * 2018-07-11 2020-01-11 Pompa per circuito di raffreddamento di motore per veicolo.

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JP6188942B2 (ja) 2017-08-30
US20170114792A1 (en) 2017-04-27
DE112015003163T5 (de) 2017-04-20
CN106471255A (zh) 2017-03-01
JPWO2016006357A1 (ja) 2017-04-27

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