WO2015040973A1 - Pompe à eau - Google Patents

Pompe à eau Download PDF

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Publication number
WO2015040973A1
WO2015040973A1 PCT/JP2014/070813 JP2014070813W WO2015040973A1 WO 2015040973 A1 WO2015040973 A1 WO 2015040973A1 JP 2014070813 W JP2014070813 W JP 2014070813W WO 2015040973 A1 WO2015040973 A1 WO 2015040973A1
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WO
WIPO (PCT)
Prior art keywords
water pump
impeller
pump according
sub
control member
Prior art date
Application number
PCT/JP2014/070813
Other languages
English (en)
Japanese (ja)
Inventor
猛 吉村
淳一郎 鬼形
Original Assignee
日立オートモティブシステムズ株式会社
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 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2015537598A priority Critical patent/JP6096308B2/ja
Publication of WO2015040973A1 publication Critical patent/WO2015040973A1/fr

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    • 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
    • F04D13/12—Combinations of two or more 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
    • F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs

Definitions

  • the present invention relates to a water pump used for supplying cooling water for cooling an engine into the engine, for example.
  • a drive shaft that is rotatably supported in a pump housing, a main impeller integrally formed at the tip of the drive shaft, and a secondary shaft that is fitted to the drive shaft so as to be relatively rotatable.
  • An impeller is interposed between the main impeller and the sub impeller, and connects the main impeller and the sub impeller when the temperature is equal to or higher than a predetermined temperature, while the sub impeller is connected to the main impeller when the temperature is lower than the predetermined temperature.
  • a clutch mechanism for separating is interposed between the main impeller and the sub impeller, and connects the main impeller and the sub impeller when the temperature is equal to or higher than a predetermined temperature, while the sub impeller is connected to the main impeller when the temperature is lower than the predetermined temperature.
  • the clutch mechanism cuts off the connection between the main impeller and the sub impeller for a certain time after the low temperature start of the internal combustion engine to improve the warm-up performance, and connects the main impeller and the sub impeller after the warm-up is completed. Then, cooling of the engine is started.
  • the outer diameter of the main impeller is increased and the pump chamber is also inevitably arranged because the sub impeller is arranged in the radial direction so that the main impeller is held inside. Will increase in the radial direction. As a result, the outer diameter of the pump housing is increased, and the water pump as a whole must be enlarged.
  • the present invention was devised in view of the actual situation of the conventional water pump, and aims to reduce the size of a water pump including a main impeller and a sub-impeller and to improve the mountability to an engine. .
  • the rotational force is transmitted from one end side, the other end side is inserted into the pump chamber, and the pump chamber is accommodated in the other end side of the drive shaft.
  • a main impeller provided so as to be able to be intermittently connected via the main impeller, and a sub-impeller provided so as to be integrally rotatable on the tip side of the drive shaft with respect to the main impeller and having a smaller diameter than the main impeller. It is characterized by.
  • the water pump can be reduced in size by providing the sub-impeller on the front end side in the axial direction from the main impeller of the drive shaft.
  • FIG. 1 It is a longitudinal section showing a 1st embodiment of a water pump concerning the present invention. It is a disassembled perspective view of the water pump of this embodiment.
  • the secondary impeller provided for this embodiment is shown, A is a perspective view and B is a front view.
  • the secondary impeller provided to this embodiment is shown, A is a side view and B is a front view.
  • the secondary impeller used for this embodiment is shown, A is a front view and B is a side view.
  • the water pump 1 is applied to a cooling device that circulates an antifreeze liquid (ethylene glycol) that is cooling water between a radiator of an automobile and an engine.
  • an antifreeze liquid ethylene glycol
  • the water pump 1 is directly attached to the side portion of the cylinder block 01 of the internal combustion engine by a plurality of mounting bolts 28, and cooperates with the front end recessed groove on the cylinder block 01 side.
  • the pump housing 2 in which the pump chamber 3 is formed, the pulley 4 rotatably supported by a single ball bearing 5 on the rear end side of the pump housing 2, and the pump housing 2 are inserted into the pump housing 2.
  • a drive shaft 6 having one end integrally connected to the pulley 4, a main impeller 7 fixed to the other end of the drive shaft 6 and rotatably accommodated in the pump chamber 3, It is mainly composed of a mechanical seal 8 interposed between the pump housing 2 and the drive shaft 6 and sealing between the pump chamber 3 and the ball bearing 5.
  • the cylinder block 01 is formed with an introduction passage 03 for introducing cooling water from the radiator side (not shown) in the outer portion on the water pump 1 side.
  • the introduction passage 03 communicates with the pump chamber 3 from the direction perpendicular to the axis and has a uniform passage inner diameter.
  • the pump housing 2 is integrally formed of an aluminum alloy material, a housing body 9 is formed in a deformed annular shape on the pump chamber 3 side, and a step-shaped cylindrical portion is formed on the rear end side of the housing body 9. 10 are integrated.
  • the housing body 9 is formed with a flat annular mounting surface 9a at the front end that abuts against a flat surface provided on the side of the cylinder block 01, and a mounting bolt 28 screwed and fixed to the cylinder block 01 on the outer periphery.
  • a plurality of boss portions 9c constituting a bolt hole 9b through which is inserted.
  • a discharge port 9d is formed in the housing body 9 for discharging the cooling water flowing into the pump chamber 3 from the introduction passage 03 into the water jacket (not shown) as the main impeller 7 rotates.
  • a part of the discharge port 9d is formed between a recess formed on the outer surface of the front end of the cylinder block 01.
  • the cylindrical portion 10 includes a large-diameter portion 10a on the pump chamber 3 side, a medium-diameter portion 10b extending from the large-diameter portion 10a toward the ball bearing 5, and the medium-diameter portion.
  • the small-diameter portion 10c extends from 10b toward the large-diameter shaft portion of the drive shaft 6.
  • the middle diameter portion 10b is formed with an annular space chamber 11 into which water droplets of cooling water leaked from the mechanical seal 8 are introduced below the gravity direction, and below the annular space chamber 11, A drain chamber (not shown) for collecting and storing water droplets dropped from the annular space chamber 11 is formed.
  • the pulley 4 is integrally formed in a disc shape made of synthetic resin, and is driven from a central fixing portion 4a in which the drive shaft 6 is coupled by insert molding at the center, and an axial front end edge of the central fixing portion 4a.
  • a disc-shaped flange wall 4b extending in the radial direction of the shaft 6, a large-diameter cylindrical portion 4c bent in the axial direction of the drive shaft 6 from the outer peripheral edge of the flange wall 4b, and the cylindrical portion 4c It is comprised from the belt mounting part 4d protrudingly provided by the outer peripheral surface.
  • an outer ring 5b of the ball bearing 5 is press-fitted and fixed to an inner peripheral surface via a metal cylindrical insert 12.
  • a transmission belt wound around a driving pulley fixed to a distal end portion of a crankshaft (not shown) is wound around an outer periphery formed in a wave shape so that a rotational force is transmitted. It has become.
  • the ball bearing 5 is a general one, and an inner ring 5a press-fitted into the outer peripheral surface of the small-diameter portion 10c of the cylindrical portion 10, the outer ring 5b press-fitted into the inner periphery of the insert 12, and the inner ring It is comprised from the some ball
  • the shielding plate 13 is disposed so as to cover the rear end edge side of the ball bearing 5 so as to prevent dust from the outside from entering the ball bearing 5.
  • the drive shaft 6 is made of a metal material, and as shown in FIGS. 1 and 2, a large-diameter shaft portion 6a formed on one end of the pulley 4 side, and the large-diameter shaft portion 6a.
  • the step 6c is formed in a small diameter shape up to the portion 6c.
  • annular groove 6d is formed on the outer periphery of the distal end of the large-diameter shaft portion 6a on the pulley 4 side.
  • the annular groove 6d allows water droplets cut at the edge of the groove to pass from the annular space chamber 11 to the annular space chamber 11. It is made to drip into the storage chamber outside the figure provided in the lower part of the.
  • a drive ring 14 is press-fitted and fixed from the axial direction on the outer peripheral surface of the portion connected to the small-diameter shaft portion 6c of the medium-diameter shaft portion 6b.
  • the drive ring 14 is integrally formed of a metal material, and is formed integrally with a cylindrical main body 14a that is press-fitted and fixed to the outer peripheral surface of the medium-diameter shaft portion 6b from the axial direction, and a front end of the cylindrical main body 14a. It is comprised from the control flange part 14b.
  • the cylindrical main body 14a has an inner diameter slightly smaller than the outer diameter of the medium diameter shaft portion 6b, and is press-fitted into the medium diameter shaft portion 6b.
  • the regulation flange portion 14b is integrally formed with an annular convex portion (step portion) 14c having a small step diameter on one side surface of the cylindrical main body 14a.
  • the small-diameter shaft portion 6c extends relatively long in the axial direction, and a bearing portion 15 (underwater bearing) is rotatably provided on the outer periphery of a substantially central portion in the axial direction.
  • the bearing portion 15 is integrally formed of a carbon material and has an axial length that is set shorter than the axial length of the small-diameter shaft portion 6c.
  • the drive ring may be formed integrally with the drive shaft 6.
  • a cylindrical driven ring 16 is press-fitted and fixed to the outer periphery of the bearing portion 15.
  • the driven ring 16 includes a cylindrical ring body 16a integrally formed of stainless steel, a flange portion 16b integrally provided at one end in the axial direction of the ring body 16a opposite to the drive ring 14, It is mainly composed of a plurality of projecting portions 16c provided integrally at equal circumferential positions on the inner side surface of the flange portion 16b.
  • the follower ring 16 is configured such that the entire length in the axial direction including the flange portion 16 b is set substantially the same as the axial length of the bearing portion 15, and the inner diameter is slightly smaller than the outer diameter of the bearing portion 15. It is formed small and the press-fitting allowance is secured.
  • the ring main body 16a is slidable from the axial direction on the opposed surface of the cylindrical main body 14a of the drive ring 14 facing the other end surface in the axial direction, or opposed with a slight gap, and has an outer diameter.
  • a locking groove 16d for locking and fixing one end 20a of a clutch spring 20 described later is formed between the protrusions 16c of the flange portion 16b.
  • the driven ring 16 may be formed integrally with the main impeller 7.
  • the main impeller 7 is integrally formed of an aluminum alloy material. As shown in FIGS. 1 and 2, the main impeller 7 is formed in a substantially disk-like base portion 7a and radially on the front outer peripheral side of the base portion 7a from the center side. It is mainly composed of six blade portions 7b.
  • the main impeller 7 is disposed on the outer peripheral side of the small-diameter shaft portion 6c of the drive shaft 6 via a bearing portion (underwater bearing) 15 and a driven ring 16, and a cylindrical holding hole 7c is formed in the center of the base portion 7a in the axial direction. It is formed to penetrate.
  • the holding hole 7c is formed to have a relatively large diameter, and has an axial length in which about 2/3 of the driven ring 16 is accommodated.
  • the edge of the holding hole 7c is fixed by caulking to a portion in the vicinity of the flange portion 16b of the driven ring 16. Therefore, the main impeller 7 rotates integrally with the bearing portion 15 via the driven ring 16 and rotates relative to the drive shaft 6. Further, the holding hole 7c is configured to fit and hold a control member 21 described later on the inner periphery.
  • the sub-impeller 32 is press-fitted and fixed to the tip of the small-diameter shaft portion 6c of the drive shaft 6.
  • This sub-impeller 32 is a so-called axial flow type, and is disposed at a position facing the pump chamber 3 in the introduction passage 03 as shown in FIGS. 1, 3A, and B, and is integrally formed of a synthetic resin material.
  • a substantially cylindrical base portion 32a extending in the axial direction, six blade portions 32b projecting radially from the outer peripheral surface of the tip portion of the base portion 32a, and an outer edge of each blade portion 32b are integrated. It is mainly comprised from the annular part 32c provided in.
  • the base portion 32a has a solid inner end, but is formed with a press-fit hole 32e into which the distal end portion of the small-diameter shaft portion 6c of the drive shaft 6 is press-fitted in the inner axial direction of the rear end portion 32d. .
  • the press-fitting hole 32e is formed from the rear end surface of the rear end part 32d to a predetermined length in the direction of the internal axis, and has an inner diameter slightly smaller than the outer diameter of the small-diameter shaft part 6c to form a press-fitting allowance. Has been.
  • Each of the blade portions 32b is disposed on the outer peripheral surface of the base portion 32a at a position of about 60 ° in the circumferential direction, and each blade portion 32b is formed in a flat plate shape, and in order to obtain a water flow from the front end side to the rear end side. Inclined in the same direction. Further, the outer diameter of the annular portion 32 c is formed smaller than the inner diameter of the introduction passage 03, and a predetermined gap S is formed between the outer peripheral edge and the inner peripheral surface of the introduction passage 03.
  • a metal disk-shaped holding plate 17 is interposed as shown in FIGS.
  • the holding plate 17 is formed with a press-fitting hole 17a into which the small-diameter shaft portion 6c is press-fitted at the center, and an outer diameter is formed slightly larger than the outer diameter in the driven ring 16, and the bearing is formed on the outer peripheral side. The axial movement of the portion 15 and the driven ring 16 is restricted.
  • a clutch mechanism is provided on both outer peripheral sides of the cylindrical main body 14a of the drive ring 14 and the ring main body 16a of the driven ring 16.
  • the clutch mechanism includes a clutch spring 20 disposed on both outer circumferential sides of the drive ring 14 and the driven ring 16, and a clutch spring 20 disposed on the outer circumferential side of the clutch spring 20.
  • the clutch spring 20 is disposed on the drive ring 14 and the driven ring 16.
  • the control member 21 that controls the connection and the rotation limiting mechanism 22 that controls the rotation of the control member 21 are configured.
  • the clutch spring 20 is formed in a long coil shape in the axial direction, wound around the outer peripheral surfaces of the cylindrical main body 14a and the ring main body 16a from the axial direction, and has a spring force in a direction in which the diameter is always reduced.
  • the drive ring 14 and the driven ring 16 are connected by acting.
  • the clutch spring 20 has one end portion 20a bent in the axial direction and fixed to the locking groove 16d of the driven ring 16, and the other end portion 20b bent in the radial direction. Is engaged and fixed in an engagement groove 21 c formed on one end side in the axial direction of the control member 21.
  • the control member 21 includes a main body 21a formed in a substantially cylindrical shape, and a pair of arm portions 21b and 21b formed in radially symmetric positions on the outer peripheral surface of the main body 21a. And the inner peripheral surface of the main body 21a is arranged so as to cover the outer peripheral surface of the clutch spring 20 with a slight gap.
  • the main body 21a is set to have a predetermined length along the axial direction, has an outer diameter slightly smaller than the inner diameter of the holding hole 7c of the main impeller 7, and one end portion in the axial direction has the holding hole 7c. The other end is slidably fitted to the outer peripheral surface of the annular convex portion 14c.
  • control member 21 is not fixed to any member, and one end portion of the main body 21a is slidably fitted to the inner peripheral surface of the holding hole 7c, and the other end portion Is slidably fitted and held on the outer peripheral surface of the annular convex portion 14c.
  • the other end is in contact with the inner surface of the restriction flange portion 14b from the axial direction.
  • an engaging groove 21c formed in a substantially U-shape is cut out along the axial direction at the other end.
  • the two arm portions 21b and 21b are fixed base portions fixed at substantially the center position in the axial direction of the outer peripheral surface of the main body 21a, and project from the fixed base portions in the radial direction and bent in the axial direction so that the mechanical seal 8
  • the both arm portions 21b which are configured from the distal end portion extending to the outer peripheral position, have an outer peripheral surface formed in a circular arc shape along the circumferential direction of the main body 21a.
  • the control member 21 is configured to rotate integrally with the driven ring 16 and the bearing portion 15 via one end portion 20 a of the clutch spring 20, and the rotation limiting mechanism provided in the pump housing 2.
  • the rotation is appropriately limited (restricted) by 22, and the clutch spring 20 is expanded and deformed by this limiting action.
  • the rotation limiting mechanism 22 is constituted by an electromagnetic solenoid, and is accommodated and fixed in a holding hole 2a formed in a side portion of the pump housing 2 on the large diameter portion 10a side. 23 and a solenoid portion 24 provided on the rear end side of the solenoid body 23.
  • the solenoid body 23 is formed in a substantially cylindrical shape and is housed and held in a liquid-tight droplet in the holding hole 2a via a seal ring 34 that is fixed to the outer peripheral sealing groove.
  • a sliding hole 23a that is continuous with the through hole 2b formed in the pump housing 2 is formed in a substantially central position.
  • the solenoid portion 24 includes an electromagnetic coil, a fixed core, a movable plunger 25 and the like housed in a casing, and a push rod 26 fixed to the movable plunger 25 is provided at the tip.
  • a connector portion 24 a that is electrically connected to an electronic controller described later is integrally provided at the outer end portion of the solenoid portion 24.
  • the push rod 26 has a base end portion fixed to the movable plunger, and a tip end portion that is freely inserted into the sliding hole 23a and the through hole 2b and can be moved back and forth in the direction of the arm portion 21b of the control member 21. Is provided. That is, when the push rod 26 is energized to the electromagnetic coil, the push rod 26 moves forward via the movable plunger, and the tip end portion comes into contact with one side surface of the one arm portion 21b from the radial direction to control the push rod 26.
  • the electromagnetic coil of the solenoid unit 24 is configured such that a control current is supplied or cut off from an electronic controller (not shown).
  • This electronic controller detects the current engine state based on information signals from a crank angle sensor, an air flow meter, an engine water temperature sensor, etc., and controls various devices such as a fuel injection valve.
  • a control current is supplied to or cut off from the electromagnetic coil of the solenoid unit 24 so that the clutch spring 20 is deformed or expanded through the control member 21. It has become.
  • the main impeller 7 is a through-hole 2 that guides the cooling water supplied into the pump chamber 3 to the back of the main impeller 7 (in the direction of the mechanical seal 8) at a position facing the substantially axial direction of the clutch spring 20 of the main impeller 7.
  • Two water guide holes 30 are formed.
  • the water guide hole 30 is formed at a substantially symmetrical position substantially in the radial center of the base portion 7a of the main impeller 7, and communicates with the annular clearance on the outer peripheral side of the clutch spring 20 from the axial direction.
  • the control member 21 communicates with the control member 21 from the axial direction.
  • the electronic controller energizes and energizes the electromagnetic coil of the solenoid unit 24 by an information signal from the engine water temperature sensor. Then, the push rod 26 advances against the spring force of the coil spring 27 through the movable plunger, and the push rod tip portion comes into contact with the side surface of the tip portion of one arm portion 21b of the control member 21 from the radial direction. Thus, the rotation of the control member 21 is limited.
  • the clutch spring 20 is deformed in the diameter increasing direction via the other end 20 b of the clutch spring 20, so that the inner peripheral surface of the clutch spring 20 is separated from the outer peripheral surfaces of the drive ring 14 and the driven ring 16.
  • the connection of both 14 and 16 is cut apart. Accordingly, the drive ring 14 continues to rotate integrally with the drive shaft 6 as it is, but since the driven ring 16 stops rotating, the main impeller 7 also stops rotating.
  • the water temperature sensor that detects the engine temperature cuts off the energization of the solenoid coil of the solenoid unit 24 from the electronic controller. For this reason, since the push rod 26 is retracted by the spring force of the coil spring 27, the contact with the arm portion 21b is released, and the control member 21 is allowed to freely rotate.
  • the clutch spring 20 is restored to its original shape by its reduced diameter deformation force, and the drive ring 14 and the driven ring 16 are tightened to connect the both 14 and 16 together. Therefore, the main impeller 7 rotates integrally with the rotational force of the drive shaft 6 to perform a pump action, and as shown by the arrow in FIG. Since the water is supplied from the discharge port 9d into the water jacket, the engine can be efficiently cooled.
  • the high-pressure cooling water in the pump chamber 3 passes through the water guide holes 30 and a part of the annular coolant on the outer surface of the control member 21 and the outer periphery of the clutch spring 20 as shown by the arrows in FIG. It flows into the gap or the like, flows in the direction of the mechanical seal 8 as it is, and returns from here to the pump chamber 3.
  • the sleeve portion of the mechanical seal 8 is positively cooled by the cooling water flowing in the direction of the mechanical seal 8, and seizure due to sliding friction with the drive shaft 6 can be effectively suppressed.
  • the clutches are connected from the respective water guide holes 30. Since the cooling water is forcibly supplied to the spring 20 and the vicinity thereof, the friction powder and the like due to the operation of the clutch spring 20 is washed away, and the adhesion of the friction powder is eliminated.
  • the main impeller 7 does not rotate, but the sub impeller 32 rotates and the flow of cooling water is ensured slightly, so that the malfunction of the water temperature sensor provided in the engine is suppressed. can do. That is, for example, if the cooling does not flow at all in the water jacket and stagnates, the water temperature sensor may malfunction and the engine may overheat. However, if it is flowing slightly in the water jacket, the malfunction of the water temperature sensor is avoided and normal operation is maintained, so that the occurrence of engine overheating can be suppressed.
  • the secondary impeller 32 is provided at the tip of the small diameter shaft portion 6c of the drive shaft 6 that is spaced forward from the main impeller 7, so There is no need to increase the outer diameter of the impeller 7. Therefore, even if the auxiliary impeller 32 is provided, the enlargement of the outer diameter of the water pump 1 is suppressed, and it becomes possible to reduce the size.
  • the cooling water always flows in the direction of the main impeller 7 along with the rotation of the sub impeller 32 and a predetermined pressure is maintained in the pump chamber 3, even if the rotation of the main impeller 7 starts, the low pressure portion Since the generation of a large differential pressure between the high pressure portion and the high pressure portion can be suppressed, the generation of cavitation can be suppressed. From this point, the pump efficiency can be improved.
  • the water pump 1 can be downsized in this respect as well.
  • one end portion of the control member 21 is slidably fitted and held by the inner peripheral surface of the holding hole 7c, and the other end portion is set by the outer peripheral surface of the annular convex portion 14c. It is slidably fitted and held. Accordingly, the control member 21 is positioned in the radial direction by being slidably held on the inner peripheral surface of the holding hole 7c and the outer peripheral surface of the annular convex portion 14c. Further, since the other end is in contact with the inner surface of the restriction flange portion 14b, the axial positioning is performed.
  • FIG. 4 shows the second embodiment, and the basic configuration is the same as that of the first embodiment, except that the sub-impeller 31 is a mixed flow type.
  • the sub impeller 31 is disposed at a position facing the pump chamber 3 in the introduction passage 03, and is integrally formed of a synthetic resin material and has a tapered tip. It is mainly composed of a substantially conical base portion 31a extending in the axial direction and six blade portions 31b integrally provided on the tapered outer peripheral surface of the base portion 31a.
  • the base portion 31a has a tip surface 31d formed in a spherical shape to reduce the flow resistance of the cooling water, and has a cylindrical projection 31c integrally formed at the rear end portion of the enlarged diameter.
  • a press-fitting hole 31e is formed in the axial direction in which the tip of the small-diameter shaft portion 6c of the drive shaft 6 is press-fitted.
  • the press-fitting hole 31e is formed to a predetermined length from the rear end surface of the protrusion 31c in the direction of the internal axis, and the inner diameter is slightly smaller than the outer diameter of the small-diameter shaft part 6c to form a press-fitting allowance. ing.
  • Each of the blade portions 31b is disposed on the outer peripheral surface of the base portion 31a at a position of about 60 ° in the circumferential direction, and is formed in an inclined diameter increasing shape from the front end portion to the rear end portion of the base portion 31a. It has a torsional shape so that it can be hung on the rear end side to obtain a water flow. Further, the outer diameter of each blade 31b is formed smaller than the inner diameter of the introduction passage 03, and a predetermined gap S is formed between the outer peripheral edge and the inner peripheral surface of the introduction passage 03.
  • the pumping action accompanying the constant rotation of the sub impeller 31 can provide the same effects as the first embodiment.
  • the sub impeller 31 is a mixed flow type.
  • the drawability of the cooling water into the pump chamber 3 is enhanced, so that the supercharging action of the main impeller 7 is improved and the generation of cavitation can be further suppressed.
  • FIG. 6 shows a third embodiment in which the secondary impeller 19 is a centrifugal type. That is, the sub-impeller 19 is integrally formed of a synthetic resin material, and is disposed at a position facing the pump chamber 3 of the introduction passage 03 as shown in FIG. 6, and as shown in FIGS. It is mainly composed of a substantially streamlined base portion 19a and six blade portions 19b protruding radially from the outer peripheral surface of the base portion 19a.
  • the base portion 19a has a front end surface 19e formed in a spherical shape in order to reduce the flow resistance of the cooling water, and has a cylindrical protrusion 19c integrally formed at the rear end portion in the inner axial direction.
  • a press-fitting hole 19d into which the tip of the small-diameter shaft portion 6c of the drive shaft 6 is press-fitted is formed.
  • the press-fitting hole 19d is formed from the rear end surface of the protrusion 19c to a predetermined length in the direction of the internal axis, and has an inner diameter slightly smaller than the outer diameter of the small-diameter shaft part 6c to form a press-fitting allowance. ing.
  • Each of the blade portions 19b is disposed on the outer peripheral surface of the base portion 19a at a position of about 60 ° in the circumferential direction, and is bent in a curved shape so that the substantially central portion in the radial direction becomes the maximum concave portion, and the outer diameter is A predetermined gap S is formed between the outer peripheral edge and the inner peripheral surface of the introduction passage 03, which is smaller than the inner diameter of the introduction passage 03.
  • the sub-impeller is a water pump characterized in that the blade portion is disposed across the introduction passage and the pump chamber.
  • the auxiliary impeller is provided on the tip end side of the drive shaft, it is not necessary to increase the axial length of the entire water pump, and the flow of the cooling water generated by the auxiliary impeller is transmitted to the main impeller. Therefore, the pump efficiency can be improved by the supercharging effect.
  • the water pump according to claim b The sub impeller is a water pump characterized in that all of the blade portions are accommodated in an introduction passage.
  • the water pump according to claim 1 The sub-impeller is an axial flow type that forms an axial flow with rotation, and is a water pump.
  • the auxiliary impeller By making the auxiliary impeller an axial flow type, the cooling water sucked by the auxiliary impeller can be flowed to the main impeller, so that the pump efficiency can be improved and the occurrence of cavitation can be suppressed.
  • the water pump according to claim a The sub-impeller is a centrifugal pump.
  • the axial flow is not generated, but the flow can be generated, so that the pump driving of the main impeller can be assisted.
  • the sub-impeller is a mixed flow type that forms a mixed flow with rotation.
  • the flow of the cooling water discharged from the blades is on the conical surface with the center of the drive shaft as the axis, so that the supercharging effect of the rotation of the main impeller can be exhibited as it is, so that the pump The efficiency can be greatly improved and the occurrence of cavitation can be suppressed.
  • the water pump according to claim d The water pump is characterized in that the sub-impeller is accommodated in an introduction passage.
  • the water pump is characterized in that the control member is slidably held by a holding portion provided on the drive ring or the impeller.
  • the sub-impeller is integrally formed of a resin, and is constituted by a conical base portion at the center portion and a plurality of blade portions provided on the outer peripheral side of the base portion. .
  • the shape of the sub impeller can be freely set by resin molding.
  • the water pump is characterized in that the control member is made of an iron-based metal.
  • the control member is not deteriorated by heat. If the impeller is also an iron-based metal, the clearance of fitting does not change because the linear expansion coefficient is close. (Claim k)
  • the holding portion is constituted by a bearing installed on the drive ring or the main impeller.
  • the resin impeller has an effect of suppressing variation in the fitting gap due to thermal expansion of the resin.
  • the control member has a cylindrical main body fitted and held on an outer peripheral surface of a cylindrical holding portion provided on the inner peripheral side of the main impeller.
  • the water pump is characterized in that the control member is fitted and held on the outer peripheral side of a cylindrical holding portion in which a cylindrical main body extends along the axial direction on the back side of the impeller.
  • the control member is a water pump characterized in that a cylindrical main body is fitted and held in a cylindrical holding portion provided on the outer periphery of the drive ring.
  • a driven ring is provided between the bearing and the main impeller;
  • the driven ring includes an extending portion extending in a radial direction at one end portion and an axial direction extending from an outer peripheral edge of the extending portion, and an outer peripheral surface of the one end portion of the control member is slidably fitted.
  • a water pump characterized by having a cylindrical vibration suppressing portion held together.
  • the vibration suppressing portion can be provided on the driven ring, the degree of freedom in design increases.
  • the holding portion is provided only in the drive ring.
  • the holding portion is provided only in the impeller.
  • the holding portion is provided on both the drive ring and the impeller.
  • the shake suppressing effect is further improved by holding both ends of the control member.
  • the holding portion includes a restricting portion that restricts axial movement of the control member.

Landscapes

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

Abstract

La présente invention concerne une pompe à eau qui permet de diminuer la taille d'un logement de pompe qui comprend une roue principale et une roue auxiliaire. La présente invention comprend : un logement (2) de pompe qui possède une chambre (3) de pompe formée à l'intérieur d'une extrémité avant latérale d'un bloc cylindres (01) ; un arbre d'entraînement (6) disposé rotatif à l'intérieur du logement de pompe et qui comprend une poulie (4) placée sur une partie (6a) d'arbre de grand diamètre ; et une roue principale (7) qui est disposée dans la chambre de pompe, qui est placée sur une partie (6c) d'arbre de petit diamètre de l'arbre d'entraînement, une partie de palier (15) et un anneau de garniture (16) étant placés entre elles, de façon à pouvoir tourner l'une par rapport à l'autre et qui est raccordée de façon intermittente à l'arbre d'entraînement au moyen d'un ressort d'embrayage (20). Une roue auxiliaire (32) est placée sur une partie d'extrémité de la partie d'arbre de petit diamètre en une position séparée de la roue principale dans la direction axiale. La roue auxiliaire est disposée à l'intérieur d'un chemin de guidage (03) qui communique avec la chambre de pompe dans la direction axiale.
PCT/JP2014/070813 2013-09-19 2014-08-07 Pompe à eau WO2015040973A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2015537598A JP6096308B2 (ja) 2013-09-19 2014-08-07 ウォータポンプ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013194493 2013-09-19
JP2013-194493 2013-09-19

Publications (1)

Publication Number Publication Date
WO2015040973A1 true WO2015040973A1 (fr) 2015-03-26

Family

ID=52688630

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/070813 WO2015040973A1 (fr) 2013-09-19 2014-08-07 Pompe à eau

Country Status (2)

Country Link
JP (1) JP6096308B2 (fr)
WO (1) WO2015040973A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019515186A (ja) * 2016-05-12 2019-06-06 マン・エナジー・ソリューションズ・エスイー ラジアル圧縮機
JP2021504618A (ja) * 2017-11-22 2021-02-15 パーカー・ハニフィン・コーポレーション 遠心支援を伴う曲げ軸液圧ポンプ

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60147794U (ja) * 1984-03-13 1985-10-01 アイシン精機株式会社 内燃エンジン用ウオ−タポンプ
JPH02119995U (fr) * 1989-03-16 1990-09-27
JPH041693U (fr) * 1990-04-16 1992-01-08
JPH0430293U (fr) * 1990-07-05 1992-03-11
JPH0469697U (fr) * 1990-10-26 1992-06-19
JPH07332086A (ja) * 1994-06-14 1995-12-19 Unisia Jecs Corp 渦巻ポンプ
JPH11336686A (ja) * 1998-05-26 1999-12-07 Aisin Seiki Co Ltd ウォータポンプ
JP2005307985A (ja) * 2005-06-17 2005-11-04 Matsushita Electric Ind Co Ltd 電気掃除機用電動送風機及びこれを用いた電気掃除機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60147794U (ja) * 1984-03-13 1985-10-01 アイシン精機株式会社 内燃エンジン用ウオ−タポンプ
JPH02119995U (fr) * 1989-03-16 1990-09-27
JPH041693U (fr) * 1990-04-16 1992-01-08
JPH0430293U (fr) * 1990-07-05 1992-03-11
JPH0469697U (fr) * 1990-10-26 1992-06-19
JPH07332086A (ja) * 1994-06-14 1995-12-19 Unisia Jecs Corp 渦巻ポンプ
JPH11336686A (ja) * 1998-05-26 1999-12-07 Aisin Seiki Co Ltd ウォータポンプ
JP2005307985A (ja) * 2005-06-17 2005-11-04 Matsushita Electric Ind Co Ltd 電気掃除機用電動送風機及びこれを用いた電気掃除機

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019515186A (ja) * 2016-05-12 2019-06-06 マン・エナジー・ソリューションズ・エスイー ラジアル圧縮機
JP2021504618A (ja) * 2017-11-22 2021-02-15 パーカー・ハニフィン・コーポレーション 遠心支援を伴う曲げ軸液圧ポンプ
JP7254794B2 (ja) 2017-11-22 2023-04-10 パーカー・ハニフィン・コーポレーション 遠心支援を伴う曲げ軸液圧ポンプ

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JPWO2015040973A1 (ja) 2017-03-02

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