US20130142680A1 - Electric pump - Google Patents

Electric pump Download PDF

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Publication number
US20130142680A1
US20130142680A1 US13/690,723 US201213690723A US2013142680A1 US 20130142680 A1 US20130142680 A1 US 20130142680A1 US 201213690723 A US201213690723 A US 201213690723A US 2013142680 A1 US2013142680 A1 US 2013142680A1
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US
United States
Prior art keywords
bush
motor
attachment bore
cylindrical portion
base portion
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.)
Abandoned
Application number
US13/690,723
Other languages
English (en)
Inventor
Shinya TAMAWARI
Hiroyuki Uehara
Yusuke KOJIMA
Nozomu Sumitomo
Tadahiro Kitamura
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.)
Aisin Corp
Original Assignee
Aisin Seiki Co 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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Assigned to AISIN SEIKI KABUSHIKI KAISHA reassignment AISIN SEIKI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KITAMURA, TADAHIRO, KOJIMA, YUSUKE, Sumitomo, Nozomu, Tamawari, Shinya, UEHARA, HIROYUKI
Publication of US20130142680A1 publication Critical patent/US20130142680A1/en
Abandoned legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/02—Arrangements of pumps or compressors, or control devices therefor
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • F04B53/003—Noise damping by damping supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal

Definitions

  • This disclosure generally relates to an electric pump.
  • a pump body is attached to a bracket, for example, via a bush made of an elastic material such as rubber, for example. Because of the bush, vibration or oscillation generated at the pump body is damped before being transmitted to the bracket so that the vibration is inhibited from being transmitted to the other portion of the vehicle.
  • JP2006-112519A discloses an attachment structure for attaching an electric water pump (pump body) to an intermediate plate via a vibration-proof bush, and the intermediate plate is attached to a bracket via another vibration-proof bush.
  • the electric water pump is driven by rotations of a motor serving as a power source.
  • the number of rotations of the motor decreases and finally the motor is stopped.
  • the large vibration causes the entire electric water pump to oscillate or vibrate.
  • the bush is unable to absorb such large vibration, which results in hitting or collision between the bush and the bracket to thereby generate a hitting sound or noise.
  • an electric pump including a motor, a bracket including a support surface arranged to be perpendicular to a rotation shaft of the motor and a bush attachment bore provided to be perpendicular to the support surface, and a bush fitted to the bush attachment bore.
  • the bush attachment bore includes a base portion formed in a shape similar to a portion of the bush fitted to the bush attachment bore, the bush attachment bore including an expansion portion integrally formed with the base portion and extending in a circumferential direction of the motor.
  • FIG. 1 is a partial cross-sectional view of a pump body of an electric pump according to a first embodiment disclosed here;
  • FIG. 2 is perspective view of the electric pump according to the first embodiment
  • FIG. 3 is a schematic view of a bracket according to the first embodiment
  • FIG. 4 is an enlarged view of a bush attachment bore according to the first embodiment
  • FIG. 5 is a cross-sectional view of a bush according to the first embodiment
  • FIG. 6 is a partial cross-sectional view illustrating a state where the bracket is attached to a stay according to the first embodiment
  • FIG. 7 is a cross-sectional view taken along line VII-VII in FIG. 6 ;
  • FIG. 8A is a partial cross-sectional view illustrating a state where an inner cylindrical portion hits an outer cylindrical portion via an elastic portion according to the first embodiment
  • FIG. 8B is a partial cross-sectional view illustrating a state where an inner cylindrical portion hits an outer cylindrical portion via an elastic portion according to a known electric pump
  • FIG. 9 is a graph illustrating a relationship between a displacement of the bush and a load generated at a wall surface of the bush attachment bore according to the first embodiment
  • FIG. 10 is a schematic view of the bracket according to a second embodiment disclosed here.
  • FIG. 11 is a schematic view of the bracket according to a third embodiment disclosed here.
  • FIG. 12 is a schematic view of the bracket according to a fourth embodiment disclosed here.
  • FIG. 13 is a perspective view of a bush according to a fifth embodiment disclosed here.
  • FIG. 14 is a partial cross-sectional view illustrating a state where the bracket is attached to the stay via the bush according to the fifth embodiment
  • FIG. 15 is a cross-sectional view taken along line XV-XV in FIG. 14 ;
  • FIG. 16 is a perspective view of a bush according to a sixth embodiment disclosed here.
  • FIG. 17 is a partial cross-sectional view illustrating a state where the bracket is attached to the stay via the bush according to the fifth embodiment.
  • FIG. 18 is a cross-sectional view taken along line XVIII-XVIII in FIG. 17 .
  • a pump body 2 includes a valve unit V arranged at a first end of a cylinder 11 (i.e., at a side where a cylinder head is provided).
  • the cylinder 11 and a piston 12 form a pressure increasing and decreasing chamber A within the cylinder 11 .
  • the pump body 2 also includes a pump housing 13 arranged at a second end of the cylinder 11 .
  • the pump housing 13 includes an inner void forming a driving chamber B.
  • the pump body 2 according to the first embodiment is used as a vacuum pump serving as a vacuum pressure source of a brake booster.
  • An electric motor 14 which will be hereinafter simply referred to as a motor 14 , is accommodated within the pump housing 13 .
  • a crank arm 15 integrally rotates with a rotation shaft 14 a, serving as an output shaft, of the motor 14 .
  • a base portion of a connecting rod 16 i.e., a right end side of a connecting rod 16 in FIG. 1 , is connected to the crank arm 15 while an end portion of the connecting rod 16 , i.e., a left end side of the connecting rod 16 in FIG. 1 , is connected to the piston 12 .
  • the crank arm 15 and the connecting rod 16 constitute a crank mechanism C.
  • the valve unit V includes a valve body 21 having an air intake void 21 a and an air exhaust void 21 b , an intake valve 22 , and an exhaust valve 23 .
  • the intake valve 22 is provided at a portion of the valve body 21 connected to the air intake void 21 a.
  • the exhaust valve 23 is provided at a portion of the valve body 21 connected to the air exhaust void 21 b.
  • the exhaust valve 23 is biased by a spring 23 s in a direction where the pressure increasing and decreasing chamber A is closed or sealed.
  • the valve unit V also includes a cover plate 24 for blocking the air intake void 21 a and the air exhaust void 21 b from the outside of the pump body 2 .
  • a tube 25 is connected to the air intake void 21 a as illustrated in FIG. 2 .
  • a fluid passage E is formed from the air exhaust void 21 b of the valve body 21 to a first opening 17 a provided at an outer surface of a passage block 17 .
  • the driving chamber B is defined by an opening portion of the pump housing 13 that is closed or blocked by a plate-shaped closing member 18 .
  • a second opening 18 a is provided at the closing member 18 .
  • the passage block 17 including an inner void connected to the second opening 18 a is arranged at an opposite side from the pump housing 13 relative to the closing member 18 .
  • An air flow passage F is formed from the second opening 18 a to the first opening 17 a provided at the outer surface of the passage block 17 .
  • the intake valve 22 is opened so that air flows through the tube 25 and suctioned into the pressure increasing and decreasing chamber A by passing through the air intake void 21 a. Accordingly, the negative pressure is applied to the outside object. At this time, air in the driving chamber B is discharged or exhausted from the second opening 18 a to flow through the air flow passage F and is discharged from the first opening 17 a to the outside of the pump body 2 .
  • the exhaust valve 23 is opened so that air in the pressure increasing and decreasing chamber A is discharged to the air exhaust void 21 b to flow through the fluid passage E and is discharged from the first opening 17 a to the outside of the pump body 2 .
  • air is suctioned from the second opening 18 a into the driving chamber B. Because the intake valve 22 is closed, air in the pressure increasing and decreasing chamber A is inhibited from flowing backwards to the air intake void 21 a.
  • FIG. 2 illustrates a perspective view of an electric pump 1 including the pump body 2 , a stay 3 fixed to the pump body 2 , and a bracket 4 attached to the stay 3 .
  • the stay 3 is an intermediate member made of metal for attaching the pump body 2 to the bracket 4 .
  • the stay 3 is fixed to the pump body 2 by a bolt, for example, so that the stay 3 is united with the pump body 2 .
  • the bracket 4 is a metal member formed in an annular shape to surround the pump body 2 .
  • three bush attachment bores 5 are formed to extend through a vertical direction at a support surface 4 a of the bracket 4 so that the bush attachment bores 5 are arranged at substantially even intervals in a circumferential direction of the bracket 4 .
  • Bushes 6 are fitted to the bush attachment bores 5 respectively.
  • the bracket 4 is attached to the stay 3 via the bushes 6 in a state where the rotation shaft 14 a is positioned perpendicular to the support surface 4 a.
  • three circular penetration bores are formed at the bracket 4 .
  • the circular penetration bores are provided for fixing the electric pump 1 to a vehicle body.
  • each of the bush attachment bores 5 is a single bore including a base portion 5 a formed in a circular bore (circle) and two expansion portions 5 b extending or expanding from the base portion 5 a in a circumferential direction of the motor 14 .
  • An outer edge of the expansion portion 5 b includes two tangent portions 5 d serving as a tangent line of the circle of the base portion 5 a, a curved end portion 5 e arranged at a side away from the base portion 5 a so as to smoothly connect the two tangent portions 5 d, and an arc portion 5 f arranged at a side close to the base portion 5 a to serve as an imaginary circular arc of the base portion 5 a.
  • the width of the expansion portion 5 b in a radial direction of the motor 14 i.e., a distance between the two tangent portions 5 d, is gradually decreasing in a direction away from the base portion 5 a in the circumferential direction of the motor 14 .
  • a furthest point 5 g positioned on the end portion 5 e and most away from a center 5 c of the base portion 5 a is arranged on a circumference of a circle of which the center corresponds to the rotation shaft 14 a of the motor 14 and the radius corresponds to a distance from the rotation shaft 14 a to the center 5 c of the base portion 5 a.
  • the aforementioned circle will be hereinafter referred to as a motor concentric circle.
  • Two of the furthest points 5 g of the expansion portions 5 b and the center 5 c are inhibited from being provided on a straight line and are provided on the circumference of the motor concentric circle accordingly.
  • each of the bushes 6 includes a circular inner cylindrical portion 7 serving as a shaft member, a circular outer cylindrical portion 8 arranged coaxially with the inner cylindrical portion 7 and surrounding the inner cylindrical portion 7 , and an elastic portion 9 having a thin plate form and formed to connect the inner cylindrical portion 7 and the outer cylindrical portion 8 .
  • the inner cylindrical portion 7 is movable three-dimensionally relative to the outer cylindrical portion 8 within a range where the elastic portion 9 is deformable,
  • the inner cylindrical portion 7 includes a metal pipe portion 7 a made of metal and including a hollow portion 7 c, and a rubber pipe portion 7 b tightly formed around the metal pipe portion 7 a.
  • the rubber pipe portion 7 b, the elastic portion 9 , and the outer cylindrical portion 8 are all made of rubber material, for example, of silicon rubber, and are integrally formed one another.
  • vertical, horizontal, upward and downward directions for example, are based on FIG. 5 .
  • a vertical length of the outer cylindrical portion 8 is smaller than that of the inner cylindrical portion 7 .
  • An upper portion and a lower portion of the inner cylindrical portion 7 project from an uppermost surface and a lowermost surface of the outer cylindrical portion 8 respectively.
  • the outer cylindrical portion 8 includes an upper flange portion 8 a provided at an upper side, a lower flange portion 8 b provided at a lower side, and an intermediate portion 8 c provided between the upper flange portion 8 a and the lower flange portion 8 b.
  • Each of the upper flange portion 8 a, the lower flange portion 8 b, and the intermediate portion 8 c is formed in a circular shape in a plan view.
  • Outer diameters of the upper flange portion 8 a and the lower flange portion 8 b are greater than a diameter of the base portion 5 a of the bush attachment bore 5 .
  • An outer diameter of the intermediate portion 8 c is substantially the same as the diameter of the base portion 5 a. That is, the base portion 5 a is formed in a shape similar to a portion of the bush 6 fitted to the bush attachment bore 5 . Because the outer diameter of the intermediate portion 8 c is smaller than the outer diameter of each of the upper flange portion 8 a and the lower flange portion 8 b, an annular groove 8 d is formed at an outer side of the intermediate portion 8 c between the upper flange portion 8 a and the lower flange portion 8 b.
  • a groove width of the annular groove 8 d i.e., a vertical length of the intermediate portion 8 c, is substantially the same as a thickness of the bracket 4 .
  • the bush 6 is fitted to the bush attachment bore 5 of the bracket 4 .
  • the intermediate portion 8 c is inserted into the base portion 5 a so that an outer peripheral surface 8 e of the intermediate portion 8 c serving as a bottom surface of the annular groove 8 d makes contact with a wall surface of an inner peripheral portion of the base portion 5 a.
  • the upper flange portion 8 a and the lower flange portion 8 b of the outer cylindrical portion 8 sandwich and hold the bracket 4 to thereby fix the bush 6 to the bracket 4 .
  • the bush attachment bore 5 is larger in the circumferential direction of the motor 14 than the intermediate portion 8 c by the expansion portions 5 b, the bush 6 may be easily fixed to the bush attachment bore 5 .
  • the bracket 4 fitted to the bush 6 is attached to the stay 3 that is united to the pump body 2 .
  • a circular bore 3 a is formed at the stay 3 so that the circular bore 3 a is positioned to overlap the base portion 5 a in a state where the stay 3 is assembled on the bracket 4 and so that the circular bore 3 a is coaxial with the base portion 5 a.
  • the circular bore 3 a includes a diameter substantially the same as an inner diameter of the inner cylindrical portion 7 .
  • the stay 3 and the bracket 4 are placed on each other and thereafter a bolt 10 is inserted into the hollow portion 7 c of the inner cylindrical portion 7 and the circular bore 3 a to be tightened by a nut 10 c via a spring washer 10 a and a flat washer 10 b, which results in a completion of the attachment of the bracket 4 and the stay 3 .
  • the bracket 4 and the stay 3 are inhibited from directly contacting each other, i.e., the bushes 6 are disposed between the bracket 4 and the stay 3 .
  • the inner cylindrical portion 7 and the outer cylindrical portion 8 are maintained coaxially with each other.
  • a normal vibration i.e., a vibration in a state where the pump body 2 is driven in a normal condition
  • the vibration is transmitted to the stay 3 , which causes the inner cylindrical portion 7 to vibrate.
  • the vibration of the inner cylindrical portion 7 is absorbed by a deformation of the elastic portion 9 , the vibration is unlikely to be transmitted to the outer cylindrical portion 8 . Accordingly, even when the vibration is generated at the pump body 2 , the bracket 4 disposed or held by the outer cylindrical portion 8 is unlikely to vibrate or oscillate.
  • the vibration is transmitted to the inner cylindrical portion 7 , which leads to the deformation of the elastic portion 9 .
  • a vibration component in the circumferential direction of the motor 14 in which the motor 14 rotates is the greatest.
  • the inner cylindrical portion 7 moves while the elastic portion 9 is deformed in the circumferential direction relative to the rotation shaft 14 a. Only the deformation of the elastic portion 9 , however, is unable to absorb the vibration of the inner cylindrical portion 7 . That is, the inner cylindrical portion 7 may hit or collide with the outer cylindrical portion 8 beyond the elastic portion 9 .
  • the outer cylindrical portion 8 moves in the circumferential direction of the motor 14 while being deformed.
  • the bush attachment bore 5 includes the expansion portions 5 b in the circumferential direction, the outer peripheral surface 8 e of the intermediate portion 8 c is inhibited from hitting a wall surface 5 h (see FIG. 6 ) of the end portion 5 e of the bush attachment bore 5 .
  • a hitting sound or noise by the hitting or collision between the bush 6 and the bracket 4 is inhibited from occurring. As illustrated in FIG.
  • the outer peripheral surface 8 e of the intermediate portion 8 c makes contact with the tangent portions 5 d of the bush attachment bore 5 . Nevertheless, only a small component of force serving as a portion of a force in the circumferential direction of the bush 6 is applied to the tangent portions 5 d. In addition, after the outer peripheral surface 8 e makes contact with the tangent portions 5 d, the bush 6 is able to further move in the circumferential direction by means of the clearance formed by the expansion portion 5 b . According to the first embodiment, the furthest point 5 g is positioned on the circumference of the motor concentric circle.
  • the vibration generating direction and the direction in which the expansion portion 5 b is formed coincide with each other.
  • the bush 6 thus smoothly moves in the circumferential direction of the motor 14 to thereby reduce an occurrence of hitting sound by the hitting or contact between the outer peripheral surface 8 e and the tangent portions 5 d.
  • FIG. 8B is a cross-sectional view illustrating a state same as that in FIG. 8A , according to a known electric pump.
  • a circular bush attachment bore having the same size as the base portion 5 a is formed at the bracket 4 .
  • the expansion portion 5 b is not provided.
  • the bush 6 same as the first embodiment is provided.
  • no clearance is formed between the outer peripheral surface 8 e of the intermediate portion 8 c and a wall surface of an end portion of the bush attachment bore.
  • the outer peripheral surface 8 e hits the wall surface of the end portion of the bush attachment bore to thereby generate the hitting sound.
  • FIG. 9 is a graph illustrating a relationship between a displacement of the metal pipe portion 7 a of the inner cylindrical portion 7 in a case where the metal pipe portion 7 a moves on the circumference of the motor concentric circle, and a load applied at that time to the rubber pipe portion 7 b of the inner cylindrical portion 7 in the tangent direction of the motor concentric circle.
  • a horizontal axis indicates the displacement of the metal pipe portion 7 a while a vertical axis indicates a load applied to the rubber pipe portion 7 b.
  • Characteristics A in FIG. 9 illustrate characteristics of the electric pump 1 including the bush attachment bore 5 according to the first embodiment.
  • Characteristics B in FIG. 9 illustrate characteristics of a known electric pump.
  • the graph in FIG. 9 indirectly illustrates an existence of occurrence of hitting sound.
  • a displacement Z is a displacement of the metal pipe portion 7 a obtained in a case where the inner cylindrical portion 7 hits the outer cylindrical portion 8 via the elastic portion 9 .
  • the inclination of the characteristics B increases rapidly and the load applied to the rubber pipe portion 7 b increases drastically. That is, the intermediate portion 8 c of the bush 6 collides with the bracket 4 , which leads to the occurrence of hitting sound.
  • the load applied to the rubber pipe portion 7 b is inhibited from increasing drastically in the region Y. That is, even when the displacement of the bush 6 increases, the intermediate portion 8 c of the bush 6 is unlikely to hit or collide with the wall surface of the bush attachment bore 5 , which leads to a reduction of occurrence of hitting sound.
  • the width of the expansion portion 5 b in the radial direction of the motor 14 i.e., the distance between the two tangent portions 5 d, is gradually decreasing in the direction away from the base portion 5 a in the circumferential direction of the motor 14 .
  • the intermediate portion 8 c elastically deforms. After the large vibration is substantially cleared, the bush 6 is automatically returned by a restoring force thereof to an initial position, i.e., a position at which the base portion 5 a is arranged.
  • FIG. 10 A second embodiment will be explained with reference to FIG. 10 . An explanation of a configuration of the second embodiment substantially similar to the first embodiment will be omitted. In addition, similar components of the second embodiment to those of the first embodiment bear the same reference numerals as the first embodiment.
  • the expansion portion 5 b is formed at one side of the base portion 5 a. In a case where the motor 14 is stopping while decelerating from a state where the motor 14 rotates in the clockwise direction, the stay 3 arranged around the motor 14 tends to rotate in the clockwise direction in the same way as the motor 14 by an inertia force and the bush 6 also rotates in the clockwise direction.
  • the motor 14 vibrates greater than a case where the motor 14 is in a normal rotating state, i.e., a greater vibration than a vibration in a state where the pump body 2 is driven in the normal condition is generated at the pump body 2 .
  • the force applied in the clockwise direction increases.
  • the large vibration state of the motor 14 may be cleared for a short time period because of the rapid decrease of the number of rotations of the motor 14 .
  • the bush 6 moves upon the occurrence of vibration of the motor 14 and then the intermediate portion 8 c deforms, the large vibration state of the motor 14 is cleared by the time the intermediate portion 8 c is restored.
  • the expansion portion 5 b formed at one side of the base portion 5 a in the clockwise direction may decrease the occurrence of hitting sound and may lead to the bush attachment bore 5 in a reduced size.
  • the strength of the bracket 4 is inhibited from decreasing.
  • a third embodiment will be explained with reference to FIG. 11 .
  • An explanation of a configuration of the third embodiment substantially similar to the first embodiment will be omitted.
  • similar components of the third embodiment to those of the first embodiment bear the same reference numerals as the first embodiment.
  • the bush attachment bore 5 is formed so that the furthest points 5 g of the expansion portions 5 b and the center 5 c of the base portion 5 a are arranged on the straight line.
  • the aforementioned configuration of the bush attachment bore 5 may be desirable in a case where the arc of the motor concentric circle nearly forms a straight line because of a large outer diameter of the motor 14 , for example.
  • the bush attachment bore 5 may be easily processed accordingly.
  • a fourth embodiment will be explained with reference to FIG. 12 .
  • An explanation of a configuration of the fourth embodiment substantially similar to the first embodiment will be omitted.
  • similar components of the fourth embodiment to those of the first embodiment bear the same reference numerals as the first embodiment.
  • the width in the radial direction of each of the two expansion portions 5 b of the bush attachment bore 5 is constant and unchanged, i.e., is inhibited from decreasing in a direction away from the base portion 5 a. That is, the bush attachment bore 5 is an elongated bore having the diameter of the base portion 5 a.
  • a locus of the center 5 c of the base portion 5 a constituting the elongated bore is arranged on the circumference of the motor concentric circle.
  • the bush 6 even when the greater vibration than the vibration in the normal rotating state of the motor 14 is cleared, the bush 6 is inhibited from automatically returning to the initial position, i.e., the position at which the base portion 5 a is provided. Nevertheless, because the width of the expansion portion 5 b in the radial direction is constant and the size of the bush attachment bore 5 is larger than that of the first embodiment, the bush 6 and the bracket 4 are unlikely to hit each other even when the vibration is greater than that in the normal rotating state of the motor 14 , which reduces an occurrence of hitting sound.
  • the fifth embodiment includes a bush 60 which is different from the bush 6 according to the first embodiment.
  • the bush attachment bore 5 according to the fifth embodiment is the same as the first embodiment.
  • the bush 60 is formed to extend in a direction corresponding to the circumferential direction of the motor 14 so as to conform to the shape of the bush attachment bore 5 that extends in the circumferential direction in a case where the bush 60 is fitted to the bush attachment bore 5 .
  • the bush 60 includes an outer cylindrical portion 80 including an upper flange portion 80 a, a lower flange portion 80 b, and an intermediate portion 80 c, the portions 80 a, 80 b, and 80 c being formed in a similar shape to the shape of the bush attachment bore 5 in a plan view.
  • the intermediate portion 80 c has the same size as the bush attachment bore 5 . As illustrated in FIGS.
  • an outer peripheral surface 80 e of the outer cylindrical portion 80 is fully and thoroughly in contact with an inner peripheral surface of the bush attachment bore 5 .
  • the upper flange portion 80 a and the lower flange portion 80 b sandwich and hold the bracket 4 therebetween so as to fix the bush 60 .
  • the size of the inner cylindrical portion 7 is the same as that of the first embodiment. Accordingly, a longitudinal length L of an elastic portion 90 connecting the inner cylindrical portion 7 and the outer cylindrical portion 80 extending in the circumferential direction of the motor 14 when the bush 60 is fitted to the bush attachment bore 5 is longer than a length of the elastic portion 9 of the bush 6 according to the first embodiment.
  • the vibration is transmitted to the inner cylindrical portion 7 via the stay 3 to thereby vibrate or oscillate the inner cylindrical portion 7 .
  • a vibration component in the circumferential direction of the motor 14 is the greatest.
  • the inner cylindrical portion 7 moves in the circumferential direction while the elastic portion 90 in the longitudinal direction L elastically deforms.
  • the vibration of the inner cylindrical portion 7 is absorbed by the deformation of the elastic portion 90 and is unlikely to be transmitted to the outer cylindrical portion 80 .
  • the inner cylindrical portion 7 may be inhibited from hitting or colliding with the outer cylindrical portion 80 .
  • the outer cylindrical portion 80 specifically, the bush 60 is unlikely to move in the circumferential direction to thereby reduce occurrence of hitting sound caused by the hitting or collision between the bush 60 and the bracket 4 .
  • the sixth embodiment includes a bush 61 which is different from the bush 6 according to the first embodiment.
  • the bush attachment bore 5 according to the sixth embodiment is the same as the first embodiment.
  • an outer cylindrical portion 81 of the bush 61 includes a similar form as an enlarged form of the outer cylindrical portion 8 of the bush 6 according to the first embodiment. That is, the outer cylindrical portion 81 includes an upper flange portion 81 a, a lower flange portion 81 b, and an intermediate portion 81 c each of which is formed in a circular shape in a plan view.
  • An outer peripheral length of an outer peripheral surface 81 e is substantially equal to a length of an entire inner peripheral surface of the bush attachment bore 5 .
  • the size of the inner cylindrical portion 7 is not enlarged and is substantially the same as the size according to the bush 6 of the first embodiment. Accordingly, a radial length of an elastic portion 91 connecting the inner cylindrical portion 7 and the outer cylindrical portion 81 is longer than the radial length of the elastic portion 9 of the bush 6 according to the first embodiment.
  • the bush 61 is deformed so as to conform to the form of the bush attachment bore 5 .
  • the bush 61 is formed in a form similar to the bush 60 of the fifth embodiment. That is, in a state where the bush 61 is fitted to the bush attachment bore 5 , the longitudinal length L of the elastic portion 91 connecting the inner cylindrical portion 7 and the outer cylindrical portion 81 extending in the circumferential direction of the motor 14 when the bush 61 is fitted to the bush attachment bore 5 is longer than the length of the elastic portion 9 of the bush 6 according to the first embodiment.
  • the outer peripheral surface 81 e is fully and thoroughly in contact with the entire inner peripheral surface including the wall surface 5 h of the bush attachment bore 5 .
  • the upper flange portion 81 a and the lower flange portion 81 b sandwich and hold the bracket 4 therebetween so as to fix the bush 61 .
  • the vibration of the inner cylindrical portion 7 is absorbed by the deformation of the elastic portion 91 and is unlikely to be transmitted to the outer cylindrical portion 81 . Consequently, the inner cylindrical portion 7 may be inhibited from hitting or colliding with the outer cylindrical portion 81 .
  • the outer cylindrical portion 81 specifically, the bush 61 , is unlikely to move in the circumferential direction to thereby reduce occurrence of hitting sound caused by the hitting or collision between the bush 61 and the bracket 4 .
  • the electric pump may be achieved by combination of any of the aforementioned first to sixth embodiments wherever possible.
  • the bush 6 , 60 , 61 is unlikely to hit or collide with the bracket 4 .
  • the vibration in the circumferential direction (the rotation direction) of the motor 14 increases.
  • the bush 6 , 60 , 61 moving in the circumferential direction may hit or collide with the bracket 4 .
  • the bush attachment bore 5 formed at the bracket 4 extends or expands in the circumferential direction. Accordingly, the bush 6 , 60 , 61 may be inhibited from hitting the bracket 4 and the occurrence of hitting sound is reduced even when the motor 14 vibrates and then the bush 6 , 60 , 61 moves in the circumferential direction.
  • the expansion portion 5 b includes the width in the radial direction of the motor 14 , the width gradually decreasing in a direction away from the base portion 5 a.
  • the bush 6 , 60 , 61 is deformed when moving in the circumferential direction. According to the aforementioned embodiments, even in a case where the bush 6 , 60 , 61 moves in the circumferential direction by the vibration of the motor 14 , the bush 6 , 60 , 61 that is deformed is returned by the restoring force thereof to a position where the base portion 5 a is arranged after the larger vibration is substantially cleared. Thus, even in a case where the motor 14 repeats driving and stopping and therefore the large vibration occurs, the bush 6 , 60 , 61 is unlikely to hit the bracket 4 , which results in the reduction of the occurrence of hitting sound.
  • the expansion portion 5 b is formed at each of both sides of the base portion 5 a in the circumferential direction of the motor 14 .
  • the bush 6 , 60 , 61 greatly moves in both directions, i.e., the clockwise and counterclockwise directions.
  • the expansion portions 5 b formed at both sides of the base portion 5 a in the circumferential direction of the motor 14 inhibit the hitting of the bush 6 , 60 , 61 relative to the bracket 4 , which reduces the occurrence of hitting sound.
  • the base portion 5 a includes a circular form and the expansion portion 5 b includes the furthest point 5 g on an outer edge from the center 5 c of the base portion 5 a, the furthest point 5 g being positioned on a circumference of a circle of which the center corresponds to the rotation shaft 14 a of the motor 14 and the radius corresponds to a distance from the rotation shaft 14 a to the center 5 c of the base portion 5 a.
  • the vibration direction of the motor 14 when the motor 14 vibrates greater than in the normal rotating state corresponds to a tangent direction of the circumference of the circle of which the center corresponds to the rotation shaft 14 a and the radius corresponds to a distance from the rotation shaft 14 a to the center 5 c.
  • the vibration direction greatly varies.
  • the vibration direction matches the direction where the expansion portion 5 b is formed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Vibration Prevention Devices (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Springs (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US13/690,723 2011-12-01 2012-11-30 Electric pump Abandoned US20130142680A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011263904 2011-12-01
JP2011-263904 2011-12-01
JP2012139991A JP2013137093A (ja) 2011-12-01 2012-06-21 電動ポンプ
JP2012-139991 2012-06-21

Publications (1)

Publication Number Publication Date
US20130142680A1 true US20130142680A1 (en) 2013-06-06

Family

ID=47257663

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/690,723 Abandoned US20130142680A1 (en) 2011-12-01 2012-11-30 Electric pump

Country Status (4)

Country Link
US (1) US20130142680A1 (ja)
EP (1) EP2600003A1 (ja)
JP (1) JP2013137093A (ja)
CN (1) CN202971092U (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3124787A1 (fr) * 2021-07-02 2023-01-06 Psa Automobiles Sa Dispositif de decouplage vibratoire, notamment pour une pompe et un reducteur de vitesse de vehicule automobile
US11988218B2 (en) 2021-03-10 2024-05-21 Multi Parts Supply Usa, Inc. Electric coolant pump with expansion compensating seal

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3299646A1 (de) * 2016-09-21 2018-03-28 Adient Luxembourg Holding S.à r.l. Buchse und fahrzeugsitz
JP6883011B2 (ja) * 2018-10-09 2021-06-02 ダイハツ工業株式会社 自動車用内燃機関
DE102020109052B4 (de) * 2020-04-01 2022-02-10 Nidec Gpm Gmbh Schwingungsdämpfendes Entkopplungselement
CN112780718B (zh) * 2021-01-15 2023-03-28 上海线友电子有限公司 气体传感器抗震塞及使用该抗震塞的气体传感器

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US3037733A (en) * 1961-05-26 1962-06-05 Donald B Roman Stabilized peg-board hanger
US3813776A (en) * 1973-05-15 1974-06-04 Mccullough Corp Vibration isolation system particularly adapted for use with a chain saw
USD285647S (en) * 1984-04-27 1986-09-16 Isaac Sachs Drop clamp suspension bracket or similar article
US4931683A (en) * 1985-11-30 1990-06-05 Siemens Aktiengesellschaft Housing for a small motor
US4938448A (en) * 1987-09-14 1990-07-03 Sanden Corporation Mounting mechanism for an automotive air conditioning compressor
US6145803A (en) * 1997-02-04 2000-11-14 Imi Cornelius Inc. Quick release motor mount
US20050196294A1 (en) * 2004-03-02 2005-09-08 Maytag Corporation Vibration damping pump bracket
US20050206054A1 (en) * 2004-03-18 2005-09-22 Tokai Rubber Industries, Ltd. Vibration damping bushing
US7837168B2 (en) * 2007-03-30 2010-11-23 Lexmark International, Inc. Mounting device and method for positioning a motor within an image forming apparatus

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JPS50105905U (ja) * 1974-02-05 1975-08-30
US4733738A (en) * 1986-10-14 1988-03-29 Neil Rowe Tractor spray pump support
JP2601522B2 (ja) * 1988-08-11 1997-04-16 スズキ株式会社 自動車の電気式フューエルポンプ取付け装置
US5524860A (en) * 1994-09-29 1996-06-11 Ives; Lewis Universal mounting bracket and method
KR200213521Y1 (ko) * 1997-12-30 2001-04-02 양재신 유압펌프모터의 장착구조
JP2006112519A (ja) * 2004-10-14 2006-04-27 Toyota Motor Corp ウォータポンプの取り付け構造
JP2007023939A (ja) * 2005-07-19 2007-02-01 Denso Corp 電動ポンプ、電動ポンプの取付構造、および電動ポンプに組み合わされるブラケット

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1716940A (en) * 1925-07-13 1929-06-11 Woller Oliver C Ritz Bracket
US3037733A (en) * 1961-05-26 1962-06-05 Donald B Roman Stabilized peg-board hanger
US3813776A (en) * 1973-05-15 1974-06-04 Mccullough Corp Vibration isolation system particularly adapted for use with a chain saw
USD285647S (en) * 1984-04-27 1986-09-16 Isaac Sachs Drop clamp suspension bracket or similar article
US4931683A (en) * 1985-11-30 1990-06-05 Siemens Aktiengesellschaft Housing for a small motor
US4938448A (en) * 1987-09-14 1990-07-03 Sanden Corporation Mounting mechanism for an automotive air conditioning compressor
US6145803A (en) * 1997-02-04 2000-11-14 Imi Cornelius Inc. Quick release motor mount
US20050196294A1 (en) * 2004-03-02 2005-09-08 Maytag Corporation Vibration damping pump bracket
US20050206054A1 (en) * 2004-03-18 2005-09-22 Tokai Rubber Industries, Ltd. Vibration damping bushing
US7837168B2 (en) * 2007-03-30 2010-11-23 Lexmark International, Inc. Mounting device and method for positioning a motor within an image forming apparatus

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988218B2 (en) 2021-03-10 2024-05-21 Multi Parts Supply Usa, Inc. Electric coolant pump with expansion compensating seal
FR3124787A1 (fr) * 2021-07-02 2023-01-06 Psa Automobiles Sa Dispositif de decouplage vibratoire, notamment pour une pompe et un reducteur de vitesse de vehicule automobile

Also Published As

Publication number Publication date
EP2600003A1 (en) 2013-06-05
CN202971092U (zh) 2013-06-05
JP2013137093A (ja) 2013-07-11

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