US20050220614A1 - Fluid pump apparatus - Google Patents

Fluid pump apparatus Download PDF

Info

Publication number
US20050220614A1
US20050220614A1 US11/095,503 US9550305A US2005220614A1 US 20050220614 A1 US20050220614 A1 US 20050220614A1 US 9550305 A US9550305 A US 9550305A US 2005220614 A1 US2005220614 A1 US 2005220614A1
Authority
US
United States
Prior art keywords
impeller
blades
flow chamber
electric motor
blower
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
US11/095,503
Other languages
English (en)
Inventor
Kunihiro Tsuzuki
Shinichi Yokoyama
Akikazu Uchida
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TSUZUKI, KUNIHIRO, UCHIDA, AKIKAZU, YOKOYAMA, SHINICHI
Publication of US20050220614A1 publication Critical patent/US20050220614A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation

Definitions

  • This invention relates to a fluid pump apparatus, which compresses and pumps out fluid by rotation of an impeller having multiple blades, and in particular to an air supply pump in which fan noises can be reduced.
  • fan noises generated at the both sides of the impeller are interfered with each other to reduce sonic energies and thereby the fan noises.
  • the present invention is made in view of the above problems, and it is an object of the present invention to provide a fluid pump apparatus which reduces noises audible to the human beings to a small amount, by moving peak frequency of the noises to a higher value out of the audible frequency band.
  • the frequency (N ⁇ S) of fan noises at a primary peak appears at higher frequencies out of the audible frequency band, so that the noises audible to the human beings can be reduced.
  • fin pitch angles of the respective blades are made to be equal to each other.
  • the peak frequencies of the fan noises can be centralized on one point (frequency) according to such feature, and the variation of the peak frequency at the primary peak is avoided. As a result, the frequency of the fan noises at the primary peak can be completely moved to the higher frequency out of the audible frequency band.
  • the number of blades of the impeller is so made to be a prime number, so that fan noises are prevented from appearing at other frequencies than that of the primary peak.
  • the fan noises of 0.5 peak are prevented from generating in the audible frequency band to the human beings.
  • the peak frequencies of the fan noises are prevented from de-concentrating and the peak frequency of the fan noises are prevented from generating in audible frequency band.
  • a blower is formed by a vortex flow type blower, which has a vortex flow chamber and an impeller rotatably supported in the vortex flow chamber.
  • a volume decreasing means such as a groove or an inclined surface, is formed in a partitioning portion, which is formed in the vortex flow chamber between a starting portion and an ending portion of the fluid flow.
  • a cross sectional area of the vortex flow chamber is gradually decreased at the ending portion of the vortex flow chamber in a rotational direction of the impeller (blades), so that pressure variation of the fluid is decreased when the blades come across the partitioning portion, to thereby reduce the fan noise (wind noise).
  • the fan noises can be reduced, in particular, when the primary peak of the fan noises passes through the audible frequency band during periods of starting and stopping the air pump.
  • FIG. 1 is a cross-sectional view of an air supply pump, according to an embodiment of the present invention.
  • FIG. 2 is a partial side view of a blower housing of the air supply pump shown in FIG. 1 ;
  • FIG. 3A is an enlarged partial front view of an impeller of the air supply pump shown in FIG. 1 ;
  • FIG. 3B is a partial side view of the impeller shown in FIG. 3A ;
  • FIG. 4 is a graph showing noise level according to the present invention.
  • FIG. 5 is a graph showing noise level according to the conventional apparatus.
  • the air supply pump compresses air and pumps out the compressed air.
  • the air supply pump is used, for example, in a secondary air supply system for an automotive engine, wherein the air supply pump supplies the compressed air into an exhaust pipe of the engine at an upstream side of a catalyst for purifying the exhaust gas.
  • the air supply pump which comprises a blower device having a double-blade and vortex flow type impeller, is shown as an example in the first embodiment.
  • the air supply pump as shown in FIG. 1 , comprises an electric motor 1 , the above mentioned blower device 2 , and an air duct portion 4 in which a filter 3 is arranged.
  • the electric motor 1 of this embodiment is a DC motor, which comprises a stator 7 having a cylindrical yoke 5 and multiple permanent magnets 6 fixed to an inner peripheral surface of the yoke 5 , a rotor (armature) 8 arranged in the stator 7 , a brush assembly 12 arranged in a motor housing 11 and having multiple brushes 10 which are in a sliding contact with a commutator 9 provided in the armature 8 .
  • the armature 8 comprises a rotational shaft 13 rotatably supported by the motor housing 11 and the stator 7 , an armature core 14 fixed to the shaft 13 , an armature coil wound on the armature core 14 , and the commutator 9 electrically connected to the armature coil.
  • the brush assembly 12 comprises multiple brushes 10 to be brought into the sliding contact with the commutator 9 , a brush holder 15 movably holding the brushes 10 therein, multiple springs 16 for urging the brushes 10 toward the commutator 9 , and a spacer 17 for firmly supporting the brush holder 15 in the motor housing
  • the blower device 2 has an impeller 21 of a double-blade vortex flow type, and a blower housing 22 .
  • the impeller 21 is formed into a disc shape, wherein multiple blades (fins) 21 a are formed at an outer periphery and at both sides of the disc-shaped impeller 21 .
  • a center portion of the impeller 21 is connected to an end of the rotational shaft 13 of the electric motor 1 by a connecting means 23 , so that the impeller 21 can be rotated integrally with the rotational shaft 13 .
  • the blower housing 22 comprises a first casing 25 fixed to the motor housing 11 by means of screws 24 , and a second casing 27 fixed to the first casing 25 by clips 26 .
  • a vortex flow chamber (fluid flow chamber) 28 is formed in the blower housing 22 , for compressing the air by the rotation of the multiple blades 21 a of the impeller 21 .
  • the vortex flow chamber 28 is formed into a C-shaped space formed at the outer peripheral portion of the impeller 21 (along the multiple blades formed at the outer periphery of the impeller), so that the air flows along this vortex flow chamber.
  • an air inlet port 31 is formed in the first casing 25 of the blower housing 22 , at a starting portion 28 a of the vortex flow chamber 28 (a portion at which the blades 21 a come into the vortex flow chamber in accordance with the rotation of the impeller 21 ).
  • the air inlet port 31 is communicated with a downstream side of the air duct portion 4 , as shown in FIG. 1 .
  • An air outlet port 32 is formed in the blower housing 22 at an ending portion 28 b of the vortex flow chamber 28 (a portion at which the blades 21 a exit from the vortex flow chamber in accordance with the rotation of the impeller), so that the compressed air is discharged through the air outlet port 32 .
  • the electric motor 1 When the electric motor 1 is connected to a battery (not shown) of a vehicle through a relay, the electric power is supplied to the electric motor 1 , and the shaft 13 and the impeller 21 are rotated together.
  • the multiple blades 21 are circumferentially moved (rotated) so that the air in the vortex flow chamber 28 is compressed, while the air is moved from the starting portion 28 a to the ending portion 28 b . Since a negative pressure is generated at the air inlet port 31 , the air is guided (sucked) from the air duct portion 4 through the air filter 3 toward the air inlet port 31 . On the other hand, since a positive pressure is generated at the air outlet port 32 , the air compressed in the vortex flow chamber 28 is discharged from the air outlet port 32 .
  • a rotational speed, at which the electric motor 1 is normally operated, is called as “a normal rotational speed”.
  • operational modes of the electric motor 1 is either “ON state (supply of the electric power)” or “OFF state (cut off of the electric power)”.
  • the rotational speed of the stable condition corresponds to the “normal rotational speed”.
  • a peak frequency of fan noise is moved to a higher frequency side out of an audible frequency band, so that a noise level audible to human beings is reduced.
  • the multiple blades (fins) 21 a are rotated in one direction and each of the blades 21 a gives flow velocity to the air.
  • a partitioning portion 33 is formed in the blower housing 22 for partitioning the vortex flow chamber 28 between the starting and ending portions 28 a and 28 b , as shown in FIG. 2 .
  • the frequency of the pulsation noise mainly depends on a cycle during which the blade 21 a comes across the air outlet port 32 .
  • the wind noise is generated by the variation of the air pressure, when the respective blades 21 a come across the partitioning portion 33 .
  • the frequency of the wind noise mainly depends on a cycle during which the blade 21 a comes across the partitioning portion 33 .
  • each of the pulsation noise and the wind noise is such a noise, wherein a frequency of the noise depends on the cycle during which the respective blades come across fixed portions (the air outlet port 32 and the partitioning portion 33 ).
  • a primary peak of the fan noise (the pulsation noise and the wind noise) appears at the cycle during which the blade 21 a comes across the fixed portions 32 and 33 ).
  • the primary peak of the fan noise appears at a frequency F (Hz), calculated by a multiplication of N and S, wherein N is a number of blades 21 a , and S is a rotational number of the electric motor for each second (rotation/sec).
  • the cycle (frequency) during which the blade 21 a comes across the fixed portions 32 and 33 is designed at a higher value than the audible frequency band when the electric motor 1 is operated at the “normal rotational speed” (at which the electric motor 1 is stably rotated at the constant speed with current supply).
  • the “audible frequency band” means a range of frequency within which the ordinal human being can hear the noise, whereas “the higher value than the audible frequency band” means a frequency at which the ordinal human being can not hear the noise.
  • the higher value is more than 20 kHz.
  • FIGS. 4 and 5 show the noise levels with respect to different noise frequencies, wherein FIG. 4 is a graph of the present invention and FIG. 5 is a graph of the conventional apparatus.
  • the frequency of the primary peak appears at a frequency (around 20.5 kHz) higher than 20 kHz, an upper limit of the audible frequency band, as shown in FIG. 4 .
  • the frequencies of the primary and 0.5 peaks appear within the audible frequency band, as shown in FIG. 5 , respectively at the frequency of 13 kHz and 6.5 kHz.
  • the frequency of 0.5 peak does not appear in the present invention.
  • the fan noise (the pulsation noise and the wind noise) audible to the human beings is reduced to a smaller value.
  • the blades 21 a are formed at the both sides of the impeller 21 .
  • the fan noise (the pulsation noise and the wind noise) is generated at the both sides of the impeller 21 .
  • the number of blades of the front side is made to be the same to that of the back side, wherein the number is 79.
  • fin pitch angles between the neighboring blades 21 a on one side are made equal to each other over the entire periphery of the impeller 21 , as shown in FIG. 3A . This is also true on the other (back) side.
  • the position of the blades 21 a of one side (the front side) in the rotational direction is the same to that of the other (back) side.
  • the position of the blades of one side can be displaced by a half pitch (at a point at which modulation point is zero) from the blades of the other side.
  • the peak frequencies of the fan noises can be centralized to one point (frequency) of the primary peak, and the frequency of the primary peak is not varied at the normal (constant) rotational speed of the electric motor 1 . And thereby, the frequency of the primary peak can be completely moved to the higher range out of the audible frequency band to the human beings.
  • the number of the blades 21 a of the respective sides of the impeller is selected at a prime number, for example at the prime number of 79.
  • the impeller 21 is so designed that the primary peak of the fan noise appears at the frequency of 20.5 kHz.
  • the fan noises of a half (1 ⁇ 2) peak or a one-fourth (1 ⁇ 4) peak can be also prevented from appearing in the audible frequency band to the human beings. Namely, the de-concentration of the noise peaks can be prevented and thereby the noise peaks are prevented from appearing in the audible frequency band.
  • multiple (two)grooves 34 are formed in the partitioning portion 33 of the blower housing 22 at a side close to the ending portion 28 b of the vortex flow chamber 28 , so that the volume of the vortex flow chamber 28 is gradually decreased as the impeller 21 is rotated.
  • a cross sectional area of the grooves 34 is gradually decreased in a rotational direction of the impeller 21 .
  • the grooves 34 are formed in the both partitioning portions 33 respectively opposing to the side of the impeller 21 .
  • the number of grooves 34 shall not be limited to two, and one or three, or any other number of grooves can be formed.
  • the groove or grooves can be further replaced by an inclined surface formed on the partitioning portions 33 , at such positions at which the blades 21 a and/or the outer periphery of the blades come across the partitioning portions 33 .
  • the fan noises of the primary peak pass through the audible frequency band during periods of starting and stopping the operation of the electrical air pump, the fan noises can be likewise reduced.
  • a volume decreasing means The grooves and the inclined surface are collectively referred to as “a volume decreasing means” in this specification.
  • the present invention is applied to the electrical air pump which compresses and pumps out the air.
  • the present invention can be used in other pump devices which compress and pump out gas other than the air, or which compress and pump out a mixture of gas and liquid (in a steam phase).
  • the double-blade impeller is used.
  • the present invention can be also applied to the blower having a single-blade impeller, in which multiple blades are formed on one side of the impeller.
  • the present invention can be further applied to a centrifugal type blower or an axial flow type blower, other than the vortex flow type blower.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US11/095,503 2004-04-02 2005-04-01 Fluid pump apparatus Abandoned US20050220614A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004109909A JP2005291149A (ja) 2004-04-02 2004-04-02 流体駆動装置
JP2004-109909 2004-04-02

Publications (1)

Publication Number Publication Date
US20050220614A1 true US20050220614A1 (en) 2005-10-06

Family

ID=35054467

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/095,503 Abandoned US20050220614A1 (en) 2004-04-02 2005-04-01 Fluid pump apparatus

Country Status (4)

Country Link
US (1) US20050220614A1 (de)
JP (1) JP2005291149A (de)
CN (1) CN1690448A (de)
DE (1) DE102005015015A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070077138A1 (en) * 2005-09-29 2007-04-05 Denso Corporation Fluid pumping system
US20070227328A1 (en) * 2006-03-29 2007-10-04 Denso Corporation Rotary blade molding method, rotary blade molding die and rotary blade molded by the same
WO2010086210A1 (de) * 2009-01-29 2010-08-05 Pieburg Gmbh Seitenkanalgebläse, insbesondere sekundärluftgebläse für eine verbrennungskraftmaschine
WO2012041625A1 (de) * 2010-09-29 2012-04-05 Pierburg Gmbh Seitenkanalgebläse, insbesondere sekundärluftgebläse für eine verbrennungskraftmaschine
US20220160195A1 (en) * 2020-11-20 2022-05-26 Makita Corporation Cleaner and method for setting cleaner

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013224912A1 (de) * 2013-12-04 2015-06-11 Robert Bosch Gmbh Elektrische Maschine mit einem ersten und einem zweiten Gehäuseteil
CN109751256A (zh) * 2017-11-02 2019-05-14 苏州宝时得电动工具有限公司 高速电机及电动工具

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3973865A (en) * 1974-02-07 1976-08-10 Siemens Aktiengesellschaft Side-channel ring compressor
US4273515A (en) * 1976-04-07 1981-06-16 General Signal Corporation Liquid ring pump
US5302081A (en) * 1990-03-28 1994-04-12 Coltec Industries Inc. Toric pump
US5498124A (en) * 1993-02-04 1996-03-12 Nippondenso Co., Ltd. Regenerative pump and casing thereof
US5584653A (en) * 1992-09-08 1996-12-17 J. Eberspacher Device for reducing the generation of noise in fans
US5919030A (en) * 1996-03-29 1999-07-06 Sanyo Electric Co., Ltd Electric fan

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3973865A (en) * 1974-02-07 1976-08-10 Siemens Aktiengesellschaft Side-channel ring compressor
US4273515A (en) * 1976-04-07 1981-06-16 General Signal Corporation Liquid ring pump
US5302081A (en) * 1990-03-28 1994-04-12 Coltec Industries Inc. Toric pump
US5584653A (en) * 1992-09-08 1996-12-17 J. Eberspacher Device for reducing the generation of noise in fans
US5498124A (en) * 1993-02-04 1996-03-12 Nippondenso Co., Ltd. Regenerative pump and casing thereof
US5919030A (en) * 1996-03-29 1999-07-06 Sanyo Electric Co., Ltd Electric fan

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070077138A1 (en) * 2005-09-29 2007-04-05 Denso Corporation Fluid pumping system
US20070227328A1 (en) * 2006-03-29 2007-10-04 Denso Corporation Rotary blade molding method, rotary blade molding die and rotary blade molded by the same
WO2010086210A1 (de) * 2009-01-29 2010-08-05 Pieburg Gmbh Seitenkanalgebläse, insbesondere sekundärluftgebläse für eine verbrennungskraftmaschine
DE102009006652B4 (de) * 2009-01-29 2014-06-18 Pierburg Gmbh Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
WO2012041625A1 (de) * 2010-09-29 2012-04-05 Pierburg Gmbh Seitenkanalgebläse, insbesondere sekundärluftgebläse für eine verbrennungskraftmaschine
US9297276B2 (en) 2010-09-29 2016-03-29 Pierburg Gmbh Side channel blower, in particular a secondary air blower for an internal combustion machine
US20220160195A1 (en) * 2020-11-20 2022-05-26 Makita Corporation Cleaner and method for setting cleaner
US11653802B2 (en) * 2020-11-20 2023-05-23 Makita Corporation Cleaner and method for setting cleaner

Also Published As

Publication number Publication date
CN1690448A (zh) 2005-11-02
DE102005015015A1 (de) 2005-11-03
JP2005291149A (ja) 2005-10-20

Similar Documents

Publication Publication Date Title
US20050220614A1 (en) Fluid pump apparatus
KR100568183B1 (ko) 터보압축기
US5810557A (en) Fan wheel for an inline centrifugal fan
CN101255868B (zh) 电机内嵌叶片泵
CN106936230B (zh) 定子、电机和压缩机
JP3826508B2 (ja) 燃料ポンプ
US3601507A (en) Compact fluid compressor
JP2002106485A (ja) モータ一体型スクロール圧縮機
JP4951588B2 (ja) 電動送風機及びこれを備えた電気掃除機
KR20140137312A (ko) 펌프
DE59101986D1 (de) Axiallüfter mit zylindrischem Aussengehäuse.
WO1997009535A1 (en) A radial fan wheel
EP2035712A1 (de) Zentrifugallaufrad
JPH1119006A (ja) 電気掃除機
JP2007510853A (ja) 多段式の摩擦真空ポンプ
JP6375516B2 (ja) 電動送風機とそれを用いた電気掃除機
US6607351B1 (en) Vacuum pumps with improved impeller configurations
JPH05179941A (ja) 車両用触媒コンバータの二次空気供給用電動ポンプ
CN110630536A (zh) 风扇和电力机械总成及其方法
CN113374716A (zh) 高速电机以及吹风机
WO2019176625A1 (ja) 電動送風機、電気掃除機およびエアタオル
RU2799889C2 (ru) Вентилятор
JP2007162483A (ja) 過流ポンプ
JP5495204B2 (ja) 電動送風機および電気掃除機
JP2021514170A (ja) 空力的付加物を有するステータグレーティングを備えた電気機械

Legal Events

Date Code Title Description
AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TSUZUKI, KUNIHIRO;YOKOYAMA, SHINICHI;UCHIDA, AKIKAZU;REEL/FRAME:016445/0696

Effective date: 20050325

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION