EP1647713A2 - Pompe pour fluide avec résonateur de Helmholtz - Google Patents

Pompe pour fluide avec résonateur de Helmholtz Download PDF

Info

Publication number: EP1647713A2
Authority: EP; European Patent Office
Prior art keywords: pump; resonator; pumping apparatus; pump body; cover
Prior art date: 2004-10-15
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.): Granted

Application number

EP05109513A

Other languages

German (de)

English (en)

Other versions

EP1647713A3 (fr

EP1647713B1 (fr

Inventor

Forte Michelantonio

Marco Simoni

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.)

CNH Industrial Italia SpA

Original Assignee

CNH Industrial Italia SpA

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.)

2004-10-15

Filing date

2005-10-13

Publication date

2006-04-19

2005-10-13 Application filed by CNH Industrial Italia SpA filed Critical CNH Industrial Italia SpA

2006-04-19 Publication of EP1647713A2 publication Critical patent/EP1647713A2/fr

2012-10-24 Publication of EP1647713A3 publication Critical patent/EP1647713A3/fr

2018-12-12 Application granted granted Critical

2018-12-12 Publication of EP1647713B1 publication Critical patent/EP1647713B1/fr

2025-10-13 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

Images

Classifications

- 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
- F04C15/0049—Equalization of pressure pulses
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/13—Noise

Definitions

the present invention relates to a pumping apparatus for fluids, in particular oil.
a pressure oscillation or so-called “ripple” is also produced, caused by the successive meshing of the gear teeth, in case the pump is a gear type pump. This "ripple" produces vibrations along the oil line and, hence, noise.
the line must therefore be fitted with a device for damping vibration within the frequency range of the pump.
the pump If powered by an internal combustion engine to pump oil to various external user devices (e.g. hydraulic steering, hydraulic actuators, etc.), the pump is also known to vary its speed as a function of engine speed, again causing vibrations.
various external user devices e.g. hydraulic steering, hydraulic actuators, etc.
vibration is damped using a resonator with a damping peak of around 2000 rpm, but which at the same time also provides for acceptable damping of vibration slightly above or slightly below this value.
a good resonator can damp vibrations ranging between 20% above and 20% below its rated design frequency.
the geometry of the resonator can also be altered so that it effectively damps only one frequency or a range of frequencies. In the latter case, however, efficiency is reduced as compared to a resonator which operates best with only one rated design frequency.
a Helmholtz resonator may be formed by a tube coaxial with another tube forming part of the oil circuit.
the inner tube, in which the oil flows, has at least one hole connected to the outer tubular resonator to fill the resonator chamber with oil, which remains stationary inside the chamber.
the stationary oil in the resonator chamber and the rigidity of the oil in the through hole act as a "mass-spring" system to damp vibration (and noise) produced by the pump.
the resonator Given the high pressures (as much as 200 bar) operating in the hydraulic systems in which it is installed, and the extensive surface area of the resonator, considerable forces are produced which the resonator, separate from the pump, must be able to withstand. As such, it must be mechanically strong enough. In addition, the resonator furthermore must be rigid enough to prevent its walls from flexing and initiating resonance phenomena which would defeat the purpose of the resonator itself.
a Helmholtz resonator in the pump itself, to eliminate or at least reduce structural noise transmission as well. Since a normal gear pump, for example, has two covers “sandwiching" the component parts of the pump, integrating the Helmholtz resonator in one of the pump covers is a valid solution.
Such an integrated resonator is described in GB-B-2.319.564.
the resonator chamber is connected to the outlet port of the pump and thus is not immediately effective in the area where the vibrations are generated.
substantive modifications of the pump body itself are required to adapt it to the cover in which the resonator chamber is incorporated. More specifically, apart from a supply channel inbetween the outlet port and the resonator chamber, additional seals around the supply channel are required to avoid leakage of oil inbetween the pump body and the cover holding the resonator chamber.
Number 10 in Figure 1 indicates a pump forming part of a pumping apparatus (shown only partly) which is the main object of the present invention.
pump 10 is a gear pump for pumping oil.
variable-eccentricity vane pumps e.g. variable-eccentricity vane pumps
pump 10 comprises a one-piece pump body 11 advantageously, though not necessarily, extruded from metal, in particular aluminium.
Pump body 11 comprises a casing 12 defining two communicating inner cavities 13a, 13b ( Figure 2).
Casing 12 has four longitudinal through holes 12a for the purpose explained in detail below.
Cavities 13a, 13b house respective rotors 14, 15 meshing with each other.
Rotor 14 is fitted to a drive shaft 16 driven around a longitudinal axis (a), and rotor 15 is driven, in use, by rotor 14.
Rotor 15 is connected to a shaft 17, having a longitudinal axis (b) parallel to axis (a).
Pump body 11 has an intake opening 18 (Figure 2) and an opposite delivery opening 19.
the wall of casing 12, in which opening 19 is formed, has a number of holes 19a ( Figure 2) for screwing on a delivery conduit (not shown) using known means, the conduit being connected to the hydraulic circuit.
Opening 18 has similar holes (not shown in Figure 2) for connecting an intake conduit (equally not shown).
the fluid being pumped in particular oil, is therefore drawn in, by rotation of rotors 14, 15, through intake opening 18 in known manner not described herein, and is pumped into the hydraulic circuit connected to delivery opening 19.
Cavities 13a and 13b in pump body 11 house a first bearing 20 and a second bearing 21.
First bearing 20 has two seats 20a, 20b for housing, in use, a portion 16a of shaft 16 and a portion 17a of shaft 17 respectively.
second bearing 21 (on the opposite side of rotors 14, 15) has two seats 21a, 21b for housing, in use, a portion 16b of shaft 16 and a portion 17b of shaft 17 respectively.
Cover 22 is of conventional design, and comprises a main body 22a, in which an opening 22b is formed through which an end 16c of shaft 16 protrudes (as best seen in Figure 1). End 16c is connected mechanically to drive means (not shown) for rotating rotor 14 (and therefore also rotor 15 meshing with rotor 14) to pump the fluid as required.
Four holes 25 are formed at the four corners of cover 22 to fix pump 10 to a support (not shown).
Cover 22 also has four dead holes (not shown) for a purpose explained in detail below.
a conventional elliptical seal is provided around the cavities 13a, 13b for sealing against a flat face of cover 22.
An identically shaped seal is provided on the rear face of pump body 11, to seal against cover 23.
cover 23 is located on the opposite side of pump body 11 and is shown in more detail in Figure 3. As will be seen, cover 23 houses a Helmholtz resonator 100 for damping at the outset any annoying vibration and relative noise produced in pump 10 by the fluid-pumping action of rotors 14 and 15.
Cover 23 comprises a main body 23a, in turn comprising four longitudinal through holes 23b, and a chamber 26 communicating with the outside solely through a hole 27 (see also Figure 2).
Chamber 26 and hole 27 substantially define Helmholtz resonator 100.
the oil for filling chamber 26 flows through hole 27, which, in use, communicates hydraulically with cavities 13a, 13b and is located on the delivery opening 19 side of pump 10.
the location of hole 27 is chosen such that it is directed to the pressurized area of the pump 10, in the vicinity of the point where the teeth of rotors 14 and 15 mesh. Hydraulic communication between this area and the hole 27 is guaranteed between the nip of the side surface of bearing 20 and its associated seat in the pump body 11.
bearing 20 is formed by two semi-circular parts which are placed onto each other, thereby adopting a figure eight configuration.
Seats 13a and 13b for their larger part obviously are also semi-circular but in contrast with bearing 20 have a transition area which is somewhat truncated, thereby forming a flat surface connection, as best seen in figure 2.
the small channel formed inbetween this flat surface and the outer surface of bearing 20 is advantageously employed to hydraulically connect resonator 100 to the pressurized side of pump 10, thus eliminating the need for drilling any additional connecting channels in the pump body 11.
a Helmholtz resonator 100 is thus integrated in pump 10 to damp, at the outset, vibrations produced by the teeth of the two meshing rotors 14 and 15.
each through hole 23b and a corresponding through hole 12a receive a respective bolt 28 (only two shown in Figure 1), the free end of which is screwed inside the corresponding dead hole (not shown) in cover 22.
One-piece pump body 11, the two bearings 20 and 21, and the two rotors 14 and 15 are thus "sandwiched" between covers 22 and 23, the latter having a Helmholtz resonator 100 in accordance with the invention.
a second Helmholtz resonator may obviously also be provided in cover 22, or in any convenient portion of one-piece pump body 11, without departing from the scope of the present invention.

Landscapes

Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Details And Applications Of Rotary Liquid Pumps (AREA)
Rotary Pumps (AREA)
Structures Of Non-Positive Displacement Pumps (AREA)

EP05109513.1A 2004-10-15 2005-10-13 Pompe pour fluide avec résonateur de Helmholtz Expired - Lifetime EP1647713B1 (fr)

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
ITBO20040639 ITBO20040639A1 (it)	2004-10-15	2004-10-15	Apparecchiatura di pompaggio per liquidi, in particolare per olio

Publications (3)

Publication Number	Publication Date
EP1647713A2 true EP1647713A2 (fr)	2006-04-19
EP1647713A3 EP1647713A3 (fr)	2012-10-24
EP1647713B1 EP1647713B1 (fr)	2018-12-12

Family

ID=35539636

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP05109513.1A Expired - Lifetime EP1647713B1 (fr)	2004-10-15	2005-10-13	Pompe pour fluide avec résonateur de Helmholtz

Country Status (2)

Country	Link
EP (1)	EP1647713B1 (fr)
IT (1)	ITBO20040639A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2008135159A1 (fr) *	2007-04-27	2008-11-13	Trw Automotive Gmbh	Pompe à engrenages comportant un clapet anti-retour et un clapet de limitation de pression
WO2010063664A1 (fr) *	2008-12-05	2010-06-10	Siemens Vai Metals Technologies Gmbh & Co	Procédé et dispositif pour la réduction semi-active des fluctuations de la pression dans un système hydraulique
DE102017206360A1 (de) *	2017-04-13	2018-10-18	Conti Temic Microelectronic Gmbh	Gehäuse für ein Pneumatik-Steuergerät und Pneumatik-Steuergerät
CN109209865A (zh) *	2018-11-21	2019-01-15	太原科技大学	一种抑制齿轮泵噪音的轴套及方法
CN112483401A (zh) *	2019-09-11	2021-03-12	复盛实业(上海)有限公司	排气轴承座及压缩机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
GB2319564B (en)	1996-11-22	2000-08-23	Cassapa S P A	Hydraulic Pump with Reduced Pressure Ripples

Family Cites Families (6)

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DE9314146U1 (de) *	1993-09-18	1995-01-26	Sihi GmbH & Co KG, 25524 Itzehoe	Flüssigkeitsringgaspumpe
JPH1082385A (ja) *	1996-09-09	1998-03-31	Ishikawajima Harima Heavy Ind Co Ltd	リショルム型コンプレッサのケーシング構造
DE19818141C2 (de) *	1998-04-23	2003-04-30	Trw Fahrwerksyst Gmbh & Co	Verfahren zur Begrenzung des von einer Hydraulikpumpe bereitgestellten Drucks sowie Hydraulikpumpe zur Durchführung des Verfahrens
KR100286837B1 (ko) *	1998-07-15	2001-05-02	구자홍	로터리 압축기의 공명기
JP2000320479A (ja) *	1999-05-12	2000-11-21	Mitsubishi Electric Corp	多気筒密閉型圧縮機
DE20302535U1 (de) *	2003-02-17	2003-06-18	TRW Fahrwerksysteme GmbH & Co. KG, 40547 Düsseldorf	Hydraulikpumpe für ein Servolenksystem

2004
- 2004-10-15 IT ITBO20040639 patent/ITBO20040639A1/it unknown
2005
- 2005-10-13 EP EP05109513.1A patent/EP1647713B1/fr not_active Expired - Lifetime

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
GB2319564B (en)	1996-11-22	2000-08-23	Cassapa S P A	Hydraulic Pump with Reduced Pressure Ripples

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2008135159A1 (fr) *	2007-04-27	2008-11-13	Trw Automotive Gmbh	Pompe à engrenages comportant un clapet anti-retour et un clapet de limitation de pression
WO2010063664A1 (fr) *	2008-12-05	2010-06-10	Siemens Vai Metals Technologies Gmbh & Co	Procédé et dispositif pour la réduction semi-active des fluctuations de la pression dans un système hydraulique
CN102271832A (zh) *	2008-12-05	2011-12-07	西门子Vai金属科技有限责任公司	用于半有源降低液压系统内压缩振荡的方法和装置
DE102017206360A1 (de) *	2017-04-13	2018-10-18	Conti Temic Microelectronic Gmbh	Gehäuse für ein Pneumatik-Steuergerät und Pneumatik-Steuergerät
DE102017206360A8 (de) *	2017-04-13	2021-07-15	Conti Temic Microelectronic Gmbh	Gehäuse für ein Pneumatik-Steuergerät und Pneumatik-Steuergerät
DE102017206360B4 (de)	2017-04-13	2022-05-19	Conti Temic Microelectronic Gmbh	Gehäuse für ein Pneumatik-Steuergerät und Pneumatik-Steuergerät
CN109209865A (zh) *	2018-11-21	2019-01-15	太原科技大学	一种抑制齿轮泵噪音的轴套及方法
CN112483401A (zh) *	2019-09-11	2021-03-12	复盛实业(上海)有限公司	排气轴承座及压缩机

Also Published As

Publication number	Publication date
EP1647713A3 (fr)	2012-10-24
EP1647713B1 (fr)	2018-12-12
ITBO20040639A1 (it)	2005-01-15

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US5791309A (en)	1998-08-11	Balancer shaft supporting structure in engine
KR101628674B1 (ko)	2016-06-09	모터 펌프 조립체
CN100526649C (zh)	2009-08-12	带有消声器的螺杆压缩机
JP2001317320A (ja)	2001-11-16	内燃機関の潤滑装置
EP1647713B1 (fr)	2018-12-12	Pompe pour fluide avec résonateur de Helmholtz
JP4224378B2 (ja)	2009-02-12	オイルポンプ
KR850001182Y1 (ko)	1985-06-12	밀폐형 압축기
JP2006517634A (ja)	2006-07-27	複合ポンプ
EP0828079B1 (fr)	2003-03-12	Compresseur du type Lysholm
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KR100213983B1 (ko)	1999-08-02	스크류 진공펌프
KR20180086326A (ko)	2018-07-31	하우징 일체형 분리판을 갖는 지로터 펌프
CN107869438B (zh)	2019-06-25	电机油泵总成、转向系统和车辆
US20050106044A1 (en)	2005-05-19	Oil pump
EP2140141B1 (fr)	2017-02-22	Pompe à deux étages ayant des supports de charge intermittents à mi-arbre
JPH0454804Y2 (fr)	1992-12-22
JP4221541B2 (ja)	2009-02-12	燃料ポンプ
CN107869443B (zh)	2019-07-26	电机油泵总成、转向系统和车辆
CN107869440B (zh)	2019-11-08	电机油泵总成、转向系统和车辆
KR20200115803A (ko)	2020-10-08	터보차저 결합기구 및 터보차저가 결합된 엔진
JPH09184592A (ja)	1997-07-15	脈動低減装置
CN119042271B (zh)	2025-03-18	液压作动系统及减振装置
JPH1047259A (ja)	1998-02-17	内燃機関のオイルポンプ

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