EP1890037A1 - Compresseur - Google Patents

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Publication number
EP1890037A1
EP1890037A1 EP06016421A EP06016421A EP1890037A1 EP 1890037 A1 EP1890037 A1 EP 1890037A1 EP 06016421 A EP06016421 A EP 06016421A EP 06016421 A EP06016421 A EP 06016421A EP 1890037 A1 EP1890037 A1 EP 1890037A1
Authority
EP
European Patent Office
Prior art keywords
compressor according
cylinder
intake
pipe
intake pipe
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.)
Withdrawn
Application number
EP06016421A
Other languages
German (de)
English (en)
Inventor
Alfred Deubler
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.)
Duerr Dental SE
Original Assignee
Duerr Dental SE
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 Duerr Dental SE filed Critical Duerr Dental SE
Priority to EP06016421A priority Critical patent/EP1890037A1/fr
Priority to DE202006012971U priority patent/DE202006012971U1/de
Priority to AT0064706U priority patent/AT9532U1/de
Priority to IT000330U priority patent/ITMI20060330U1/it
Priority to US11/834,297 priority patent/US20080085196A1/en
Publication of EP1890037A1 publication Critical patent/EP1890037A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections

Definitions

  • the invention relates to a compressor according to the preamble of claim 1.
  • Such a compressor is the EP 0 335 362 B1 refer to. It is characterized by compact dimensions with good conveying characteristics and smoothness.
  • the intake ports of the various cylinders are each provided with an intake pipe whose length is long compared to the clear cross-section of the intake pipe. In this way, the intake noise is significantly reduced.
  • the reduction of the total noise level obtained by the intake pipe is about 3 to 9 dB (A) at medium listening frequencies of about 100 Hz to 2 kHz.
  • the claim 2 calls preferred ratios between the length of the intake pipes and their inner diameter.
  • the intake filter can contribute to the sound attenuation.
  • a compressor, as indicated in claim 6, has particularly favorable flow conditions at the ends of the intake pipes, which also has a favorable effect on the noise.
  • the claim 7 calls particularly proven curvature conditions for the end of the intake pipes provided in the intake.
  • the development of the invention according to claim 8 is in view of favorable flow conditions at the inlet of the intake manifold advantageous.
  • Diameter of the intake duct as stated in claim 9, have proven particularly for compressors of medium flow rate (40 to 250 1 / min), as they are often used in dental offices.
  • the longer straight pipe section can be parallel to an outer surface of the cylinder, when the cylinder-side end of the intake pipe is connected to an air intake opening, which, as is often customary, provided in the cover of the cylinder.
  • the development of the invention according to claim 13 is in view of the advantage, on the one hand to achieve the greatest possible sound attenuation, on the other hand still unthrottled access of the air to ensure the intake of the intake pipes.
  • a compressor according to claim 17 is particularly compact.
  • the intake areas of the cylinder units are spatially separated.
  • a compressor according to claim 18 flows into the inlet ends of the intake pipes relatively cool air, which contributes to a better cylinder filling.
  • the V-type two-cylinder compressor shown in the figures has a drive unit, generally designated 10, which comprises an electric motor 12 and a crank drive unit 14.
  • the crank drive unit 14 has a housing 16 into which the shaft of the electric motor 12 is drawn.
  • the latter carries there two angularly offset crank pin, which also drive via connecting rods piston not shown.
  • the housing 16 of the crank drive unit 14 is closed at the front by a grid 18, behind which there is a fan wheel 20 driven by the motor shaft. This serves to suck in cooling air for the drive unit 14 and the electric motor 12.
  • the housing 16 of the drive unit 14 has a substantially square prismatic geometry, and on each of its two outer surfaces a compression unit 22 is placed.
  • Each of the compression units 22 comprises a cylinder block 24, a cylinder cover 26 closing its radially outer end, and the piston running inside the cylinder block 24, not shown in the drawing.
  • an inlet valve and an outlet valve are housed, as more specifically the EP 0 335 362 B1 refer to.
  • the inlet valve of the compression units 22 is in each case connected to a filter chamber 28, which is designed to run parallel to the cylinder axis at one of the corners of the cylinder block 24.
  • the outer end of the filter chamber 28 is closed by a fitting 30, which has a central passage 32.
  • a filter cartridge 34 is attached, which retains impurities in the intake air and after removal of the fitting 30 can be replaced.
  • the fitting 30 has at its free, upper end a radial mounting flange 36 which can cooperate detent with a locking groove 38 which is provided at the cylinder-side end of a total of 40 designated suction pipe.
  • the intake pipe has a shape similar to a walking stick and comprises a cylinder-side bent pipe section 42 and a rectilinear pipe section 44 borne by this.
  • the bent pipe section 42 has a circumferential extent of 180 °. Its diameter is chosen so that the straight pipe section 44 extends at a small distance above the outer surface of the cylinder block 24.
  • the pipe sections 42 and 44 together form a correspondingly curved intake passage 46 which leads back from the upper end of the cylinder block 24 to the outer surface of the housing 16.
  • the intake pipe 40 is provided with a toroidal bead 48, which seen in axial section circumferential extent is about 270 °. It connects the outer surface of the intake pipe 40 bumplessly with the end of the intake passage 46.
  • such an intake pipe 40 as it is used in compressors with a capacity of about 120 1 / min and a connection value of the electric motor 12 of about 1, 5 kW, the length of the pipe section 44 is about 110 mm, the radius the center line of the pipe section 42 is about 16 mm, the clear diameter of the intake passage 46 about 8 mm and the wall thickness of the intake pipe 40 about 4 mm at the free end and 6 mm at the cylinder end.
  • the rectilinear pipe section 44 of the intake pipe 40 extends over slightly more than 90% of the axial extent of the cylinder unit formed by the cylinder block 24 and the cylinder cover 26. In this way, the compressor sucks air from the proximity of the cool outer surface of the housing 16, but the flow cross-section still remains so large that no appreciable throttling of the sucked air between the end face of the intake pipe 40 and the outer surface of the housing 16 takes place.
  • the material for the intake pipe 40 is generally an elastomeric material, in particular a silicone material having a Shore A hardness of 50 to 70, preferably about 60.
  • the then obtained total noise insulation is based on the one hand on the sound attenuation in the interior of the filter cartridge 34, in the sound attenuation in the curved pipe section 42 where the sound waves encounter the wall material of the intake pipe 40 and are reflected from there, on the sound attenuation in the straight pipe section 44, where the sound waves are reflected several times until they reach the free end of the intake pipe 40, and on the sound attenuation by hitting the outside of the housing 16.
  • the sound attenuation through the plastic layer 50 and the pad 52 if these measures are foreseen.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP06016421A 2006-08-07 2006-08-07 Compresseur Withdrawn EP1890037A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP06016421A EP1890037A1 (fr) 2006-08-07 2006-08-07 Compresseur
DE202006012971U DE202006012971U1 (de) 2006-08-07 2006-08-23 Kompressor
AT0064706U AT9532U1 (de) 2006-08-07 2006-08-29 Kompressor
IT000330U ITMI20060330U1 (it) 2006-08-07 2006-09-25 Compressore
US11/834,297 US20080085196A1 (en) 2006-08-07 2007-08-06 Compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06016421A EP1890037A1 (fr) 2006-08-07 2006-08-07 Compresseur

Publications (1)

Publication Number Publication Date
EP1890037A1 true EP1890037A1 (fr) 2008-02-20

Family

ID=37596267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06016421A Withdrawn EP1890037A1 (fr) 2006-08-07 2006-08-07 Compresseur

Country Status (5)

Country Link
US (1) US20080085196A1 (fr)
EP (1) EP1890037A1 (fr)
AT (1) AT9532U1 (fr)
DE (1) DE202006012971U1 (fr)
IT (1) ITMI20060330U1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104641113A (zh) * 2012-09-26 2015-05-20 帝人制药株式会社 压缩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58158383A (ja) 1982-03-15 1983-09-20 Matsushita Electric Ind Co Ltd 密閉型電動圧縮機
FR2668211A1 (fr) 1990-10-22 1992-04-24 Daewoo Carrier Corp Resonateur pour compresseur rotatif hermetique.
US20020127123A1 (en) 2001-03-12 2002-09-12 Sung-Tae Lee Compressor
US20030235507A1 (en) 2002-06-20 2003-12-25 Chen Kwang-Tsan Miniature air compressor
US20040018098A1 (en) 2002-07-29 2004-01-29 Coleman Powermate, Inc. Air compressor housing
US20060124385A1 (en) * 2004-12-10 2006-06-15 Ingersoll-Rand Company Modular pressure pulsation dampener

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1622876A (en) * 1925-06-13 1927-03-29 Leo Hermann Air pump
US2298749A (en) * 1940-10-25 1942-10-13 Copeland Refrigeration Corp Refrigerating mechanism
US3734122A (en) * 1972-02-14 1973-05-22 Sybron Corp Dental compressed air/vacuum apparatus
US6524080B2 (en) * 2000-04-11 2003-02-25 R. K. Dewan & Co. Hermetically sealed compressors
US20060206098A1 (en) * 2005-03-14 2006-09-14 Mike Fard Low vibration tube

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58158383A (ja) 1982-03-15 1983-09-20 Matsushita Electric Ind Co Ltd 密閉型電動圧縮機
FR2668211A1 (fr) 1990-10-22 1992-04-24 Daewoo Carrier Corp Resonateur pour compresseur rotatif hermetique.
US20020127123A1 (en) 2001-03-12 2002-09-12 Sung-Tae Lee Compressor
US20030235507A1 (en) 2002-06-20 2003-12-25 Chen Kwang-Tsan Miniature air compressor
US20040018098A1 (en) 2002-07-29 2004-01-29 Coleman Powermate, Inc. Air compressor housing
US20060124385A1 (en) * 2004-12-10 2006-06-15 Ingersoll-Rand Company Modular pressure pulsation dampener

Also Published As

Publication number Publication date
ITMI20060330U1 (it) 2008-02-08
US20080085196A1 (en) 2008-04-10
AT9532U1 (de) 2007-11-15
DE202006012971U1 (de) 2007-03-29

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