EP1726828A1 - Compresseur frigorifique - Google Patents

Compresseur frigorifique Download PDF

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Publication number
EP1726828A1
EP1726828A1 EP06009113A EP06009113A EP1726828A1 EP 1726828 A1 EP1726828 A1 EP 1726828A1 EP 06009113 A EP06009113 A EP 06009113A EP 06009113 A EP06009113 A EP 06009113A EP 1726828 A1 EP1726828 A1 EP 1726828A1
Authority
EP
European Patent Office
Prior art keywords
passage
compressor according
outlet
aperture
refrigerant compressor
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.)
Granted
Application number
EP06009113A
Other languages
German (de)
English (en)
Other versions
EP1726828B1 (fr
Inventor
Holger Barth
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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.)
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Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP1726828A1 publication Critical patent/EP1726828A1/fr
Application granted granted Critical
Publication of EP1726828B1 publication Critical patent/EP1726828B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B39/0027—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
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • 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
    • F04B39/125—Cylinder heads

Definitions

  • the invention relates to a refrigerant compressor, in particular Verdrängerver emphasizer such as reciprocating compressor or scroll compressor, comprising a compressor housing with an outlet chamber enclosed by this and an outlet passage leading from the discharge chamber to a high pressure external port.
  • Verdrängerver emphasizer such as reciprocating compressor or scroll compressor
  • Such refrigerant compressors are known from the prior art. In these refrigerant compressors, especially when these reciprocating compressors, pulsations from the outlet chamber and into the adjoining piping system, which on the one hand lead to undesirable noise nuisance in the piping system and on the other hand lead to mechanical stress on the piping system due to the pressure peaks.
  • the invention is therefore based on the object to improve a refrigerant compressor of the generic type such that in this the pulsations are attenuated as much as possible.
  • the advantage of the solution according to the invention is the fact that the damper element can be inserted into the outlet passage in the cylinder head and thus requires relatively little space, in particular the fact that the damper element has no independent large damper chamber, but with respect to the volume required for damping with the outlet chamber interacts.
  • the damper element according to the invention suppresses a coupling between the discharge chamber acting as a spring for the pulsations in the mechanical analog and the quantity of refrigerant in the piping system effective as mass in the mechanical analog, so that pulsations can be optimally suppressed.
  • a particularly favorable solution provides that the damping element is designed so that form in this extinguishing standing waves at a higher harmonics of a fundamental frequency of the refrigerant compressor.
  • the advantage of this solution is the fact that the damper element can be designed to save space, since it is only designed so that form in this extinguishing standing waves not the fundamental frequency but a higher harmonic of the fundamental frequency of the refrigerant compressor, this for the suppression the pulsations is sufficient because the pulsations in the piping system not with the Fundamental frequency, but with a higher harmonic of the fundamental frequency occur, so that it is not necessary to interpret the damper element so that can form in this extinguishing standing waves of the fundamental frequency, which would have the consequence that the damper element must be designed very large volume. Rather, the design of the damper element for extinguishing standing waves extends at a higher harmonic of the fundamental frequency, which should, however, include the higher harmonics of the fundamental frequency, with which the pulsations occur primarily.
  • the frequency corresponding to the product of the speed of the refrigerant compressor multiplied by the number of discharges of refrigerant per revolution in the respective discharge chamber.
  • the passage could be provided as a breakthrough in the input aperture and in the respective output aperture.
  • a particularly favorable solution provides that the at least one passage in each of the diaphragms is formed by a pipe section reaching to the reflection space.
  • this piece of pipe is facing the intended on the other panel reflection surface.
  • such a passage has an inner opening, at which, with respect to the passage, a jump in the cross-section to the reflection space occurs, i. in that each of the at least one passage with a cross-sectional jump opens into a reflection space between the inlet aperture and the outlet aperture.
  • the damping effect of the damper element can be optimized in a simple manner.
  • the inner opening is arranged at a distance from the respective other aperture.
  • the inner opening of the respective other aperture is closer than the aperture having the respective passage.
  • the at least one pipe section of a diaphragm with an inner end portion is arranged overlapping with the pipe section of the respective other panel.
  • the pipe sections are connected to each other in the region of the inner end regions.
  • the at least one passage in one aperture has approximately the same passage cross-section as the at least one passage in the other aperture.
  • a particularly advantageous embodiment of a refrigerant compressor according to the invention provides that the inlet aperture has a plurality of passages.
  • the plurality of passages are arranged around a central axis of the damper element around.
  • a structurally particularly favorable solution provides that the plurality of passages are arranged rotationally symmetrical about the central axis.
  • the exhaust panel has a plurality of passages.
  • An optimal solution with regard to the flow conditions provides that the sum of the passage cross sections of the at least one passage of the inlet aperture amounts to more than 25% of a passage cross section of the outlet passage.
  • the sum of the passage cross sections of the at least one passage of the outlet aperture is more than 25% of the passage cross section of the outlet passage.
  • the damper element can be fixed via an outer mounting element.
  • one of the diaphragms is provided with flange areas serving as a mounting element and thus can simultaneously be used as a mounting flange for the damper element in the cylinder head.
  • a compressor housing 10, partially shown in FIG. 1, of a positive displacement compressor according to the invention comprises a cylinder housing 12 with a valve plate 14 on which a cylinder head 18, which forms an inlet chamber 22 and an outlet chamber 24 above the valve plate 14, is arranged, which are separated by a partition 26 in the cylinder head 18.
  • the cylinder head 18 is further provided with a connection stub 28, which is preferably arranged in a cover 30 of the cylinder head 18 and forms an outlet passage 32, through which the compressed refrigerant can exit the outlet chamber 24 and enter a pipe connection 34.
  • the pipe connection 34 can be placed on a connection surface 36 of the connecting piece 28 and can be mounted thereon.
  • damper element used, which, as shown in Figure 1 to 6, an inlet aperture 42 and an outlet 44 ,
  • damper element 40 leads to no increased space requirement in the compressor housing 10.
  • the inlet aperture 42 comprises two passages 46a and 46b formed by tube pieces 48a and 48b which extend from the outlet chamber 24 facing inlet openings 52a and 52b to the outlet aperture 44 facing first inner openings 54a and 54b over a distance RE.
  • the two passages 46a and 46b are preferably arranged symmetrically to a central axis 56 of the damper element 40. Further, the first inner openings 54a and 54b are at a distance AE from the Exhaust orifice 44 are removed and each face a closed reflecting surface 58a and 58b formed by the outlet orifice 44 of the outlet orifice 44, so that pulsations passing through the passages 46a and 46b first with a jump in cross section at the first inner orifices 54a, 54b into a space 50a, 50b, which is bounded by the outlet passage 32 and the outlet orifice 44, and then undergoes reflection at the reflecting surfaces 58a and 58b of the outlet orifice 44, thereby being partially reflected back through the passages 46a and 46b or into one outside the tube pieces 48a, 48b lying and surrounding these space 60a, 60b, which is bounded on the one hand by the outlet passage 32 of the connecting piece 28, on the other hand by the pipe sections 48a and 48b
  • reflection surfaces 62a and 62b are in turn associated with these opposing second inner openings 64a and 64b of these spaced AA passages 66a and 66b, so that with respect to the passages 66a, 66b, a jump in cross section between the second inner openings 64a, 64b and the reflection spaces 60a, 60b, wherein the passages 66a and 66b are formed on the side of the exhaust orifice 44, by pipe pieces 68a and 68b extending from the exhaust orifice 44 to the second inner orifices 64a and 64b, and at a distance RA from Outlet openings 70a and 70b arranged in the outlet orifice 44 are arranged in the inner openings 64a, 64b, with the outlet openings 70a and 70b facing the pipe connection 34, so that the compressed refrigerant emerging therefrom can flow out via the pipe connection 34.
  • the passages 66a and 66b are arranged symmetrically to the central axis 56, but offset by 90 ° relative to the passages 46a, 46b.
  • the second inner openings 64 are arranged at a distance AA from the inlet panel 42.
  • the distances AE between the inner openings 54a and 54b and the reflecting surfaces 58a and 58b and the distances AA between the inner openings 64a and 64b and the reflecting surfaces 62a and 62b are less than the lengths of the pipe sections 48a and 48b and 68a and 68b, so that the pipe sections 48a and 48b with their inner end portions 72a and 72b, and 74a and 74b overlap each other. Therefore, the tube pieces 48a and 48b and 68a and 68b are connected to each other in the region of their inner ends 72a and b and 74a and b, so that the tube pieces 48a and 48b and 68a and 68b keep the inlet aperture 42 and the outlet aperture 44 spaced apart.
  • the outlet orifice 44 is provided with flange regions 80, so that the outlet orifice 44 can be placed on the connection surface 36 with an interposed seal 82, while with a further seal 84, the is on the opposite side of the seal 82 of the flange 80, the pipe connection 34 is sealingly placed on the flange portion 80.
  • the damper element 40 according to the invention in a simple manner in the outlet passage 32 can be mounted, starting from the integrally connected to the flange 80 exhaust port 44, the pipe sections 68a and 68b and 48a and 48b extend into the outlet passage 32 and thus the inlet aperture 42 in the Outlet passage 32 defined hold in position.
  • the inlet aperture 42 has a diameter such that it extends substantially over the cross section of the outlet passage 32, so that compressed refrigerant can enter the damper element 40 only via the inlet openings 52.
  • the damper element 40 acts thereby pulsation damping, since in this pulsation waves which usually occur at frequencies corresponding to higher harmonics of the fundamental frequency are attenuated by reflection.
  • the condition for self-standing standing waves in the pipe sections 48a and 48b is that the length RE of the pipe sections 48a and 48b must correspond to half a wavelength ⁇ / 2 of a harmonic of the fundamental frequency due to the entrance openings 52a and 52b and the inner openings 54a and 54b reflections at open ends respectively.
  • the condition for canceling standing waves between the inner openings 54a and 54b and the reflecting surfaces 58a and 58b is that the length AE of a quarter wavelength ⁇ / 4 must correspond to a higher harmonic of the fundamental frequency, since reflections through the inner openings 54a and 54b at the open end and through the reflection surfaces 58a and 58b, reflections take place at the closed end.
  • the condition for canceling standing waves between the reflecting surfaces 58a and 58b, and 62a and 62b is that the distance BE of the half wavelength ⁇ / 2 of the higher harmonics must correspond to the fundamental frequency because of reflection between closed ends.
  • the damper element 40 is capable of attenuating a number of higher harmonics of the fundamental frequency, the distances RE, BE and RA being chosen so that twice that value corresponds to one of the lowest harmonics of the fundamental frequency occurring in the pulsations occurs and wherein the distances AE and AA are chosen so that their quadruple value corresponds to one of the lowest harmonics of the fundamental frequency at which the pulsations occur.
  • the exhaust chamber 24 on the one hand and the subsequent pipe 34 on the other hand still acts as a chamber for the pulsation damping, so that the damper element 40 itself does not require a large-volume chamber and thus permits a compact construction of the cylinder head 18, in which the damper element 40 can be easily integrated For its part, it only has to deflect and reflect pulsation waves.
  • the volume of the outlet chamber 24 is to be chosen so large that this at least twice, even better at least three times a stroke volume per cylinder of the reciprocating compressor corresponds to obtain the best possible damping effect.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP06009113.9A 2005-05-23 2006-05-03 Compresseur frigorifique Active EP1726828B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005024765 2005-05-23
DE102005029760A DE102005029760A1 (de) 2005-05-23 2005-06-20 Kältemittelverdichter

Publications (2)

Publication Number Publication Date
EP1726828A1 true EP1726828A1 (fr) 2006-11-29
EP1726828B1 EP1726828B1 (fr) 2015-08-05

Family

ID=36778241

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06009113.9A Active EP1726828B1 (fr) 2005-05-23 2006-05-03 Compresseur frigorifique

Country Status (4)

Country Link
US (1) US8317489B2 (fr)
EP (1) EP1726828B1 (fr)
JP (1) JP4365386B2 (fr)
DE (1) DE102005029760A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014166788A1 (fr) * 2013-04-10 2014-10-16 Bitzer Kühlmaschinenbau Gmbh Compresseur frigorifique

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8444397B2 (en) 2010-09-21 2013-05-21 Johnson Controls Technology Company Manual selective attenuator
US9366462B2 (en) * 2012-09-13 2016-06-14 Emerson Climate Technologies, Inc. Compressor assembly with directed suction
KR101560696B1 (ko) 2013-12-24 2015-10-15 동부대우전자 주식회사 압축기 및 토출 머플러
KR101543660B1 (ko) 2013-12-24 2015-08-11 동부대우전자 주식회사 압축기 및 맥동저감 밸브조립체
JP6532701B2 (ja) * 2015-02-27 2019-06-19 三菱重工サーマルシステムズ株式会社 開放型圧縮機
US10830239B2 (en) 2015-08-11 2020-11-10 Carrier Corporation Refrigeration compressor fittings
RU2737072C2 (ru) 2015-08-11 2020-11-24 Кэрриер Корпорейшн Компрессор, способ его использования и система паровой компрессии
WO2017058369A1 (fr) 2015-10-02 2017-04-06 Carrier Corporation Réseaux de résonateurs à compresseur à vis
US20180172195A1 (en) * 2016-12-16 2018-06-21 Ingersoll-Rand Company Integrated muffler and pulsation dampener for a compressor
US11236748B2 (en) 2019-03-29 2022-02-01 Emerson Climate Technologies, Inc. Compressor having directed suction
US11767838B2 (en) 2019-06-14 2023-09-26 Copeland Lp Compressor having suction fitting
US11248605B1 (en) 2020-07-28 2022-02-15 Emerson Climate Technologies, Inc. Compressor having shell fitting
US11619228B2 (en) 2021-01-27 2023-04-04 Emerson Climate Technologies, Inc. Compressor having directed suction

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DE19912926A1 (de) * 1999-03-22 2000-09-28 Bock Gmbh & Co Kaeltemaschinen Kolbenverdichter für Kältemittel
DE10011023A1 (de) * 2000-03-07 2001-09-13 Wolfgang Riese Schalldämpfer für Kompressoren
US20010050198A1 (en) * 2000-06-12 2001-12-13 An Kwang Hyup Muffler
GB2365066A (en) * 2000-07-28 2002-02-13 Draftex Ind Ltd Noise attenuation arrangements for pressurised-gas conduits

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Publication number Priority date Publication date Assignee Title
DE4118949A1 (de) * 1991-06-08 1992-12-10 Teves Gmbh Alfred Pumpe oder kompressor, in radial- oder axialkolbenbauart
DE19912926A1 (de) * 1999-03-22 2000-09-28 Bock Gmbh & Co Kaeltemaschinen Kolbenverdichter für Kältemittel
DE10011023A1 (de) * 2000-03-07 2001-09-13 Wolfgang Riese Schalldämpfer für Kompressoren
US20010050198A1 (en) * 2000-06-12 2001-12-13 An Kwang Hyup Muffler
GB2365066A (en) * 2000-07-28 2002-02-13 Draftex Ind Ltd Noise attenuation arrangements for pressurised-gas conduits

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014166788A1 (fr) * 2013-04-10 2014-10-16 Bitzer Kühlmaschinenbau Gmbh Compresseur frigorifique

Also Published As

Publication number Publication date
DE102005029760A1 (de) 2006-11-30
JP4365386B2 (ja) 2009-11-18
US8317489B2 (en) 2012-11-27
JP2006329197A (ja) 2006-12-07
EP1726828B1 (fr) 2015-08-05
US20060275150A1 (en) 2006-12-07

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