EP1180214A1 - Compresseur a refrigerant - Google Patents

Compresseur a refrigerant

Info

Publication number
EP1180214A1
EP1180214A1 EP00929315A EP00929315A EP1180214A1 EP 1180214 A1 EP1180214 A1 EP 1180214A1 EP 00929315 A EP00929315 A EP 00929315A EP 00929315 A EP00929315 A EP 00929315A EP 1180214 A1 EP1180214 A1 EP 1180214A1
Authority
EP
European Patent Office
Prior art keywords
piston
outlet opening
projection
sectional area
cross
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
EP00929315A
Other languages
German (de)
English (en)
Other versions
EP1180214B1 (fr
Inventor
Frank Holm Iversen
Preben Bjerre
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.)
Danfoss Deutschland GmbH
Original Assignee
Danfoss Compressors GmbH
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 Danfoss Compressors GmbH filed Critical Danfoss Compressors GmbH
Publication of EP1180214A1 publication Critical patent/EP1180214A1/fr
Application granted granted Critical
Publication of EP1180214B1 publication Critical patent/EP1180214B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04B39/0005—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 adaptations of pistons

Definitions

  • the invention relates to an axial piston refrigerant compressor with at least one piston-cylinder unit, the cylinder of which is closed by a valve plate which has at least one pressure valve with an outlet opening, a projection of the piston protruding into the outlet opening when the piston is nearby its top dead center.
  • an axial piston compressor is known with a recess in that part of the piston face which extends from the outlet opening of the pressure valve to the center of the piston face.
  • a piston projection can be provided in the recess, which cooperates with the outlet opening.
  • the piston projection should fill the outlet opening at top dead center as completely as possible in order to avoid its "harmful space", ie also to expel the gas contained therein and thereby increase the efficiency of the compressor.
  • the actual (free) cross-sectional area of the outlet opening is reduced when the piston approaches its upper point, so that the flow resistance in the outlet opening increases.
  • the flow conditions in the outlet opening and around the valve closure element can cause the compressed gas to form recirculation zones in part of the outlet opening.
  • the piston projection can increase the problem in that the distance between the projection and the outlet opening has already decreased to a flow restriction before the projection has reached the outlet opening.
  • the free cross-sectional area of the outlet opening can thus be considerably narrowed before the pressure valve opens.
  • the invention has for its object to provide an axial piston refrigerant compressor of the type mentioned, which has an even higher efficiency.
  • this object is achieved in that the outlet opening, the piston projection, the inside of the valve plate and the end face of the piston limit a flow channel with a continuous course of its axial cut edges over at least most of its circumference that the free cross-sectional area of the flow channel is so long through the smallest Cross-sectional area of the outlet opening is determined until the piston has reached a position during its pressure stroke which is below the top dead center by at least the height of the outlet opening, that during the further pressure stroke of the piston the relative decrease in the free cross-sectional area of the flow channel is less than the relative decrease of the volume of the pressure chamber and that at least 45% of the volume of the outlet opening in top dead center of the piston are filled by the projection.
  • the cross-sectional area of the outlet opening decreases towards the outside of the valve plate, that the cross-sectional area of the projection decreases towards its free end and that the cross-sectional areas of the outlet opening and of the projection change in the axial direction in such a way that the free cross-sectional area changes of the flow channel changes relatively less during piston movement than the volume remaining in the cylinder. It is thereby achieved that the flow resistance of the flow channel remains at a low value, while the flow or mass flow decreases during the pressure stroke of the piston.
  • the flow resistance of the flow channel can be determined by the smallest cross-sectional area of the outlet opening until the free end of the piston projection is aligned with the inside of the valve plate. This ensures an optimal gas outflow while the mass flow through the outlet opening is greatest.
  • the flow resistance of the flow channel through the smallest cross-sectional area of the outlet opening must be determined until 50% of the height of the piston projection has penetrated into the outlet opening. This achieves an optimal gas outlet until the piston speed is significantly reduced and the gas flow has decreased.
  • An advantageous embodiment consists in that an axial section through the outlet opening of the valve plate and the piston projection has curved cutting edges.
  • the cutting edge of the outlet opening can be steeper than that of the projection.
  • the compressor according to the invention can be designed such that the transitions between the valve plate surface and the outlet opening and the transition between the piston end face and the projection are continuous, the transition between the outlet opening and valve seat and the transition between the projection and the piston end face being rounded .
  • the gas discharge during the emptying of the cylinder can take place with almost no eddy formation, the flow resistance being reduced.
  • the outlet opening can be asymmetrical. This is advantageous if the outlet opening is offset from the center of the cylinder.
  • the outlet opening can be made symmetrical. This is advantageous if the outlet opening is close to the center of the cylinder.
  • the piston projection can also be designed asymmetrically. As a result, the projection can be adapted to an asymmetrical outlet opening. If the piston projection is symmetrical, it can be adapted to a symmetrical outlet opening.
  • FIG. 2 shows an axial section corresponding to FIG. 1 of a further known axial piston refrigerant compressor with an end projection of the piston
  • Fig. 3 is an axial section corresponding to Fig. 1 of a piston-cylinder unit of a first
  • FIG. 4 shows an axial section through a piston-cylinder unit of an embodiment of a refrigerant compressor according to the invention, somewhat modified compared to the embodiment according to FIG. 3, 5 likewise shows an axial section, corresponding to the previous figures, of part of a piston-cylinder unit of a third exemplary embodiment of a refrigerant compressor according to the invention,
  • FIG. 6 likewise shows an axial section, corresponding to the previous figures, of part of a piston-cylinder unit of a fourth exemplary embodiment of a refrigerant compressor according to the invention.
  • 7 shows an axial section corresponding to FIG. 4 of a piston-cylinder unit to illustrate the determination of the free cross-sectional area of the flow channel.
  • FIG. 8 shows an axial section corresponding to FIG. 3 of a piston-cylinder unit with two different piston positions.
  • a piston 1 is guided in a cylinder, not shown, which is closed by a valve plate 2.
  • the valve plate 2 is provided with a schematically represented pressure valve 3, which has a circular cylindrical outlet opening 4 in the valve plate 2 with a valve seat 5 formed on the outside of the valve plate 2 and a valve closure element 6 in the form of a plate.
  • the valve closure element 6 is lifted under the internal pressure of the cylinder against the force of a spring, not shown, from the valve seat 5 to open the pressure valve 3, or is designed as a leaf spring clamped on one side on the valve plate 2.
  • the volume of the outlet opening 4 acts as a "harmful space", which further reduces the efficiency of the compressor.
  • the known refrigerant compressor according to FIG. 2 differs from that according to FIG. 1 only in that the end face 8 of the piston 1 is provided with an approximately frustoconical projection 9 which partially fills the outlet opening 4.
  • the projection 9 can already restrict the flow before the projection 9 enters the outlet opening 4 and before the pressure valve 3 is opened.
  • the pressure valve 3 is opened, the flow velocity of the gas as it is pushed out of the cylinder by the piston 1 is greatest, so that a reduction in the cross-sectional area of the flow channel considerably reduces the efficiency of the compressor.
  • the end face 8 of the piston 1 is provided with a projection 10, which partially fills the outlet opening 11 of the pressure valve 3 at the top dead center of the piston 1, as indicated by the continuous boundary line of the piston 1 is shown.
  • the dashed lines represent the piston 10 in various lower positions.
  • the cross-sectional area or the diameter of the outlet opening 11 changes over its entire height H, i.e. the cross-sectional area or its diameter decreases continuously and non-linearly from the inside to the outside.
  • the transition from the inside 7 of the valve plate 2 to the outlet opening 11 is also rounded.
  • the projection 10 of the piston 1 also has a cross-sectional area that decreases continuously over its entire height and non-linearly towards its free end. The same also applies to the cross-sectional diameter of the projection 10. However, the rate of decrease in the cross-sectional area of the projection 10 is somewhat greater than that of the outlet opening 11. At the same time, the transition between the flat end face 8 of the piston 10 and the peripheral surface of the projection 10 is continuous or rounded .
  • a flow channel 12 is formed between the projection 10 and the outlet opening 11, the axial section edges of which are continuously curved in each axial section plane and the free cross-sectional area of which depends on the position of the piston 1, i.e. decreases during its pressure stroke.
  • the cross-sectional area of the flow channel 12 does not change abruptly, but continuously over the length of the flow channel.
  • the piston 1 While the piston 1 is moving from the lower position shown in broken lines in FIG. 3 to the top dead center, ie during its pressure stroke, it reaches the middle position shown in dashed lines. In this position the cross-sectional area of the flow channel is reduced. However, as the piston 1 approaches top dead center, its speed and thus also the mass or volume flow of the expelled gas decrease. Therefore, the cross-sectional area of the flow passage 12 can be reduced without increasing the pressure loss. At the top dead center of the piston 1, represented by the solid line, the cross-sectional area of the flow channel 12 is reduced to a minimum, but at the same time the gas flow (mass or volume flow) has decreased.
  • the efficiency of the compressor is increased by reducing the pressure loss during the evacuation of the cylinder and at the same time reducing the "harmful space".
  • FIG. 4 differs from that of FIG. 3 only in that the transition 13 between the valve seat 5 and the outlet opening 11 and the transition 14 between the end face of the projection 10 and its peripheral surface are continuously rounded.
  • the continuous transitions 13, 14 and the continuous transitions between the inside 7 of the valve plate 2 and the outlet opening 11 and between the end face 8 of the piston 1 and the circumferential surface of the projection 10 cause less eddies to occur in the gas flow, so that the recirculation zones and the flow noise can be reduced.
  • the outlet opening 15 of the pressure valve 3 is asymmetrical.
  • the projection 16 of the piston 1 is also correspondingly asymmetrical. That is, the slopes of the flanks of the outlet opening 15 and the protrusion 16 are different on opposite or opposite sides, left and right in the axial sectional view.
  • this exemplary embodiment corresponds to the exemplary embodiment according to FIG. 4.
  • the outlet opening 18 and the projection 19 are also asymmetrical, so that their axial section contours largely correspond to each other, and both are even closer than in the embodiment of FIG. 5 on the wall of the cylinder 17.
  • the gas flows during the pressure stroke when the pressure valve 3 is open, mainly from the left, approximately central region of the end face 8 in FIG. 6 to the outlet opening 18, the surfaces facing each other near the inside of the cylinder 17 can -li ⁇
  • outlet opening 18 and the projection 19 are provided with edges 20 and 21 which merge into partially cylindrical surfaces 22 and 23, respectively.
  • the arrangement of the outlet opening 18 in the immediate vicinity of the inside of the cylinder 17 enables both the outlet opening 18 and the suction opening (not shown) to be formed in the valve plate 2 with a larger diameter.
  • the projection 10, 16, 19 can fill at least approximately 45% of the volume of the outlet opening 11, 15, 18.
  • FIG. 7 illustrates the determination of the free cross-sectional area of the flow channel for a given position of the piston 1 using the example of the rotationally symmetrical shape of the outlet opening 11 and piston projection 12 shown in FIG. 4.
  • the free cross-sectional area generally contains that for the outflowing gas standing and the smallest geometric cross-sectional area determined by the "" clear width "" of the flow channel.
  • the free cross-sectional area can be determined mathematically for different courses of the axial cut edges of the outlet opening 11 and the piston projection 12.
  • a series of points 24 are defined on the axial cut edges of the outlet opening 11 over the entire height of the valve plate 2.
  • a plurality of points 25 are defined on the axial cut edges of the projection 12.
  • d eff 2 - ⁇ ja - d
  • d eff can be thought of as the diameter of a circular opening that has the same cross-sectional area as the annular gap between the inside of the outlet opening and the piston projection.
  • the point 24 on the axial cut edge of the outlet opening 11 is now connected in a corresponding manner to all points 25 of the projection, and values for d eff are determined. The smallest value found corresponds to the effective diameter of the flow channel for this point 24 in question.
  • the free cross-sectional area A of the flow channel 12 for a given piston position is determined from the overall smallest value d effmm of the effective one
  • A d e 2 ffmm - - results.
  • the respective volume V of the pressure chamber comprises the free volume in the cylinder and the volume of the dead space up to the upper end surface of the valve plate 2.
  • Pressure space decreases relatively faster than the free cross-sectional area A of the passage 12, whereby an increase in flow resistance and flow noise are avoided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur à réfrigérant qui comporte au moins une unité piston-cylindre et une plaque à soupape (2) qui présente au moins une ouverture d'évacuation (11). Le piston (1) est pourvu d'une saillie (10) qui pénètre dans l'ouverture d'évacuation (11) lorsqu'il se trouve à proximité de son point mort haut. Pour élever le degré d'efficacité et abaisser le niveau de bruit, il est prévu, selon l'invention, que l'ouverture d'évacuation (11), la saillie de piston (10), la plaque à soupape (2) et le piston (1) délimitent un canal d'écoulement (12), que la surface de section libre du canal d'écoulement (12) soit définie par la plus petite surface de section (11) jusqu'à ce que le piston (1), pendant sa course sous pression correspondant à au moins la hauteur (H) de l'ouverture d'évacuation (11), se trouve en-dessous de son point mort haut, que, pendant le reste de la course sous pression du piston (1), la réduction relative de la surface de section libre du canal d'écoulement (12) soit plus petite que la réduction relative du volume de la chambre de pression, et qu'au moins 45 % du volume de l'ouverture d'évacuation (11) soient occupés par la saillie du piston (1) lorsque celui-ci se trouve à son point mort haut.
EP00929315A 1999-05-25 2000-05-22 Compresseur a refrigerant Expired - Lifetime EP1180214B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19923611 1999-05-25
DE19923611 1999-05-25
PCT/DK2000/000271 WO2000071896A1 (fr) 1999-05-25 2000-05-22 Compresseur a refrigerant

Publications (2)

Publication Number Publication Date
EP1180214A1 true EP1180214A1 (fr) 2002-02-20
EP1180214B1 EP1180214B1 (fr) 2003-08-13

Family

ID=7908914

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00929315A Expired - Lifetime EP1180214B1 (fr) 1999-05-25 2000-05-22 Compresseur a refrigerant

Country Status (5)

Country Link
US (1) US6623258B1 (fr)
EP (1) EP1180214B1 (fr)
AU (1) AU4744300A (fr)
DE (1) DE50003277D1 (fr)
WO (1) WO2000071896A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPQ489799A0 (en) * 1999-12-24 2000-02-03 Orbital Engine Company (Australia) Proprietary Limited Improved fluid compressor
KR100922213B1 (ko) * 2003-06-13 2009-10-20 엘지전자 주식회사 밀폐형 압축기
ATE484678T1 (de) * 2003-07-31 2010-10-15 Arcelik As Verdichter
US7654283B2 (en) * 2003-10-21 2010-02-02 Seiko Epson Corporation Check valve and pump including check valve
KR100774485B1 (ko) 2005-08-26 2007-11-08 엘지전자 주식회사 압축기
WO2009132932A1 (fr) 2008-05-01 2009-11-05 Arcelik Anonim Sirketi Compresseur à circulation de fluide frigorigène améliorée
DE102008036999B4 (de) * 2008-08-07 2012-03-29 Danfoss Household Compressors Gmbh Kältemittelkompressor, Kolben eines Kältemittelkompressors und Kolbenanordnung
JP5533061B2 (ja) * 2009-06-12 2014-06-25 パナソニック株式会社 密閉型圧縮機および冷凍装置
KR101660537B1 (ko) * 2010-06-14 2016-09-27 한온시스템 주식회사 압축기
KR101261136B1 (ko) 2010-12-16 2013-05-06 한라비스테온공조 주식회사 압축기
JP5828136B2 (ja) * 2011-08-08 2015-12-02 パナソニックＩｐマネジメント株式会社 密閉型圧縮機
GB2499336A (en) * 2013-04-19 2013-08-14 Vilis Ivars Lietuvietis Interior heat exchanger for reciprocating gas compressor
JP6876463B2 (ja) * 2017-02-24 2021-05-26 株式会社前川製作所 圧縮機用ピストン、圧縮機及びヒートポンプユニット

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DE527635C (de) 1929-03-11 1931-06-20 John Frederick Nevinson Craig Kuehlvorrichtung fuer Kolbenmaschinen, insbesondere Luftkompressoren
US2190537A (en) * 1937-05-03 1940-02-13 Wiebicke Paul Diesel motor
DE1257578B (de) 1961-03-17 1967-12-28 Halbergerhuette G M B H Fluessigkeitskolbenpumpe
DE3032009A1 (de) * 1980-08-25 1982-03-04 Dienes Werke für Maschinenteile GmbH & Co KG, 5063 Overath Kolbenverdichter fuer kleinkaeltemaschinen
IT1200677B (it) * 1984-07-27 1989-01-27 Enfo Grundlagen Forschungs Ag Compressore alternativo con una valvola combinata di aspirazione e di mandata
US5203857A (en) * 1990-06-01 1993-04-20 Bristol Compressors, Inc. Gas compressor head and discharge valve construction
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See references of WO0071896A1 *

Also Published As

Publication number Publication date
US6623258B1 (en) 2003-09-23
WO2000071896A1 (fr) 2000-11-30
AU4744300A (en) 2000-12-12
DE50003277D1 (de) 2003-09-18
EP1180214B1 (fr) 2003-08-13

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