EP1831564B1 - Valve, in particular for compressors - Google Patents

Valve, in particular for compressors Download PDF

Info

Publication number
EP1831564B1
EP1831564B1 EP20050810999 EP05810999A EP1831564B1 EP 1831564 B1 EP1831564 B1 EP 1831564B1 EP 20050810999 EP20050810999 EP 20050810999 EP 05810999 A EP05810999 A EP 05810999A EP 1831564 B1 EP1831564 B1 EP 1831564B1
Authority
EP
European Patent Office
Prior art keywords
spring
turns
valve
obturator
seat
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.)
Expired - Lifetime
Application number
EP20050810999
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1831564A1 (en
Inventor
Massimo Schiavone
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.)
Dott ing Mario Cozzani Srl
Original Assignee
Dott ing Mario Cozzani Srl
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 Dott ing Mario Cozzani Srl filed Critical Dott ing Mario Cozzani Srl
Publication of EP1831564A1 publication Critical patent/EP1831564A1/en
Application granted granted Critical
Publication of EP1831564B1 publication Critical patent/EP1831564B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • F04B39/1033—Adaptations or arrangements of distribution members the members being disc valves annular disc valves
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased

Definitions

  • the present invention relates to a valve, and in particular relates to a valve for reciprocating compressors of the reciprocating type.
  • valves of the type currently used in said compressors are normally automatic valves, comprising a valve body, called the seat, consisting of a plate having, formed therein, a plurality of axial flow channels which may be concentric or non-concentric.
  • the opening and closing of said channels is performed by the obturator, a member which may consist of a plurality of elements or a single element.
  • the obturators are subject to the action of resilient stressing means, typically metal, cylindrical helical, compression springs.
  • the springs are housed inside a valve body (called "counter-seat") consisting of a plate in which the flow through channels are formed.
  • the abovementioned spring housings may also contain spring protection elements which are preferably made of thermoplastic material and which have the function of eliminating metal contact between the surface of the spring and the external metal parts, such as, for example, the walls of the housing formed in the counter-seat or the obturator itself.
  • said springs are of the compression type with a cylindrical helix or conical helix.
  • Said springs which are made of steel wire, are formed by a total number of turns, equivalent to the sum of the active turns and the non-active turns.
  • the non-active turns are in contact with the adjacent turns and moreover said turns are suitably ground at the ends to ensure a good axial stability of the said spring.
  • the springs constitute one of the most critical parts of the valve; in fact, the high opening/closing frequencies produce, on them and on the parts in contact with them, wear of varying nature and varying degrees. According to the state of the art, most of said wear, which is produced by the movement of the spring, has been analyzed and defined, and may be classified as follows:
  • a spring-loaded valve e.g. a check valve or a safety valve, comprising a coil spring which functions not only to bias a valve member toward its seat but also to retain the valve member in assembly with the valve.
  • a valve for the control of large-section flows with high operating frequency, and in particular for compressors or the like comprising a flow aperture and a closure device, said flow aperture comprising one or more orifices formed on a fixed body cooperating with said closure device and introduced into the flow channel, said closure device rotating with respect to an axis perpendicular to the plane on which said fixed body lies, and being equipped with driving means; said closure device is equipped with at least a hollow on the surface facing said fixed body which houses an insert, said insert being formed so as to be substantially complementary with said orifice of said fixed body.
  • an anular check valve for piston-type compressors in which a valve member is movable between a valve plate and a guard.
  • the valve member is loaded and guided by a helical spring which rests radially at opposite ends against cylindrical surfaces provided respectively on the guard and on the valve member.
  • a helical spring which rests radially at opposite ends against cylindrical surfaces provided respectively on the guard and on the valve member.
  • at least one end of the spring where it rests radially, has a machined finish so that it fits closely.
  • a radially outer surface of the end coil engages an inwardly facing surface on the valve, member.
  • a round wire spring is used.
  • the object of the present invention is therefore to provide a valve for compressors, in which the wear characteristics of the springs are optimized compared to that known in the cited documents and in the state of the art, and in which problems of interference between all the turns of the springs of the valve, both in the rest condition as in the compression condition, are almost eliminated, ensuring a greater working life of the compressor and a precise operation also at high frequencies.
  • the present invention therefore relates to a valve for reciprocating compressors according to claim 1.
  • the difference in diameter between the end turns, which are open conical terminal turns, and the turns immediately adjacent to them is twice the cross-section of the metal wire which forms the spring.
  • the end turns both have dimensions smaller than those of the immediately adjacent turns.
  • the valve according to the present invention may be provided with protection members which are preferably made of plastic material and are arranged inside the housing which accommodates the spring, so as to preserve further the wear thereof.
  • Figure 1 shows an embodiment of the valve according to the present invention
  • 1 denotes the seat of the said valve, comprising a plate 101 provided with a plurality of axial and eccentric through-holes 111 acting as flow ways for the fluid and having a central, axial, threaded, through-hole 201 with which the threaded end 306 of the bolt 6 mates.
  • the plate 101 also has formed therein the grooves 121 which communicate with the through-holes 111.
  • the central portion of the bolt 6 also has, mounted thereon, the bush 406 and the counter-seat 2 provided with a central axial through-hole 302; the seat 1, bush 406 and counter-seat 2 are fixed together by means of the nut 106 screwed onto the threaded end 206 of the bolt 6.
  • the axial through-ducts 102 are formed in the counter-seat 2.
  • the obturator 4 is arranged between the seat 1 and the counter-seat 2, being coaxial and concentric with the bush 406 and axially slidable along it by means of its central axial hole 304.
  • the obturator has, formed therein, eccentric apertures 104 which are staggered axially with respect to the axial holes 111 of the plate 101 of the seat 1, while these apertures are in alignment with the ducts 102 formed in the counter-seat 2.
  • the seat 1 and counter-seat 2 are moreover joined together by means of the pin 401 which is inserted inside the blind hole 301 formed in the plate 101 and passes through the hole 204 of the obturator 4 and enters into the blind hole 202 of the counter-seat 2.
  • the counter-seat 2 is also provided with the cylindrical housing 402 inside which the cylindrical helical compression spring 5 is arranged, the end turns 105 having a diameter smaller than that of the turns 205 immediately adjacent to them.
  • the inserts 412 and 422 are arranged inside the housing 402, said inserts being preferably made of thermoplastic material or the like and having the function of eliminating metal contact of the spring 5 with the associated housing 402.
  • the end wall of the insert 412 presses, owing to the action of the spring 5, against the surface of the obturator 4 which in the figure is shown open as a result of the action of the fluid flow which passes through the holes 111 in the plate 101 of the seat 1.
  • the spring 5 in this figure is shown compressed inside the housing 402.
  • FIG 2 shows a cross-sectioned detail of the valve according to Figure 1 ; identical parts are indicated by the same numbers.
  • the valve is shown here in the closed condition, with the obturator 4 which is in contact with the grooves 121 in the plate 101 which communicate, as can be seen in Figure 1 , with the holes 111 through which the fluid flows.
  • the spring 5 is shown here in the equilibrium condition, expanded compared to the condition shown in Figure 1 .
  • Figure 3 shows a plan view of the spring 5 which acts on the obturator 4 of the valve; as can be noted, the end turn 105 visible in the figure has a diameter smaller than that of the turn 205 adjacent to it.
  • Figures 4A and 4B highlight the fact that the presence of the inter-turn apertures, together with the difference in diameter between the open conical end turns 105 and the immediately adjacent turns 205 result in non-interference of all the turns over the useful working section.
  • the operating principle of the valve according to the present invention will become obvious from the description below.
  • the valve of the type shown in Figure 1 is normally used in compressors and operates with decidedly high opening and closing frequencies. Consequently, the resilient stressing means which act on the obturator 4 are subject to considerable wear and this irremediably affects proper operation of the valve.
  • the spring 5 has characteristics such as to ensure that it is damaged to a considerably lesser extent than the normal cylindrical helical springs.
  • One of the main causes of wear of the springs in question is associated with the fact that the said end turns lie in planes parallel to each other, perpendicular to the axis of the spring, but inclined with respect to the plane of extension of the helix, namely to the planes in which the other turns of the spring lie. This different inclination causes in fact a poor distribution of the load on the spring and makes it more prone to wear.
  • thermoplastic inserts 412 and 422 are inserted inside the housing 402 so that metal contact between the spring 5 and the walls of the counter-seat 2 and/or the obturator 4 is further eliminated.
  • the valve thus designed is able, on the one hand, to ensure, also at high frequencies, a precise operation and, on the other hand, the average life of the resilient stressing means and therefore the valve itself is prolonged considerably.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Check Valves (AREA)
  • Sliding Valves (AREA)
  • Lift Valve (AREA)
EP20050810999 2004-12-22 2005-11-18 Valve, in particular for compressors Expired - Lifetime EP1831564B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITGE20040116 ITGE20040116A1 (it) 2004-12-22 2004-12-22 Valvola, in particolare per compressori.
PCT/EP2005/056083 WO2006067011A1 (en) 2004-12-22 2005-11-18 Valve, in particular for compressors

Publications (2)

Publication Number Publication Date
EP1831564A1 EP1831564A1 (en) 2007-09-12
EP1831564B1 true EP1831564B1 (en) 2010-03-24

Family

ID=35583437

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050810999 Expired - Lifetime EP1831564B1 (en) 2004-12-22 2005-11-18 Valve, in particular for compressors

Country Status (11)

Country Link
US (1) US20090126807A1 (pt)
EP (1) EP1831564B1 (pt)
JP (1) JP5148287B2 (pt)
KR (1) KR101258303B1 (pt)
CN (1) CN101084375B (pt)
AT (1) ATE462080T1 (pt)
BR (1) BRPI0519219B1 (pt)
DE (1) DE602005020186D1 (pt)
ES (1) ES2342547T3 (pt)
IT (1) ITGE20040116A1 (pt)
WO (1) WO2006067011A1 (pt)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITFI20120048A1 (it) 2012-03-08 2013-09-09 Nuovo Pignone Srl "automatic valve with a spring holder ring"
KR102170295B1 (ko) * 2018-11-27 2020-10-28 (주) 지티씨 압축기용 밸브 조립체

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2327611A (en) * 1941-09-30 1943-08-24 Albert T Schelwer Coupling
AT243420B (de) * 1963-05-08 1965-11-10 Enfo Grundlagen Forschungs Ag Mehrringventil
AT239426B (de) * 1963-07-04 1965-04-12 Enfo Grundlagen Forschungs Ag Selbsttätiges Ventil, insbesondere für Kolbenverdichter
AT243421B (de) * 1964-08-14 1965-11-10 Hoerbiger Ventilwerke Ag Ringventil für Kolbenverdichter
US4120489A (en) * 1970-06-22 1978-10-17 Bebrueder Ahle Double truncoconical spring of wire with circular cross section
DE2506420C3 (de) * 1975-02-15 1982-03-11 Gebrüder Ahle, 5253 Lindlar Nichtzylindrische, gewundene Druckfeder aus Draht mit kreisförmigem Querschnitt, insbesondere zur Anwendung bei Kraftfahrzeugen
US4307751A (en) * 1979-11-29 1981-12-29 Edison International, Inc. Plate valve
US4612962A (en) * 1981-03-23 1986-09-23 Control Devices, Incorporated Spring-loaded valve
JPH01305110A (ja) * 1988-06-03 1989-12-08 Nhk Spring Co Ltd 内燃機関用バルブスプリング
JPH0219885U (pt) * 1988-07-22 1990-02-09
US5246215A (en) * 1989-06-16 1993-09-21 Nhk Spring Co., Ltd. Spring seat member with notch for ground spring end
JPH05106559A (ja) * 1991-10-17 1993-04-27 Tokico Ltd エアコンプレツサ
ATE144815T1 (de) * 1992-06-02 1996-11-15 Burckhardt Ag Maschf Ringventil für einen kolbenkompressor
JP3451689B2 (ja) * 1993-12-28 2003-09-29 ダイキン工業株式会社 圧縮機用逆止弁
IT1314504B1 (it) * 2000-03-02 2002-12-18 Cozzani Mario S R L Valvola per il controllo di flussi di grande sezione, in particolareper compressori o simili.
JP2002039070A (ja) * 2000-07-26 2002-02-06 Hitachi Ltd 圧縮機
EP1247982B1 (de) * 2001-04-04 2005-02-23 Hoerbiger Kompressortechnik Holding GmbH Ringplattenventil für Kolbenkompressoren
JP2003155975A (ja) * 2002-09-30 2003-05-30 Sanyo Electric Co Ltd 多段圧縮装置の弁機構

Also Published As

Publication number Publication date
DE602005020186D1 (de) 2010-05-06
EP1831564A1 (en) 2007-09-12
US20090126807A1 (en) 2009-05-21
ATE462080T1 (de) 2010-04-15
JP5148287B2 (ja) 2013-02-20
CN101084375A (zh) 2007-12-05
BRPI0519219A2 (pt) 2009-01-06
CN101084375B (zh) 2012-02-01
JP2008524510A (ja) 2008-07-10
WO2006067011A1 (en) 2006-06-29
ITGE20040116A1 (it) 2005-03-22
BRPI0519219B1 (pt) 2019-08-06
KR101258303B1 (ko) 2013-04-25
ES2342547T3 (es) 2010-07-08
KR20070085826A (ko) 2007-08-27

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