EP0300989A1 - Soupape à plateau pour compresseur - Google Patents

Soupape à plateau pour compresseur Download PDF

Info

Publication number
EP0300989A1
EP0300989A1 EP88890156A EP88890156A EP0300989A1 EP 0300989 A1 EP0300989 A1 EP 0300989A1 EP 88890156 A EP88890156 A EP 88890156A EP 88890156 A EP88890156 A EP 88890156A EP 0300989 A1 EP0300989 A1 EP 0300989A1
Authority
EP
European Patent Office
Prior art keywords
plate
valve
catcher
ring
damper
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
EP88890156A
Other languages
German (de)
English (en)
Other versions
EP0300989B1 (fr
Inventor
Friedrich Dipl.-Ing.Dr. Bauer
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.)
CESSIONE;HOERBIGER VENTILWERKE AKTIENGESELLSCHAFT
Original Assignee
ENFO Grundlagen Forschungs AG
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 ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
Publication of EP0300989A1 publication Critical patent/EP0300989A1/fr
Application granted granted Critical
Publication of EP0300989B1 publication Critical patent/EP0300989B1/fr
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
    • F04B39/1053—Adaptations or arrangements of distribution members the members being Hoerbigen valves
    • 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]
    • Y10T137/785—With retarder or dashpot
    • 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]
    • Y10T137/7859—Single head, plural ports in parallel
    • Y10T137/786—Concentric ports
    • 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]
    • Y10T137/7859—Single head, plural ports in parallel
    • Y10T137/7861—Annular head
    • Y10T137/7862—Central post on seat
    • Y10T137/7863—Stop
    • Y10T137/7864—With guide

Definitions

  • the invention relates to a plate valve for a compressor, with a valve seat, a catcher and a valve plate controlling through-channels in the valve seat, which consists of an outer ring and at least one inner ring, the rings being connected to one another by radial webs, and with springing for the valve plate, which consists of springs supported on the catcher and arranged above the outer ring, which only act on the outer ring.
  • Plane valves of this type are known in several versions.
  • the plates arranged between the valve seat and the catcher, which are moved in the stroke cycle of the compressor and hit the catcher and the valve seat at relatively high speeds, are subjected to high loads.
  • the valve plate is most stressed, which in many cases performs a wobbling movement due to uneven flows through the controlled medium, in which it first hits the catcher or the valve seat with its outer edge.
  • the invention has a further improvement of the plate valves of this type for compressors and has set itself the task of mitigating the surcharges of the valve plate, which is known to be the most stressed, both when opening and closing the valve, so that the life of the plate valve and its operational safety are increased accordingly.
  • the invention is based on the plate valve mentioned at the outset and consists of a combination of several measures. It is characterized in that the valve plate is composed of a closure plate made of softer material, e.g. plastic, and a guide plate made of harder, flexible material, e.g. steel, in such a way that the two plates rest on one another, the closure plate being the valve seat and the guide plate the catcher is facing, and that the outer ring of both plates, which is loaded only by the springs, is wider than the inner rings.
  • the closure plate which is made of softer material, preferably plastic, ensures a perfect seal and at the same time reduces the impact of the valve plate on the valve seat. At the same time supports the guide plate harder material such as steel from the softer closure plate and gives it the required strength and stability. It also serves for the uniform transmission of the spring forces to the individual rings of the closure plate. The wide outer ring reinforces the valve plate in the most stressed area and at the same time creates the necessary space for the springs. In addition, the concentration of the springs on the outer edge of the valve plate improves their parallel guidance during the lifting movement, so that the tendency to wobble is largely eliminated.
  • a damper plate is provided which is loosely inserted between the catcher and the guide plate and extends only over the area of the inner rings of the guide plate and the associated closure plate.
  • the damper plate reduces the impact of the valve plate on the catcher and makes it easier to detach the valve plate from the catcher during the closing movement.
  • the damper effect is particularly advantageous if the damper plate consists of concentric rings which are connected to one another by radial webs, and if at least one ring section between two adjacent radial webs is bent out of the plate plane in a wave shape. This design causes an additional resilient catch of the valve plate during the opening movement.
  • the ring sections of the steamer plate are narrower than the rings of the valve plate and / or the rings of the stop surface of the catcher that are axially aligned with them, then the area over which the adjacent plates rest on one another when the valve is open , reduced accordingly. This also reduces the adhesive force between the surfaces lying one on top of the other, so that even when an oil film appears on the surfaces, a disadvantageous adhesive force occurs Late closing of the valve would be avoided.
  • the same advantages can be achieved or, when used together, can be enhanced by cutting out part of the ring sections of the damper plate and passing through the webs in the cut-out areas until the ring after next. The reduction in the contact area results from the absence of one or more rings of the damper plate.
  • a further embodiment of the invention provides that at least two ring sections are bent out in a wave shape in different directions from the plane of the damper plate. This results in an increase in the spring action and an approximately even distribution over the surface of the damper plate.
  • the total thickness of the damper plate with bent-out ring sections should be smaller in the relaxed state than the free distance between the catcher and the guide plate in the region of the damper plate.
  • the spring force of the ring sections bent out of the damper plate acts only during the opening movement of the valve plate to cushion the impact, but avoids an increase in the closing force itself and thus a delay in the opening movement.
  • the catcher can have a flat stop surface against which the damper plate rests when the valve is open. This creates a gradation on the outer edge of the damper plate, so that the outer ring of the valve plate has a stroke greater by the thickness of the damper plate and can swing out a little before swinging out on the catcher.
  • This design is particularly advantageous if the damper plate is relatively thick and has ring sections bent out of it, which anyway absorb the spring plate.
  • the depth of the recess in the stop area of the fan gers is suitably smaller than the thickness of the damper plate in the unloaded state, so that the resilient ring sections come fully into effect.
  • the flow of the controlled medium through the valve can be improved in the invention in that both in the closure plate and in the guide plate the free slots between the outer ring and the subsequent inner ring are wider than the remaining slots between the inner rings.
  • This measure takes into account the wider design of the outer ring and brings about an adaptation of the area of the individual slots available for the flow to the flow quantity occurring in the respective area.
  • FIG. 1 shows an axial central section through a first embodiment of a plate valve according to the invention for a compressor
  • FIG. 2 shows a partial section of the valve plate in a top view
  • FIG. 3 shows a side view
  • FIG. 4 shows a top view of the damper plate
  • FIG. 5 shows a axial middle section through a further embodiment of the plate valve according to the invention, only the left valve half being shown.
  • the plate valve consists of a valve seat 1 and a catcher 2, which is fastened on the valve seat 1 with the aid of a screw 3. With its outer edge 4, the catcher 2 rests on the valve seat 1, a spacer ring 5 is arranged in the center between the valve seat 1 and the catcher 2.
  • the valve seat 1 through channels 6 for the medium controlled by the plate valve are recessed, which are controlled by a valve plate 7.
  • the valve plate 7 lies in an intermediate space 8 between the valve seat 1 and the catcher 2 and is guided with its inner edge on the outer surface of the spacer ring 5.
  • the catcher 2 has on its side facing the valve plate 7 a stop surface 9, on which a damper plate 10 rests. Are in the catcher Outflow openings provided for the controlled medium.
  • the valve plate 7 is composed of a closure plate 14 and a guide plate 15.
  • the closure plate 14 faces the valve seat 1 and is made of a softer material than the guide plate 13, e.g. made of a plastic material, and controls the through channels 6 of the valve seat 1.
  • the made of harder material, e.g. Steel guide plate 15 faces the catcher 2 and has the task of supporting and stabilizing the closure plate 14, which is made of less solid material.
  • the guide plate 15 distributes the spring force exerted by the springs 13 on the valve plate 7 over the entire surface of the valve plate 7.
  • the closure plate 14 and the guide plate 15 have the same plan and lie on one another. At most, they can be connected to each other at individual points or over their entire area, e.g. be glued.
  • the valve plate 7, that is to say both the closure plate 14 and the guide plate 15, consists of an outer ring 16 and a plurality of inner rings 17 which are connected to one another by radial webs 18.
  • the outer ring 16 of the closure plate 14 and the guide plate 15 is substantially wider than the inner rings 17.
  • the slots 19 between the outer ring 16 and the adjoining inner ring 17 are also wider than the remaining slots 19 between the inner rings 17.
  • FIG. 3 and 4 show the damper plate 10.
  • This also consists of concentric rings 20 which are connected to one another by radial webs 21 are. Some ring sections between the webs 21 are bent out of the plate plane in a wave shape. From Fig. 3 it can be seen that the ring portions 22 of the outermost ring 20 downward and the ring portions 23 of the middle ring 20 are bent upward. The innermost ring 20 is flat. The bends of the ring sections 22 and 23 are shown somewhat enlarged in FIG. 3. Any other deformation of the damper plate 10 is also possible within the scope of the invention, which results in a spring effect of the damper plate 10 in a certain range. As from fig.
  • the ring sections 23 are narrower than the ring sections 22 and also narrower than the innermost ring 20 of the damper plate 10.
  • the ring sections 23 are in particular also narrower than the plate rings 17 of the valve plate 7 and the stop surface 9 of the catcher 2 which cooperate with them this measure, the contact surface between the valve plate 7 and the damper plate 10 is reduced, which also reduces the adhesive force between the two plates, which occurs due to adhesive action if an oil film is present between the two plates 7 and 10 or the catcher 2.
  • Fig. 4 is also indicated by dashed lines 25 that the radial webs 21 can pass between the outer and inner ring 20 of the damper plate 10, the middle ring 20 with the ring portions 23 can thus be completely eliminated.
  • This design also reduces the contact surface between the damper plate 10 and the catcher 2 or the valve plate 7, so that the two plates can easily detach from the stop surface 9 of the catcher 2 and from one another when the valve is closed. All rings 20 of the damper plate 10 can also be narrower than the rings of the valve plate 7 or catcher 2.
  • the total thickness of the damper plate 10 with bent-out ring sections 22, 23 is smaller in the relaxed state than the free distance between the catcher 2 and the existing in the region of the damper plate 10 Guide plate 15 in the space designated 8 in FIG. 1.
  • the damper plate 10 is loosely inserted between the catcher 2 and the guide plate 15 so that it rests on the valve plate 7 when the valve is closed and follows its movements. It can also be seen that the damper plate 10 extends in the radial direction only over the inner rings 17 of the valve plate 7, the wider outer ring 16 being loaded only by the springs 13. However, it is also possible to clamp the damper plate 10 in the valve or to provide it with its own guide, for example with flexible handlebars.
  • valve plate 7 Due to the action of the springs 13 distributed over the circumference of the valve plate 7, stabilization and good parallel guidance of the valve plate 7 is achieved during the lifting movement. The tendency of the valve plate 7 to wobble and disadvantageous oblique impacts of the plate edge on the valve seat 1 or the catcher 2 are largely avoided.
  • a recess 24 for the damper plate 10 is provided in the stop surface 9 of the catcher 2.
  • the embodiment shown in FIG. 5 differs from this in that the stop surface 9 of the catcher 2 is flat, so that the damper plate 10 forms a small gradation in the region of the outer ring 16 of the valve plate 7. This has the effect that the outer ring 16 can perform a somewhat larger stroke movement than the inner rings 17, whereby its impacts on the catcher 2 are damped.
  • the valve plate 7 is also in the embodiment according to fig. 5 from a closure plate 14 and a guide plate 15, the outer ring 16 being wider than the inner rings 17.
  • the slot 19 between the outer ring 16 and the inner rings 17 is also wider than the other slots 19 between the inner rings 17, the outflow openings 11 in catcher 2 are somewhat wider in this area than in the central area of the plate valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Check Valves (AREA)
  • Compressor (AREA)
EP88890156A 1987-07-01 1988-06-17 Soupape à plateau pour compresseur Expired - Lifetime EP0300989B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0165687A AT398809B (de) 1987-07-01 1987-07-01 Plattenventil für einen kompressor
AT1656/87 1987-07-01

Publications (2)

Publication Number Publication Date
EP0300989A1 true EP0300989A1 (fr) 1989-01-25
EP0300989B1 EP0300989B1 (fr) 1991-01-23

Family

ID=3518128

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88890156A Expired - Lifetime EP0300989B1 (fr) 1987-07-01 1988-06-17 Soupape à plateau pour compresseur

Country Status (5)

Country Link
US (1) US4854341A (fr)
EP (1) EP0300989B1 (fr)
JP (1) JP2577444B2 (fr)
AT (1) AT398809B (fr)
DE (1) DE3861643D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU622183B2 (en) * 1988-05-31 1992-04-02 Hoerbiger Ventilwerke Aktiengesellschaft Ring valve
EP0498980A1 (fr) * 1991-02-14 1992-08-19 Dresser-Rand Company Clapet pour un cylindre droit comportant une chambre de compression de gaz
AU632212B2 (en) * 1991-04-08 1992-12-17 Garlock Pty Ltd Improved multiple-ring compressor valve
EP0399443B1 (fr) * 1989-05-26 1993-12-29 Fulton Thermatec Corporation Soupape de retenue avec plaque de déviation
EP1939451A2 (fr) 2006-12-22 2008-07-02 Hoerbiger Kompressortechnik Holding GmbH Soupape annulaire automatique
WO2019170883A1 (fr) 2018-03-08 2019-09-12 Burckhardt Compression Ag Soupape à plaque et son procédé de fonctionnement

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0572748B1 (fr) * 1992-06-02 1996-10-30 Maschinenfabrik Sulzer-Burckhardt AG Soupape annulaire pour compresseur à piston
US5669411A (en) * 1995-12-14 1997-09-23 Legros; Brian J. Compressor valve
CA2396712A1 (fr) 2000-01-11 2001-07-19 Neil C. Penza Plaque de soupape profilee
AT504695B1 (de) * 2006-12-22 2008-12-15 Hoerbiger Kompressortech Hold Saugventil mit abhebegreifer
US7540301B2 (en) * 2006-12-27 2009-06-02 Walter Tuymer Compressor valve
JP2010270824A (ja) * 2009-05-21 2010-12-02 Ihi Corp 往復動圧縮機の弁装置
CN104033633B (zh) 2009-11-18 2016-12-07 扎洛夫阀股份有限公司 簧阀模块及阀装配系统及方法
KR101230550B1 (ko) * 2010-11-08 2013-02-07 주식회사 만도 쇽업소버의 감쇠력 가변 밸브 조립체
ITFI20120048A1 (it) * 2012-03-08 2013-09-09 Nuovo Pignone Srl "automatic valve with a spring holder ring"
AT514712B1 (de) * 2013-09-04 2015-06-15 Hoerbiger Kompressortech Hold Ventilplatte für Gaswechselventile
USD746598S1 (en) * 2014-01-27 2016-01-05 Roger Alexander Herz Record album frame
US11293556B2 (en) 2014-11-05 2022-04-05 Nuovo Pignone Srl Automatic ring valve, shutters for automatic ring valves, and method for manufacturing said shutters
ITUB20150797A1 (it) * 2015-05-22 2016-11-22 Nuovo Pignone Tecnologie Srl Valvola per un compressore alternativo
EP3181969B1 (fr) 2015-12-14 2019-08-07 Hamilton Sundstrand Corporation Clapet anti retour
US10995866B2 (en) 2017-06-30 2021-05-04 Zahroof Valves Inc. Stacked valve assembly
GB2568483B (en) 2017-11-16 2022-06-22 Bae Systems Plc Suspension strut
EP3636921A1 (fr) * 2018-10-09 2020-04-15 Burckhardt Compression AG Soupape de siège, composants de soupape d'une soupape de siège et procédé de fabrication de composants de soupape d'une soupape de siège
CN112227860B (zh) * 2020-09-13 2022-06-07 中国人民解放军海军工程大学 双层隔离式缓冲止挡板机构

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE480326C (de) * 1925-05-15 1929-08-01 Demag Akt Ges Selbsttaetiges Ventil fuer Kompressoren und Pumpen
US1768844A (en) * 1922-04-10 1930-07-01 Sullivan Machinery Co Valve
DE1034438B (de) * 1955-06-06 1958-07-17 R U L Schmidthuber Plattenvent Ringplattenventil
AT228913B (de) * 1962-01-18 1963-08-12 Hoerbiger Ventilwerke Ag Mehrringventil
AT285021B (de) * 1968-07-12 1970-10-12 Hoerbiger Ventilwerke Ag Gewölbte Federplatte für Verdichterventile
GB1500391A (en) * 1974-05-13 1978-02-08 Thermoking Corp Gas compressor valve arrangement with wear resistance
US4532959A (en) * 1984-01-16 1985-08-06 Ingersoll-Rand Company Valving element for a plate-type valve

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE200669C (fr) *
US946012A (en) * 1908-08-21 1910-01-11 Albert F Christ Fence-wire-reeling apparatus.
US955018A (en) * 1909-01-29 1910-04-12 John D Twiggs Jr Valve.
US1116341A (en) * 1913-11-07 1914-11-03 Blake & Knowles Steam Pump Works Pump-valve.
US1695069A (en) * 1925-10-14 1928-12-11 Ingersoll Rand Co Plate valve
GB532178A (en) * 1938-08-18 1941-01-20 Frankfurter Maschb Ag Improvements relating to plate valves
DE722156C (de) * 1938-10-30 1942-07-03 Karl Rud Dienes Fa Ringplattenventil
US2870783A (en) * 1953-10-23 1959-01-27 Hoerbiger & Co Annular plate valve
AT295018B (de) * 1969-12-23 1971-12-27 Hoerbiger Ventilwerke Ag Plattenventil für Kolbenverdichter
AT288582B (de) * 1970-02-18 1971-03-10 Hoerbiger Ventilwerke Ag Plattenventil für Kolbenverdichter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1768844A (en) * 1922-04-10 1930-07-01 Sullivan Machinery Co Valve
DE480326C (de) * 1925-05-15 1929-08-01 Demag Akt Ges Selbsttaetiges Ventil fuer Kompressoren und Pumpen
DE1034438B (de) * 1955-06-06 1958-07-17 R U L Schmidthuber Plattenvent Ringplattenventil
AT228913B (de) * 1962-01-18 1963-08-12 Hoerbiger Ventilwerke Ag Mehrringventil
AT285021B (de) * 1968-07-12 1970-10-12 Hoerbiger Ventilwerke Ag Gewölbte Federplatte für Verdichterventile
GB1500391A (en) * 1974-05-13 1978-02-08 Thermoking Corp Gas compressor valve arrangement with wear resistance
US4532959A (en) * 1984-01-16 1985-08-06 Ingersoll-Rand Company Valving element for a plate-type valve

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU622183B2 (en) * 1988-05-31 1992-04-02 Hoerbiger Ventilwerke Aktiengesellschaft Ring valve
EP0399443B1 (fr) * 1989-05-26 1993-12-29 Fulton Thermatec Corporation Soupape de retenue avec plaque de déviation
EP0498980A1 (fr) * 1991-02-14 1992-08-19 Dresser-Rand Company Clapet pour un cylindre droit comportant une chambre de compression de gaz
AU632212B2 (en) * 1991-04-08 1992-12-17 Garlock Pty Ltd Improved multiple-ring compressor valve
EP1939451A2 (fr) 2006-12-22 2008-07-02 Hoerbiger Kompressortechnik Holding GmbH Soupape annulaire automatique
AT504693B1 (de) * 2006-12-22 2009-02-15 Hoerbiger Kompressortech Hold Selbsttätiges ringventil
WO2019170883A1 (fr) 2018-03-08 2019-09-12 Burckhardt Compression Ag Soupape à plaque et son procédé de fonctionnement
US11486505B2 (en) 2018-03-08 2022-11-01 Burckhardt Compression Ag Plate valve and method for operating same

Also Published As

Publication number Publication date
ATA165687A (de) 1994-06-15
US4854341A (en) 1989-08-08
DE3861643D1 (de) 1991-02-28
AT398809B (de) 1995-02-27
EP0300989B1 (fr) 1991-01-23
JP2577444B2 (ja) 1997-01-29
JPS6487887A (en) 1989-03-31

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