EP1998045A1 - Machine volumétrique avec soupapes coaxiales - Google Patents

Machine volumétrique avec soupapes coaxiales Download PDF

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Publication number
EP1998045A1
EP1998045A1 EP07109328A EP07109328A EP1998045A1 EP 1998045 A1 EP1998045 A1 EP 1998045A1 EP 07109328 A EP07109328 A EP 07109328A EP 07109328 A EP07109328 A EP 07109328A EP 1998045 A1 EP1998045 A1 EP 1998045A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
coaxial
annular piston
displacement machine
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Withdrawn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
EP07109328A
Other languages
German (de)
English (en)
Inventor
Klaus Reitzig
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.)
R Schafer & Urbach & Co KG GmbH
Original Assignee
R Schafer & Urbach & Co KG 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 R Schafer & Urbach & Co KG GmbH filed Critical R Schafer & Urbach & Co KG GmbH
Priority to EP07109328A priority Critical patent/EP1998045A1/fr
Publication of EP1998045A1 publication Critical patent/EP1998045A1/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Withdrawn legal-status Critical Current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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/109—Valves; Arrangement of valves inlet and outlet valve forming one unit
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve

Definitions

  • the present invention relates to a coaxial valve head displacement machine and the use thereof.
  • suction valve lifts In the construction of displacement machines for conveying fluids (gases and liquids), whether oscillating or rotating compressors or oscillating or rotating displacers, suction valve lifts have been the state of the art for many decades.
  • the suction valve lift is a proven alternative to the bypass valve design (also called recirculation valves) located in the delivery line when the engines are idle for a short time and frequently at a constant input speed to save energy. be operated without load, or with reduced power.
  • Typical applications for positive displacement machines e.g. Liquid pumps, with suction valve lift are found in the steel industry in the descaling of slabs, sheets and strands with high-pressure water jets of up to 1,000 bar in hydraulic press drives with up to 300 bar working pressure and in mining, there in the so-called “Long Wall Mining ", where plunger pumps aperiodically convey special pressure fluids into storage tanks (accumulators), which in turn feed the punches of the hydraulic longwall and port construction and occasionally also hydraulically driven mining machines with pressures of up to 600 bar.
  • accumulators storage tanks
  • a simple application of a suction valve lift in liquid pumps is often manually for the purpose of emptying pump heads by means of a spindle or eccentric suction valve lift.
  • An example of such systems are known from the prior art triplex series plunger pumps.
  • the present invention has now taken on the task of providing a positive displacement machine with a coaxial valve arrangement, in which also significantly higher operating pressures, in particular more than 400 bar, can be driven to provide a Saugventilanhebung.
  • the coaxial cylindrical body has peripheral suction passages closable by the coaxially disposed annular spring-loaded suction valve opposite the displacer working space and extending from outside to inside at an acute angle to the cylinder axis.
  • the means for Saugventilanhebung comprise at least two in the opposite direction to the spring force of the suction valve acted upon, arranged in Koaxialventil analyses pressure plunger.
  • the plunger acting in the opposite direction to the spring force on the suction valve e.g. extend on the compression springs opposite side of the intake parallel to the cylinder axis, allow an increase of the intake valve at idle. They can be easily integrated into the coaxial valve body as small components.
  • two, three or more oppositely arranged plunger are provided.
  • the coaxial valve body has a central pressure channel which can be closed by the coaxially arranged, spring-loaded pressure valve.
  • the means for Saugventilanhebung include an acted upon by a fluid annular piston, which is arranged axially displaceable in the Koaxialventil ecology to the pressure channel and the form, force or pressure-locking manner is connected to the plungers.
  • the annular piston is connected via connecting rods, e.g. Bolts, which protrude preferably perpendicular to the cylinder axis on the side facing away from the suction valve ends of the plunger, connected to the pressure rams form-, force or pressure-locked.
  • connecting rods e.g. Bolts, which protrude preferably perpendicular to the cylinder axis on the side facing away from the suction valve ends of the plunger, connected to the pressure rams form-, force or pressure-locked.
  • annular piston is connected directly to the pressure rams in a pressure-locked manner.
  • This embodiment in which, for example, a wider, on the plunger projecting annular piston used with a larger fluid acted upon face can be designed for very high flow rates.
  • At least two return springs are preferably arranged between the annular piston and the coaxial valve body. By the return springs of the annular piston is automatically reset when stopping the application of fluid.
  • a positive displacement machine according to the invention is for conveyed, in particular for gases and liquids, in particular at delivery pressures up to 1000 bar or even above, z. B. can be used in water promotion up to 7000 bar.
  • top and bottom which are used in the following, refer to those in FIG. 1 shown arrangement.
  • FIG. 1 shows a section through a two-part pump cylinder 1, 2 with a displacer 3 and above an associated valve head with a pump head housing 4 and a cover 5 of a positive displacement machine according to the invention with a Koaxialventilkopfan ever.
  • the pump head housing 4 is provided with a suction port 6. With the suction port 6 a plurality of intake ports 7 are connected, which lead to a spring-loaded, annular suction valve 8 of the valve head.
  • the suction valve 8 is formed by an annular disc, also called Saugventilteller.
  • the intake ports 7 are formed in a KoaxialventilAvem 9, which is arranged in the interior of the valve head, as bores. The intake ports 7 extend from the outside inward at an acute angle to the cylinder axis. They are distributed in a circle over the circumference and connected via a Ansaugringraum 7a in Koaxialventil emotions 9 with the suction port 6.
  • the Ansaugringraum 7 a is formed by an annular recess in the Koaxialventil ecology 9 between this and the pump head housing 4.
  • the intake ports 7 and the Ansaugringraum 7 a are in this embodiment in a lower cylindrical portion 9 a of the Koaxialventil stressess 9, to which an upper cylindrical portion 9 b and a ceiling portion 9 c of the Koaxialventil stressess 9 connect.
  • the valve head is at one, in FIG. 1 upper end of the pump cylinder 1, 2 arranged. At this end is one of the dead points of the displacer 3 and in the pump cylinder 1, 2 a displacer 10 is formed. At this displacement work space 10, the valve head and with him the suction valve 8 connects.
  • the spring load of the suction valve 8 is formed by a coil spring 11 which is disposed below the suction valve 8 within the pump cylinder 1, 2 and in the interior of which the upper end of the displacer 3 is immersed in the pressure stroke.
  • the displacer working chamber 10 merges at its upper end into a coaxial pressure channel 12 which is formed in the center of the annular suction valve 8 and above in the coaxial valve body 9, in its lower portion 9a, through a central axial bore.
  • the pressure channel 12 is closed at its upper end by a spring-loaded pressure valve 13.
  • the pressure valve 13 is in the coaxial valve body 9, in its upper portion 9 b, arranged in a pressure chamber 14 forming a central bore.
  • the pressure chamber 14 is connected to a pressure ring space 14b via a plurality of pressure channels 14a distributed in a circle over the circumference.
  • the pressure channels 14a are formed by bores and the pressure ring space 14b through an annular bore in the coaxial valve body 9.
  • the pressure ring space 14b is, as characterized by a port 14c, connected to an outlet opening, not shown.
  • the spring load of the pressure valve 13 is formed by a coil spring 15, which is arranged in the pressure chamber 14 and in the interior of which the pressure valve 13 is located.
  • the means for Saugventilanhebung have in this embodiment, an annular piston 18, a plurality of return springs 19, two connecting rods 20 and two push rod 21.
  • the plungers 21 are on opposite sides, i. offset by 180 ° to each other, arranged above the suction valve 8 and are acted upon in the opposite direction to the spring force of the suction valve 8 with force.
  • the push rods 21 extend parallel to the cylinder axis and are located in bores in the coaxial valve body 9, specifically in its lower portion 9a, in each case between two intake ducts 7.
  • the annular piston 18 For urging the plunger 21 with force of the annular piston 18 is provided, which is mounted axially displaceable in the Koaxialventil Sciences 9 and acted upon by the pressurized fluid.
  • the annular piston 18 is arranged coaxially around the pressure channel 12 and projects into an annular recess in the Koaxialventilanalysis 9, in its lower portion 9 a.
  • the annular piston 18 has a lower collar 18a and an upper collar 18b, wherein the collar 18a and 18b abut the coaxial body 9 on the outside via seals, the lower collar 18a at the lower portion 9a and the upper collar 18b abut the upper portion 9b.
  • a piston working chamber 22 is formed between an upper end surface of the annular piston 18 within the upper collar 18b and a lower annular surface of the coaxial valve body 9, namely the upper portion 9b.
  • the fluid line 17 opens into this piston working space 22.
  • a connecting rod 20 is provided which extends perpendicularly and thus radially to the cylinder axis, ie perpendicular to the direction of movement of the annular piston 18.
  • Each connecting rod 20 is arranged at its one end in a bore of the annular piston 18 and protrudes at its other end on the upper, the suction valve 8 remote from the end of the corresponding plunger 21.
  • the connecting rods 20 are thereby connected to the pressure rams pressure-sealed.
  • the annular piston 18 is arranged with its lower end face within the lower collar 18a at a distance from the opposite, lower annular surface of the recess of the Koaxial stressess 9, namely the lower portion 9a.
  • the return springs 19 supported the annular piston 18 relative to the Koaxialventilisson 9.
  • Each of the return springs 19 designed as helical springs sits with its lower end on the annular surface of the recess and protrudes with its upper end into a bore in the annular piston 18, which extends from the lower end face and extends parallel to the cylinder axis.
  • the return springs 19 are distributed in a circle over the circumference. There are at least three return springs 19 are provided.
  • the return springs 19 exert an axially acting restoring force on the ring body 18 away from the suction valve 8,
  • the displacer 3 oscillates in the pump cylinder 1, 2 back and forth, or is in FIG. 1 up and up, moving.
  • the suction valve 8 is opened automatically against the force of the coil spring 11.
  • suction valve 8 is conveyed into the pressure channel 12 of the coaxial valve body 9.
  • the conveyed material exits via the pressure valve 13, which is opened automatically during the pressure stroke and against the spring force 15, into the pressure chamber 14, the pressure channels 14a and the pressure ring chamber 14b at the outlet opening.
  • the fluid is supplied under pressure from, for example, about 10 bar via the inlet opening 16 in the channel 17, this acts in the piston working chamber 22 on the annular piston 18 and pushes it against the force of the springs 19 in the direction of the suction valve 8.
  • the in the Annular piston 18 inserted connecting rods 20 press on the plunger 21, which in turn press on the suction valve 8 and thus lead to the opening of the suction valve 8 while the pump is running.
  • the pressurization of the fluid is adjusted so that the return springs 19 move the annular piston 18 axially upward away from the suction valve 8. Normal operation can start again.
  • FIG. 2 shows in several views a further embodiment of the invention, as it is preferably used for positive displacement machines with a coaxial valve head arrangement for larger throughput volumes.
  • the suction valve 8 is made larger and loaded by a strong coil spring 11.
  • a strong coil spring 11 In the correspondingly modified coaxial valve body 23 adapted means for Saugventilanhebung are provided, which have an annular piston 24, a plurality of return springs 25 and two pressure plunger 26.
  • the annular piston 24 differs from the annular piston 18 in that it is formed as a disk-shaped, without lower and upper collar 18 a, 18 b, with a smaller height and a greater width and thus with larger end faces.
  • the annular piston 24 is located in an annular bore of the Koaxialventil analysess 23, wherein its lower end face is arranged at a distance from the opposite, lower annular surface of the annular bore.
  • the return springs 25 supported the annular piston 24 from the Koaxialventilintelligence 23, each of the coil springs formed as return springs 25 abuts with its upper end on the lower end face of the annular piston 24 and protrudes with its lower end into a bore in the Koaxialventilanalysis 23, from the lower Ring surface goes out and parallel to the cylinder axis.
  • the annular piston 24 is located closer to the cylinder axis than the annular piston 18.
  • the larger upper end surface of the annular piston 24 leads to a larger piston working chamber 27.
  • the pressure piston 26 are longer and protrude at its upper end into the annular space of the annular piston 24, i. the annular piston 24 itself is disposed above the upper ends of the push rod 26 and thereby connected to the pressure plunger 26 pressure-locked.
  • This embodiment allows for the same working pressure of the pneumatic and hydraulic actuation as in the first embodiment, larger actuation forces of the plunger 26th

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP07109328A 2007-05-31 2007-05-31 Machine volumétrique avec soupapes coaxiales Withdrawn EP1998045A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07109328A EP1998045A1 (fr) 2007-05-31 2007-05-31 Machine volumétrique avec soupapes coaxiales

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07109328A EP1998045A1 (fr) 2007-05-31 2007-05-31 Machine volumétrique avec soupapes coaxiales

Publications (1)

Publication Number Publication Date
EP1998045A1 true EP1998045A1 (fr) 2008-12-03

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ID=38667014

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07109328A Withdrawn EP1998045A1 (fr) 2007-05-31 2007-05-31 Machine volumétrique avec soupapes coaxiales

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EP (1) EP1998045A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016124422A1 (de) 2016-12-14 2018-06-14 Hammelmann GmbH Hochdruckplungerpumpe sowie Verfahren zur Funktionsunterbrechung eines Fluidstroms
IT201900020072A1 (it) * 2019-10-30 2021-04-30 Annovi Reverberi Spa Valvola bidirezionale automatica e pompa dotata di detta valvola
WO2024134450A1 (fr) * 2022-12-21 2024-06-27 Mixtron S.R.L. Ensemble soupape et pompe pourvue dudit ensemble soupape
WO2024134393A1 (fr) * 2022-12-21 2024-06-27 Mixtron S.R.L. Ensemble clapet de refoulement et d'aspiration automatiques et pompe pourvue dudit ensemble clapet

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2971690A (en) * 1958-10-24 1961-02-14 Worthington Corp Unloading means for a reciprocating compressor
US3209985A (en) * 1963-07-11 1965-10-05 Borg Warner Capacity control mechanisms
US3347264A (en) 1963-12-23 1967-10-17 Stuart E Bunn Suction and discharge valve
US3820922A (en) * 1972-05-30 1974-06-28 F Buse Multiplunger reciprocating pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2971690A (en) * 1958-10-24 1961-02-14 Worthington Corp Unloading means for a reciprocating compressor
US3209985A (en) * 1963-07-11 1965-10-05 Borg Warner Capacity control mechanisms
US3347264A (en) 1963-12-23 1967-10-17 Stuart E Bunn Suction and discharge valve
US3820922A (en) * 1972-05-30 1974-06-28 F Buse Multiplunger reciprocating pump

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016124422A1 (de) 2016-12-14 2018-06-14 Hammelmann GmbH Hochdruckplungerpumpe sowie Verfahren zur Funktionsunterbrechung eines Fluidstroms
IT201900020072A1 (it) * 2019-10-30 2021-04-30 Annovi Reverberi Spa Valvola bidirezionale automatica e pompa dotata di detta valvola
EP3816445A1 (fr) * 2019-10-30 2021-05-05 Annovi Reverberi S.p.A. Soupape bidirectionnelle automatique et pompe équipée de ladite soupape
US11732700B2 (en) 2019-10-30 2023-08-22 Annovi Reverberi S.P.A. Automatic bidirectional valve and pump provided with said valve
WO2024134450A1 (fr) * 2022-12-21 2024-06-27 Mixtron S.R.L. Ensemble soupape et pompe pourvue dudit ensemble soupape
WO2024134393A1 (fr) * 2022-12-21 2024-06-27 Mixtron S.R.L. Ensemble clapet de refoulement et d'aspiration automatiques et pompe pourvue dudit ensemble clapet

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