WO2005059362A1 - Compresseur a piston pour comprimer des substances gazeuses dans au moins deux chambres de travail - Google Patents

Compresseur a piston pour comprimer des substances gazeuses dans au moins deux chambres de travail Download PDF

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Publication number
WO2005059362A1
WO2005059362A1 PCT/EP2004/014024 EP2004014024W WO2005059362A1 WO 2005059362 A1 WO2005059362 A1 WO 2005059362A1 EP 2004014024 W EP2004014024 W EP 2004014024W WO 2005059362 A1 WO2005059362 A1 WO 2005059362A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valves
piston part
plates
cylinder
Prior art date
Application number
PCT/EP2004/014024
Other languages
German (de)
English (en)
Inventor
Beat Frefel
Original Assignee
Fritz Haug 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 Fritz Haug Ag filed Critical Fritz Haug Ag
Priority to DE502004005581T priority Critical patent/DE502004005581D1/de
Priority to US10/581,614 priority patent/US20070116588A1/en
Priority to EP04803681A priority patent/EP1702162B1/fr
Publication of WO2005059362A1 publication Critical patent/WO2005059362A1/fr

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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/02—Multi-stage pumps of stepped piston type

Definitions

  • Piston compressor for compressing gaseous media in at least two work rooms
  • the invention relates to a piston compressor for compressing gaseous media in at least two work spaces with the features of the independent claim.
  • a piston compressor for compressing gaseous media has a stepped piston with a first piston part and at least a second coaxially arranged piston part.
  • the piston compressor has a first cylinder with an inner bore for receiving the first piston part to form a first workspace.
  • the second cylinder also has an inner bore for receiving the second piston part to form a second working space.
  • the second piston part has a smaller diameter than the first piston part.
  • Each of the at least two cylinders is closed by a plate with valve arrangements, the second piston part with the smaller diameter being guided through an opening in one of the plates with valve arrangements.
  • the stepped piston can move back and forth in the compressor, whereby gaseous medium is sucked in and then compressed. With the help of the stepped piston, compression in at least two separate work rooms is possible.
  • One work area is ring-shaped (annular gap), while the other work area is cylindrical.
  • the stroke movements of the stepped piston can take place, for example, via a connecting rod system with a drive via a crank mechanism.
  • the stepped piston is connected to the drive via a piston rod or a guide piston.
  • the stepped piston could therefore be built on a crosshead of a compressor engine.
  • the plates with valve arrangements close the cylinders and serve to control the inlet and outlet of the gaseous medium to be compressed.
  • Such a valve arrangement has several advantages. So the plates with the valve arrangements can be easily assembled and disassembled. A modular design is also made possible because the necessary valves can be attached to the plates in a simple manner. The advantages of this design are the good utilization of the cylinder cross-section and the smoothly moving valve plates. The damage space, wear and flow losses are therefore small with this valve arrangement and it is therefore particularly suitable for smaller and high-speed compressors.
  • the first piston part is arranged at one end of the second piston part. The piston part with the larger diameter thus forms the front end of the step piston.
  • the first piston part forms a cylindrical working space and the second smaller piston part forms an annular working space.
  • the piston parts and the two cylinders are thus arranged in such a way that compression takes place in push-pull.
  • the gaseous medium is compressed in one direction of movement in each work area and sucked in the other work area (and vice versa).
  • the second piston part is arranged at the end of the first piston part.
  • the second piston part the diameter of which is smaller than the diameter of the first piston part, thus forms the front end of the stepped piston.
  • the second smaller piston part forms a cylindrical working space and the first larger piston part forms an annular working space.
  • the piston parts and the two cylinders are arranged such that compression takes place in the “same cycle ⁇ - . In this arrangement, one direction of movement has the same effect for both workspaces.
  • a compression takes place simultaneously in the two work rooms. However, the compression takes place in two stages. In a first stage, compression takes place via the annular gap (formed by the second working space).
  • the compression in the second Step takes place over the piston surface of the second piston part, which forms the front end of the step piston.
  • the piston parts are each preferably sealed against the inner bore of the cylinder parts by means of piston rings.
  • the advantage of this embodiment is that the losses via the piston rings emerge from the second stage into the first stage and do not reach the outside. As a result, gas losses can be minimized considerably. The loads on the piston rings are also reduced.
  • the diameter of the second smaller piston part is preferably selected in comparison to the diameter of the first larger piston part such that the annular gap volume of the first stage has a volume three to four times greater than the working space at the front end of the step piston.
  • the plates are disc-shaped and delimit the work areas on the end face, as a result of which the work rooms are closed in a simple manner. This also enables a simple and compact design of compressors.
  • the plates with valve arrangements have at least one inlet valve and at least one outlet valve. This ensures that air or other gaseous media is drawn in via an inlet valve in one direction of movement and that the compressed air is expelled through the outlet valves during the opposite movement.
  • the plates advantageously have bores for the valve arrangements.
  • the corresponding valves can be arranged on these holes.
  • Such holes can be wall on the plates, which are preferably made of metal such as steel or aluminum, are introduced.
  • inlet valves and outlet valves are designed as lamellar valves, as tongue valves, or individual valves with spring return.
  • a slat closes (respectively opens) the passage through a hole for the passage of the media.
  • a tongue closes (or opens) the passage through several holes for the passage of the media at the same time.
  • a single valve closes (or opens) the passage through one or more holes for the passage of the media.
  • Such valves are particularly suitable for use in a compression unit with a small stroke volume. These valve types are characterized by the fact that they are easy and inexpensive to manufacture or obtain. They can also be easily arranged in the plate.
  • the plates are sealed off from the cylinder parts by seals, for example flat seals, O-ring seals or, if necessary, metallic seals.
  • FIG. 1 cross section through a first exemplary embodiment of a piston compressor according to the invention
  • FIG. 2 cross section through an alternative exemplary embodiment of a piston compressor according to the invention
  • Figure 3 ' enlarged view of a section through the upper part of a piston compressor with lamellar valves and
  • a piston compressor designated 15 with a step piston 1 is shown.
  • the stepped piston 1 consists of two piston parts: a first piston part 16 and a second piston part 17.
  • the pistons are of course basically arranged symmetrically and coaxially in an axis A.
  • the stepped piston 1 can move back and forth in the x-direction along the axis A.
  • the first piston part 16, which defines the front end of the stepped piston is arranged in a first cylinder 7.
  • the diameter of the first piston part 16 is larger than the diameter of the second piston part 17.
  • Another working space 22 is in the region of the second cylinder 8 and the second piston part 17 are arranged. Obviously, this working space 22 is configured in a ring shape.
  • the compressor 15 also has a cylinder head 29.
  • the plate 9 is located between the cylinder head 29 and the first cylinder 7.
  • the plate 9 has a circular opening 20, the diameter of which preferably corresponds to the diameter of the inner bore 19 of the second cylinder 8.
  • the opening 20 can, however, also be designed in such a way that there is a seal with the piston part 17.
  • At least one inlet valve 3 and 13 and one outlet valve 4 and 14 are arranged on the plates 2 and 9, respectively.
  • the inlet valves 3 and 13 and the outlet valves 4 and 14 are designed as lamella valves 31.
  • the piston parts 16 and 17 have piston rings 5 on their outer surfaces for sealing the respective working spaces 21 and 22, respectively. Other seals such as labyrinth seals or rod packs are also conceivable.
  • the front piston part 16 also has guide elements 6, on the one hand to increase the stability of the stepped piston 1 and on the other hand to minimize the distance between the stepped piston 1 and the cylinder (here only the cylinder part 7). As a result, the efficiency of the piston compressor 15 can be improved.
  • the compression takes place in two stages. In a first stage, the medium is compressed via the annular gap 28 in the lower working space 21. In the second stage, the medium in the front working chamber 22 is compressed via the piston surface 30 of the front piston 17. Due to the relatively small piston area 30, higher final pressures can be achieved here.
  • the arrangement is characterized, inter alia, in that the losses emerge from the second stage into the first stage via the piston rings 5 and thus do not escape into the open. In this way, gas losses can be minimized considerably.
  • the loads on the piston rings 5 are minimized since, due to the high support pressure in the lower working chamber 21, the differential pressure acting on the piston rings 5 is smaller with respect to the front working chamber 22.
  • the second piston part 16 has additional guide elements 6. Depending on the dimensioning and application, several such sealing elements and / or guide elements can be arranged.
  • a stepped piston 1 is moved by an oscillating drive, for example via a crank drive.
  • the stepped piston 1 is preferably connected to the drive via a piston rod.
  • the guide of the stepped piston 1 can be done in particular by a crosshead (also not shown).
  • FIG. 3 shows a section through an upper plate 9 with the representation of an inlet valve 3 in the form of a lamellar valve 31.
  • a hole 23 in the form of a through hole is provided in the plate 9 for an inlet valve 3, which is covered by a respective lamella .
  • the lamella valves 31 are attached off-center.
  • a total of at least one lamella is to be provided as the inlet and outlet valve.
  • the number of slats essentially depends on the size and the intended performance data.
  • the piston parts 16 and 17 must have recesses at locations where components of the valves 3 and 4 protrude into the displacement.
  • the position of the stepped piston 1 around the longitudinal axis A must be fixed.
  • the inlet valves 3 and outlet valves 4 can, according to the design with lamellar valves 31, also each be designed as a tongue valve, in which case a tongue would cover several bores 23 at the same time (not shown).
  • FIG. 4 shows an example of a valve arrangement on a plate 9, which also applies analogously to the valve arrangement of the plate
  • valves 3 and 4 are designed as individual valves with spring return 33, which are arranged centrally above the bores 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne un compresseur à piston (15) pour comprimer des substances gazeuses, contenant un piston différentiel (1) comprenant une première partie de piston (16) et une seconde partie de piston (17) qui sont disposées dans un axe. Deux cylindres (7, 8) comprenant des alésages internes de diamètres différents, forment deux chambres de travail (21, 22). Les cylindres sont refermés par des plaques (2, 9) présentant des systèmes de soupapes. Selon l'invention, la partie de piston (17) qui a le plus petit diamètre, est guidée à travers une ouverture (20) dans la plaque (2). En tant que soupapes sont utilisées en particulier des soupapes à lamelle, des soupapes à languette ou des soupapes à ressort de rappel.
PCT/EP2004/014024 2003-12-09 2004-12-09 Compresseur a piston pour comprimer des substances gazeuses dans au moins deux chambres de travail WO2005059362A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE502004005581T DE502004005581D1 (de) 2003-12-09 2004-12-09 Kolbenkompressor zum verdichten gasförmiger medien in wenigstens zwei arbeitsräumen
US10/581,614 US20070116588A1 (en) 2003-12-09 2004-12-09 Piston compressor for compressing gaseous media in at least two working chambers
EP04803681A EP1702162B1 (fr) 2003-12-09 2004-12-09 Compresseur a piston pour comprimer des substances gazeuses dans au moins deux chambres de travail

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP03028312A EP1541867A1 (fr) 2003-12-09 2003-12-09 Compresseur à pistons pour compresser des gaz dans au moins deux chambres à compression
EP03028312.1 2003-12-09

Publications (1)

Publication Number Publication Date
WO2005059362A1 true WO2005059362A1 (fr) 2005-06-30

Family

ID=34486159

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/014024 WO2005059362A1 (fr) 2003-12-09 2004-12-09 Compresseur a piston pour comprimer des substances gazeuses dans au moins deux chambres de travail

Country Status (4)

Country Link
US (1) US20070116588A1 (fr)
EP (2) EP1541867A1 (fr)
DE (1) DE502004005581D1 (fr)
WO (1) WO2005059362A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2161451A1 (fr) 2008-09-09 2010-03-10 HAUG Kompressoren AG Compresseur à piston
DE102010035164A1 (de) 2010-08-23 2012-02-23 Garri Alexandrow Rotationskolben Gasverdichter

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2161452A1 (fr) 2008-09-09 2010-03-10 HAUG Kompressoren AG Compresseur à piston et procédé de montage ou de démontage d'un compresseur à piston
CN103557136B (zh) * 2013-10-21 2016-04-13 深圳市恒永达科技有限公司 一种移液泵、移液系统及分析装置
ITCO20130059A1 (it) * 2013-11-15 2015-05-16 Nuovo Pignone Srl Assieme pistone-cilindro per compressore centrifugo
WO2016097146A1 (fr) * 2014-12-18 2016-06-23 Ge Healthcare Bio-Sciences Ab Système de pompe pour conditionnement en ligne
DE102015209728A1 (de) 2015-05-27 2016-12-01 Robert Bosch Gmbh Pumpeneinrichtung, Bremssystem
EP3682917A1 (fr) * 2019-01-15 2020-07-22 Berlin Heart GmbH Refroidissement d'un système d'entrainement pour pompes à membrane
FR3108954B1 (fr) 2020-04-03 2023-11-03 Commissariat Energie Atomique Système de compression passive à piston
US11994121B1 (en) * 2023-06-09 2024-05-28 Tonand Inc. Piston in piston variable displacement hydraulic device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH123787A (de) * 1926-12-04 1927-12-16 Anders Anderberg Doppelt wirkende Pumpe.
US4334833A (en) * 1980-10-28 1982-06-15 Antonio Gozzi Four-stage gas compressor
US4368008A (en) * 1981-02-10 1983-01-11 Tadeusz Budzich Reciprocating controls of a gas compressor using free floating hydraulically driven piston
US4369633A (en) * 1981-09-03 1983-01-25 Snyder David A Multiple stage compressor with flash gas injection assembly

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246932A (en) * 1939-09-21 1941-06-24 Chicago Pneumatic Tool Co Combination single and two stage vacuum pump
DE19850269A1 (de) * 1998-10-31 2000-05-04 Wabco Gmbh & Co Ohg Gasverdichter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH123787A (de) * 1926-12-04 1927-12-16 Anders Anderberg Doppelt wirkende Pumpe.
US4334833A (en) * 1980-10-28 1982-06-15 Antonio Gozzi Four-stage gas compressor
US4368008A (en) * 1981-02-10 1983-01-11 Tadeusz Budzich Reciprocating controls of a gas compressor using free floating hydraulically driven piston
US4369633A (en) * 1981-09-03 1983-01-25 Snyder David A Multiple stage compressor with flash gas injection assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2161451A1 (fr) 2008-09-09 2010-03-10 HAUG Kompressoren AG Compresseur à piston
DE102010035164A1 (de) 2010-08-23 2012-02-23 Garri Alexandrow Rotationskolben Gasverdichter

Also Published As

Publication number Publication date
EP1541867A1 (fr) 2005-06-15
US20070116588A1 (en) 2007-05-24
EP1702162B1 (fr) 2007-11-21
EP1702162A1 (fr) 2006-09-20
DE502004005581D1 (de) 2008-01-03

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