EP0301303A1 - Pompe à pistons pour la compression de fluides ou de gaz - Google Patents

Pompe à pistons pour la compression de fluides ou de gaz Download PDF

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Publication number
EP0301303A1
EP0301303A1 EP88111092A EP88111092A EP0301303A1 EP 0301303 A1 EP0301303 A1 EP 0301303A1 EP 88111092 A EP88111092 A EP 88111092A EP 88111092 A EP88111092 A EP 88111092A EP 0301303 A1 EP0301303 A1 EP 0301303A1
Authority
EP
European Patent Office
Prior art keywords
pressure
seals
piston
working
piston pump
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Withdrawn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
EP88111092A
Other languages
German (de)
English (en)
Inventor
Klaus Prof. Dr.-Ing. Spies
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.)
Kamat-Pumpen GmbH and Co KG
Kamat Pumpen GmbH and Co KG
Original Assignee
Kamat-Pumpen GmbH and Co KG
Kamat Pumpen GmbH and Co KG
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 Kamat-Pumpen GmbH and Co KG, Kamat Pumpen GmbH and Co KG filed Critical Kamat-Pumpen GmbH and Co KG
Publication of EP0301303A1 publication Critical patent/EP0301303A1/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Withdrawn legal-status Critical Current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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • the invention relates to a piston pump with a working piston for compressing liquids and gases, preferably to extremely high pressures, as a component of piston pumps, primarily in-line piston or differential piston pumps, with devices for filling and emptying the working space.
  • the invention has for its object to eliminate the various, above-described and with the known technical possibilities, problems and difficulties in the seals of pumps and pressure intensifiers for extremely high pressures according to the invention in that the pressure is connected stepwise or stepwise over several in series Seal kits dismantled and, in the case of pressure media with no lubricating effect, the necessary lubricating effect on the seals is achieved by a corresponding oil supply.
  • the highest operating pressures can be subdivided into pressure levels that can be managed with economically justifiable means, and the elements that have been tried and tested for sealing medium pressures can be used constructively.
  • Elasto meren as sealing materials, the pressures in the individual sealing stages connected in series can be reduced to orders of magnitude at which the above-described problems of premature sealing wear do not occur.
  • a basic concept is chosen for this, in which several sets of seals are arranged one behind the other between the piston and the cylinder wall and oil is applied to the gaps between the individual seals, the pressure between the seals gradually decreasing from seal level to seal level, so that each seal only has the respective differential pressure has to be bridged.
  • the gradual reduction in pressure between the individual sealing stages is achieved according to the invention in that the spaces between the sealing sets are components of simple oil circuits which are coupled to one another via small pressure intensifiers.
  • Figure 1 shows the basic structure of a single or multi-piston pump with the simplest variant of the seal according to the invention with gradual pressure reduction.
  • the crank mechanism 1 is connected via cross heads 2 to the piston rod (s) 3, which are located in the cylinders 4 oscillate back and forth.
  • the suction of the pressure medium takes place via the lines 5 and the check valves 6, while the discharge of the high-pressure pressure medium takes place via the check valves 7 and the discharge lines 8.
  • the pressure chamber 16 of the pressure booster 15 is connected via the line 17 to the annular space 11 arranged between the seals.
  • the area ratio in the pressure booster 15 ie the ratio of the effective areas of the pressure spaces 14, 16 in the ratio 1: 2 .
  • FIG 2 shows the relatively simple structure of the oil hydraulic auxiliary circuit.
  • the relatively small pressure intensifier 15 has only relatively small oil reserves in the annular space 14 connected via line 17 to the annular space 11 between the seals 9, 10.
  • the annular space 11 between the seals 9, 10 and the pressure space 16 under the piston surface of the pressure booster 15 are connected to a hydraulic accumulator 22.
  • another oil-hydraulic auxiliary circuit can also be selected, in which there is a higher pressure than the working pressure in the cylinder space to produce a lubricating effect, as shown in Fig. 3 can be seen.
  • the line 13 connected to the working space (s) 12 of the pump becomes in contrast to the embodiment according to Fig. 2 connected to the pressure chamber 16 under the piston surface of the pressure intensifier 15, while the annular space 14 of this pressure intensifier is connected via line 17 to the annular space 11 between the seals 9, 10.
  • the pressure accumulator 22 has the effect that the leakage losses of the oil-hydraulic auxiliary circuit, which are only slight in this case, can be absorbed over long periods of time. Should the piston 23 of the pressure intensifier 15 nevertheless approach its end position after a long operating time, so that only very little oil volume is present in the pressure chamber 14, then in this case the switch 25 is actuated and the associated circuit 26 is closed, so that the next one follows When the pump is at a standstill, the pressure intensifier 15 is automatically refilled.
  • the embodiment variant according to FIG. 4 has three seals 9, 10, 27 arranged one behind the other and two annular spaces 11, 28 located between these seals and two oil-hydraulic auxiliary circuits assigned to these annular spaces.
  • the two auxiliary circuits serve to gradually reduce the operating pressure prevailing in the pressure chamber 12 of the pump over two intermediate stages.
  • the pressure intensifier 15 with the connecting lines 13, 17 has the effect that the pressure in the annular space 11 is greatly reduced compared to the pressure in the working space 12, and as a result the seal 9 only needs to seal the differential pressure
  • the stub line is connected to the pressure intensifier 29 by the second oil-hydraulic auxiliary circuit 30 and the connecting line 31 to the annular space 28 achieved that the seal 10 only needs to seal the differential pressure between the annular spaces 11, 28 and is therefore to a large extent relieved of force.
  • the seal 27 then only has to seal the pressure prevailing in the second oil-hydraulic auxiliary circuit.
  • the pressure in the individual will follow one another the intermediate stages from the work space 12 in the form of an arithmetic series. If, for example in the embodiment according to FIG. 4, the pressure in the working space were 6,000 bar, then a pressure of 4,000 bar would have to exist in the annular space 11 and a pressure of 2,000 bar in the annular space 28. Only in this case are the differential pressures and the forces acting on the seals 9, 10, 27, ... the same. Since in the pressure intensifiers 15, 29, ... the pressure is reduced according to geometric relationships, an arithmetic series is brought into line with a geometric progression if any number of pressure levels is assumed.
  • the pressure intensifiers can therefore at the same differential pressure aimed at both sides of the seals, ie when the requirement is that the same on all seals Forces work, not the same size.
  • Fig. 5 shows an embodiment for the seal set of a piston pump, in which, due to the lack of lubrication of the working medium in the first oil-hydraulic auxiliary circuit, there is initially a higher pressure than the pressure of the working medium in the cylinder chamber 12 in order to adequately lubricate the seal 9. A gradual pressure reduction then takes place via the further oil-hydraulic auxiliary circuits in the annular spaces 28, 35, the last seal 36 sealing the residual pressure in the annular space 35 against the atmospheric pressure.
  • the pressure intensifier 15 consequently causes an increase in pressure for the oil-hydraulic auxiliary circuit connected downstream, while the pressure intensifiers 29, 37 lead to pressure reductions in the respectively downstream oil-hydraulic circuits, in this exemplary embodiment the reference pressure for the gradual pressure reduction being the pressure in the annular space 11 and the seals of the seal 10 to be counted when, in order to keep the forces acting on the individual seals constant, the aforementioned proportionality factor should be maintained.
  • the pressure accumulators 22, 32, 38 serve - as in the exemplary embodiments according to FIGS. 2-4 - to provide oil reserves in the event of any leakage losses in the oil-hydraulic auxiliary circuits in order to be able to maintain the operation of the pump and the gradual pressure reduction for as long as possible. Filling devices (not shown) ensure - as in the aforementioned examples - that the pressure intensifier is automatically refilled when the pump is at a standstill.
  • Differential piston pumps are also often used to generate extremely high pressures and are also referred to as "pressure intensifiers" according to their physical and technical mode of operation.
  • Differential piston pumps of this type can be constructed according to FIG. 6 “working on one side” or according to FIG. 7 also “working on two sides”.
  • the drive piston ie the piston of larger diameter
  • a technically just manageable pressure ie between 200 and 400 bar, depending on the application, which is then “translated” to the extremely high pressure of the working medium.
  • the sealing principle according to the invention can be implemented with seals and oil connected in series equally use hydraulic auxiliary circuits for the gradual pressure reduction. In the embodiment shown in Fig.
  • the pressure intensifier 15 is switched so that the pressure in the Annulus 11 is already reduced according to the gradual degradation compared to the pressure in the working space 12.
  • the structure of the two oil-hydraulic auxiliary circuits fully corresponds to the analog example for the in-line piston pump according to Fig. 4.
  • the piston 39 which is used to drive, and which moves — firmly connected to the working piston 3 — back and forth in the housing 40 is acted upon alternately with hydraulic fluid via the pressure inlets and outlets 41, 42, the respective reversing being effected via control devices (not shown) in the end positions.
  • Fig. 7 shows a differential piston pump in a double-acting mode of operation, in which the drive piston 39 is acted upon alternately by hydraulic fluid of medium pressure via the pressure feeds 41, 42 and is moved back and forth in the cylinder 40. The reversal takes place via likewise not shown Control devices.
  • the design of the oil-hydraulic auxiliary circuits for the seals 9, 10, 27, 36 of the two working pistons 3 corresponds to the exemplary embodiment according to FIG. 5.
  • the pressure for the annular spaces 11 is initially slight compared to the pressure of the working medium in the working space 12 increased to achieve a sufficient lubricating effect for the seals 9.
  • the pressure prevailing in the annular spaces 11 is then gradually reduced via the two downstream oil-hydraulic auxiliary circuits with the pressure intensifiers 29, 37, which are connected to the annular spaces 28, 35.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP88111092A 1987-07-30 1988-07-12 Pompe à pistons pour la compression de fluides ou de gaz Withdrawn EP0301303A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3725221 1987-07-30
DE19873725221 DE3725221A1 (de) 1987-07-30 1987-07-30 Kolbenpumpe mit arbeitskolben zur verdichtung von fluessigkeiten und gasen

Publications (1)

Publication Number Publication Date
EP0301303A1 true EP0301303A1 (fr) 1989-02-01

Family

ID=6332683

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88111092A Withdrawn EP0301303A1 (fr) 1987-07-30 1988-07-12 Pompe à pistons pour la compression de fluides ou de gaz

Country Status (3)

Country Link
EP (1) EP0301303A1 (fr)
JP (1) JPH01110878A (fr)
DE (1) DE3725221A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO168134C (no) * 1989-05-16 1992-01-15 Alcatel Stk As Gassdrevet stempelpumpe for olje
JPH0673382U (ja) * 1991-11-20 1994-10-18 直義 大石 高圧水噴射装置
DE102004013142A1 (de) * 2004-03-17 2005-10-06 Sonplas Gmbh Pumpvorrichtung für ein Fluid
DE102017219964A1 (de) * 2017-11-09 2019-05-09 Continental Teves Ag & Co. Ohg Elektrohydraulischer Aktuator und Verfahren zum Betreiben eines Elektrohydraulischen Aktuators

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2827860A (en) * 1956-01-03 1958-03-25 Jack S Roberts Piston lubricator
US3179057A (en) * 1962-08-31 1965-04-20 Union Carbide Corp Equipment system for producing ultrahigh process pressures
DE2710428A1 (de) * 1977-03-10 1978-09-14 Hammelmann Paul Plungerpumpe
GB2113773A (en) * 1982-01-22 1983-08-10 Yoshiichi Yamatani Apparatus for providing high pressure fluid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2827860A (en) * 1956-01-03 1958-03-25 Jack S Roberts Piston lubricator
US3179057A (en) * 1962-08-31 1965-04-20 Union Carbide Corp Equipment system for producing ultrahigh process pressures
DE2710428A1 (de) * 1977-03-10 1978-09-14 Hammelmann Paul Plungerpumpe
GB2113773A (en) * 1982-01-22 1983-08-10 Yoshiichi Yamatani Apparatus for providing high pressure fluid

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 7, Nr. 275 (M-261)[1420], 8. Dezember 1983; & JP-A-58 152 182 (SUREAKI KANEKO) 09-09-1983 *

Also Published As

Publication number Publication date
DE3725221A1 (de) 1989-02-09
JPH01110878A (ja) 1989-04-27

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