EP0308468B1 - Pompe hydraulique monopiston a commande manuelle - Google Patents

Pompe hydraulique monopiston a commande manuelle Download PDF

Info

Publication number
EP0308468B1
EP0308468B1 EP88903168A EP88903168A EP0308468B1 EP 0308468 B1 EP0308468 B1 EP 0308468B1 EP 88903168 A EP88903168 A EP 88903168A EP 88903168 A EP88903168 A EP 88903168A EP 0308468 B1 EP0308468 B1 EP 0308468B1
Authority
EP
European Patent Office
Prior art keywords
piston
bore
channel
chamber
restrictor
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
EP88903168A
Other languages
German (de)
English (en)
Other versions
EP0308468A1 (fr
Inventor
Stefan Rothhaar
Otfried Stuck
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.)
Flutec Fluidtechnische Geraete GmbH
Original Assignee
Flutec Fluidtechnische Geraete 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 Flutec Fluidtechnische Geraete GmbH filed Critical Flutec Fluidtechnische Geraete GmbH
Publication of EP0308468A1 publication Critical patent/EP0308468A1/fr
Application granted granted Critical
Publication of EP0308468B1 publication Critical patent/EP0308468B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/129—Poppet valves

Definitions

  • the invention relates to a hydraulic single-piston pump, which has the features of the preamble of claim 1.
  • the invention has for its object to improve a single-piston pump of the type mentioned. This object is achieved by a pump with the features of claim 1.
  • the throttle bore of the second channel not only reduces costs. It also leads to less susceptibility to faults even under harsh operating conditions and allows a smaller overall height. Above all, the throttle bore means that the force to be applied during the working stroke depends on the actuation speed, that is to say the pump speed.
  • the actuation speed that is to say the pump speed.
  • the user can, in the pump according to the invention, independently of the pressure in the piston chamber, the actuating force to be exerted on the piston within the range defined by the full piston cross section and the reduced piston cross section Adapt borders to your possibilities.
  • any load regardless of its size, can be raised with fewer pumping cycles than with a lower pumping speed by means of a higher pumping speed, which, however, also requires more effort.
  • Another advantage of the solution according to the invention is that during the working stroke in the rod space no negative pressure can arise which, if the rod seal is not fully functional, results in air being sucked in.
  • the second channel In the case of a relatively short length of the second channel, this can be designed as a throttle bore over its entire length. As a rule, however, the second channel will be longer than the required length of the throttle section. You can then run the second channel with the exception of the portion forming the throttle bore with a larger diameter.
  • two throttle bores which follow one another at a distance can also be provided in the course of the second channel. These two throttle bores are then connected to one another by a channel section with a larger diameter.
  • This embodiment has advantages in terms of production technology and flow technology. For example, for reasons of production costs, it is advantageous if one of the two throttle bores is arranged coaxially with the section of the second channel which is larger in diameter.
  • the second throttle bore can also be coaxial, but can also run at an angle to this channel section.
  • the channel section with a larger diameter penetrates from the end face of the piston facing the piston chamber.
  • One throttle bore can connect coaxially to the end in the piston.
  • the other throttle bore can either be provided in a closure body which closes the beginning of this channel section penetrating from the piston end face. But you can also let the second throttle bore open into the channel between the closure body and the other throttle section, for example from the outer surface of the piston.
  • the single figure shows an incompletely shown longitudinal section of the embodiment.
  • a hand-operated hydraulic piston pump designated as a whole by 1, has a cylinder 2, in which a piston, designated as a whole by 3, is arranged so as to be longitudinally displaceable.
  • the piston 3 is provided at one end with a piston rod 4 which is guided so as to be longitudinally displaceable in a guide 2 'which adjoins the end of the cylinder 2 which delimits the rod chamber 5.
  • the sealing of the piston rod 4 in the guide 2 ' is indicated by an O-ring 6.
  • the piston chamber 7, which is separated from the rod chamber 5 by the piston 3, is connected to a tank 10 via a connecting line 8 and a first check valve 9, and to a working cylinder 12 via a second check valve 11, which is, for example, the working cylinder of a lifting truck.
  • the piston seal on the inside wall of the cylinder is an O-ring 13 formed, which lies in an annular groove of the piston 3.
  • the piston has a central extension 3 ′ on the side delimiting the piston chamber 7, the outer diameter of which is smaller than the section adapted to the inner diameter of the cylinder 3, but larger than the diameter of the piston rod 4.
  • This valve body 15 is arranged at one end of a guide sleeve 16 which is longitudinally displaceable on a guide pin 17 which projects from a perforated plate 18 which is screwed into the initial section of the blind hole 14.
  • a helical compression spring 19 surrounding the guide sleeve 16 and the guide pin 17 is supported on the perforated plate 18 and loads the valve body 15 with the required force.
  • a transverse bore 20 opens into the end section of the blind bore 14 located in the piston rod 4 and penetrates from an annular groove 21 provided at the transition from the piston rod 4 to the piston 3 into the piston rod 4 at right angles to its longitudinal axis.
  • the preload of the helical compression spring 19 is selected such that the check valve opens and the hydraulic fluid flows into the piston chamber 7 even at a relatively low overpressure in the rod chamber 5 during the piston return stroke.
  • a bore which penetrates from the end face of the piston 3 which delimits the piston chamber 7 22 is provided, which ends at a distance from the ring throat 21.
  • the diameter of the bore 22 is, as the figure shows, much larger than that of the first throttle bore 23. Its axial length is also a multiple of the axial length of the first throttle bore 23.
  • the beginning of the bore 22 is sealed by a closure body 24, at which in the exemplary embodiment is a ball pressed into the initial section of the bore 22.
  • a second throttle bore 25 opens into the bore 22 at right angles to its longitudinal extension, which second bore opens into the lateral surface of the extension 3 '.
  • the cross section of the two throttle bores 23 and 25 and their length are chosen so that during a working stroke of the piston 3 at a relatively high speed, the throttling effect is so strong that only a little hydraulic fluid can pass from the piston chamber 7 into the rod chamber 5, that on the other hand at relatively low speed of movement of the piston 3, there is largely pressure equalization between the piston chamber 7 and the rod chamber 5.
  • the diameter of the bore 22 is substantially larger than that of the throttle bore 23 and 25, so that the section lying between the two throttle bores is not involved in the throttle effect.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Dans la pompe décrite, le piston (3) possède un premier canal (14, 20) qui s'étend de l'intérieur du piston (7) à l'intérieur de la tige (5) et qui possède un clapet de non-retour (15-19) s'ouvrant pendant la course de retour. Le piston (3) est également pourvu d'au moins un deuxième canal (22, 23, 25) s'étendant de l'intérieur du piston (7) à l'intérieur de la tige (5), et qui est configuré, au moins sur une partie de sa longueur, comme orifice d'étranglement (23, 25).

Claims (7)

1. Pompe hydraulique monopiston à actionnement manuel dont le piston comprend un canal, s'étendant de la chambre de piston à la chambre de tige, qui renferme un clapet de non-retour s'ouvrant à la course de retour du piston et, au moins, un second canal, s'étendant de la chambre de piston à la chambre de tige dans lequel la circulation du liquide hydraulique de la chambre de tige à la chambre de piston s'effectue automatiquement en fonction de la différence de pressions entre les deux chambres, caractérisé en ce que le second canal (22, 23, 25) forme, au moins sur une partie de sa longueur, un canal d'étranglement (23, 25).
2. Pompe hydraulique selon la revendication 1, caractérisée en ce que le second canal (22, 23, 25) présente deux perçages d'étranglement successifs (23, 25).
3. Pompe hydraulique selon la revendication 3, caratérisée en ce que les deux perçages d'étranglement sont reliés ensemble par un canal ayant un plus grand diamètre.
4. Pompe hydraulique selon la revendication 3, caractérisée en ce que le canal de plus grand diamètre est disposé coaxialement à l'un, au moins, (23) des deux perçages d'étranglement (23, 25).
5. Pompe hydraulique selon la revendication 4, caractérisée en ce que le premier perçage d'étranglement (23) est disposé suivant un certain angle, de préférence, à angle droit, par rapport au second perçage d'étranglement (23).
6. Pompe hydraulique selon la revendication 4 ou 3, caractérisé en ce que la section de canal ayant un plus grand diamètre est formée par un perçage (22) qui' s'avance, à partir de la surface frontale du piston (3) orientée vers la chambre de piston (7) et en ce que son extrémité est à l'extrémité située à l'intérieur du piston duquel se raccorde, de préférence, coaxialement, l'un des perçages d'étranglement (23) dans l'entrée duquel est inséré un élément d'obturation (24).
7. Pompe hydraulique selon la revendication 6, caractérisée en ce que l'élément d'obturation (24) ferme le perçage (22) hermétiquement et en ce que, dans le perçage (22) débouche, entre l'obturateur (24) et l'extrémité située à l'intérieur du piston, le second perçage d'étranglement (25).
EP88903168A 1987-04-01 1988-03-31 Pompe hydraulique monopiston a commande manuelle Expired - Lifetime EP0308468B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3710919A DE3710919C1 (de) 1987-04-01 1987-04-01 Hydraulische Einkolbenpumpe fuer eine Handbetaetigung
DE3710919 1987-04-01

Publications (2)

Publication Number Publication Date
EP0308468A1 EP0308468A1 (fr) 1989-03-29
EP0308468B1 true EP0308468B1 (fr) 1990-08-22

Family

ID=6324601

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88903168A Expired - Lifetime EP0308468B1 (fr) 1987-04-01 1988-03-31 Pompe hydraulique monopiston a commande manuelle

Country Status (5)

Country Link
US (1) US4923373A (fr)
EP (1) EP0308468B1 (fr)
JP (1) JPH01502840A (fr)
DE (1) DE3710919C1 (fr)
WO (1) WO1988007495A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW232759B (fr) * 1992-03-16 1994-10-21 Wagner Spray Tech Corp
US5318139A (en) * 1993-04-29 1994-06-07 Evans Robert W Reduced waiting time hydraulic drilling jar
US5624001A (en) 1995-06-07 1997-04-29 Dailey Petroleum Services Corp Mechanical-hydraulic double-acting drilling jar
DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung
US6290004B1 (en) 1999-09-02 2001-09-18 Robert W. Evans Hydraulic jar
US6481495B1 (en) 2000-09-25 2002-11-19 Robert W. Evans Downhole tool with electrical conductor
DE102004028999A1 (de) * 2004-06-16 2006-01-05 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
US9630469B2 (en) * 2010-10-18 2017-04-25 Firestone Industrial Products Company, Llc Gas spring and gas damper assembly and method
DE102018213997A1 (de) * 2018-08-20 2020-02-20 Robert Bosch Gmbh Pumpenanordnung

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3112705A (en) * 1961-10-05 1963-12-03 Jane Wallen Two-speed hydraulic pumps
DE2131802C3 (de) * 1971-06-26 1974-05-16 Josef Bautz Gmbh, 7968 Saulgau Einrichtung zum Ablassen der Hubflüssigkeit aus dem Druckraum einer Schubkolbenpumpe
DE2551336B2 (de) * 1975-11-15 1979-08-30 Jungheinrich Unternehmensverwaltung Kg, 2000 Hamburg Hydraulische Hubeinrichtung mit einer Lasthub-Zylinder-Kolbeneinheit
US4357798A (en) * 1980-03-13 1982-11-09 Michael Hung Rapid actuating device of hydraulic actuator
US4520908A (en) * 1983-11-10 1985-06-04 General Motors Corporation Pressure balanced valve for adjustable hydraulic damper
FR2560938A1 (fr) * 1984-03-12 1985-09-13 Antkowiak Stephane Verin hydraulique actionne par une pompe a main incorporee ou non au verin

Also Published As

Publication number Publication date
WO1988007495A1 (fr) 1988-10-06
EP0308468A1 (fr) 1989-03-29
JPH01502840A (ja) 1989-09-28
US4923373A (en) 1990-05-08
DE3710919C1 (de) 1988-06-30

Similar Documents

Publication Publication Date Title
EP0565982A1 (fr) Agencement de soupape
DE2109378C3 (de) Rückschlagventil mit zusätzlicher Betätigung
EP0308468B1 (fr) Pompe hydraulique monopiston a commande manuelle
DE2945911C2 (fr)
DE19716042C1 (de) Hydraulische Steuervorrichtung für wenigstens ein Hubventil
EP0863342B1 (fr) Soupape de commande de pression
DE4234626C2 (de) Druckgesteuertes Ventil
DE970609C (de) Ventilanordnung fuer hydraulische Anlagen
DE2322354A1 (de) Arbeitszylinder, insbesondere hydraulikzylinder, mit einer daempfungseinrichtung fuer das ende des arbeitshubes des kolbens
EP0051728A1 (fr) Dispositif de commande pour un vérin hydraulique
DE2716694C2 (fr)
DE2929232C2 (fr)
DE874277C (de) Hydraulische Hubvorrichtung fuer Stapelgeraete
DE3135098A1 (de) Ventilaufbau, umfassend ein pumpensteuer- bzw. -regelventil und eine entlastungsanordnung
DE3737579A1 (de) Anhaengerbremsventil
DE3006530A1 (de) Hydraulisches blockier- oder halteventil
DE2932523C2 (de) Hydraulisch entsperrbares Sitzventil
DE636841C (de) Fluessigkeitsbremse, insbesondere fuer Hubwagen
EP0921321A1 (fr) Soupape d'arrêt du type soupape à siège
DE3048746A1 (de) Hydraulikanlage
DE1051591B (de) Ventil fuer hydraulische Anlagen
DE19822872A1 (de) Dosierpumpe für flüssigen Brennstoff, insbesondere einer brennkraftbetriebenen Heizeinrichtung eines Kraftfahrzeuges
DE4001197C2 (de) Sitzventil
DE2214245A1 (de) Zwillingsrueckschlagventil
DE4234742A1 (de) Ventileinheit

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19881125

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH FR LI SE

17Q First examination report despatched

Effective date: 19900124

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH FR LI SE

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
EAL Se: european patent in force in sweden

Ref document number: 88903168.8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19950216

Year of fee payment: 8

Ref country code: CH

Payment date: 19950216

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19950228

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19960331

Ref country code: CH

Effective date: 19960331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19960401

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19961129

EUG Se: european patent has lapsed

Ref document number: 88903168.8

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST