WO1989011035A1 - Pompe a piston plongeur - Google Patents

Pompe a piston plongeur Download PDF

Info

Publication number
WO1989011035A1
WO1989011035A1 PCT/EP1989/000508 EP8900508W WO8911035A1 WO 1989011035 A1 WO1989011035 A1 WO 1989011035A1 EP 8900508 W EP8900508 W EP 8900508W WO 8911035 A1 WO8911035 A1 WO 8911035A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
cylinder
pressure
fuel
groove
Prior art date
Application number
PCT/EP1989/000508
Other languages
German (de)
English (en)
Inventor
Jacob Heidemans
Original Assignee
Hei-Tech B.V.
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 Hei-Tech B.V. filed Critical Hei-Tech B.V.
Publication of WO1989011035A1 publication Critical patent/WO1989011035A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention relates to a plunger pump device with a plunger which is guided in a cylinder and movable therein, this cylinder being in the vicinity of a closed end with a supply for a medium and a discharge for this medium, both of which extend into the cylinder, and wherein this cylinder is connected at its closed end to a pressure connection and is further provided with at least one annular channel running over the inner circumference of the cylinder.
  • the invention further relates to a plunger for use in this plunger pump device.
  • the medium is referred to below as fuel.
  • the ring channel is a fuel ring channel, which is usually connected to the supply or discharge for the fuel.
  • This known plunger pump device is driven, for. B. by a camshaft, possibly via a rocker arm and / or a tappet mechanism.
  • it is ensured that there is a narrow gap between the cylinder and the plunger, so that the fuel under high pressure cannot easily leak away. Any fuel that may leak through this gap is collected in the fuel ring channel.
  • This fuel ring channel is under a relatively low pressure of less than 10 bar.
  • a disadvantage of the known plunger pumping device is that fuel corners occur from the fuel ring channel, for example for driving the pump. This leak through the gap between the plunger and the cylinder has two main causes:
  • the fuel pressure in the fuel supply and discharge leads to a pressure difference across the gap and, as a result, a viscous flow through the gap. At a low pressure .in the
  • This fuel leakage rate is small, but increases as the pressure in the fuel supply and discharge increases. In the case of fuel systems, this pressure must be kept at a certain level in order to prevent the volatile components from evaporating. For diesel fuel z. B.
  • a plunger pump device is characterized in that the plunger is provided with at least one groove running over its outer circumference, which is connected to the annular channel during the pressure stroke. This creates a pressure during the pressure stroke, the possibly leaking medium, for. B. fuel, in the direction of the ring channel. This is clarified further below.
  • An embodiment of the plunger pump device in which the supply and discharge for the medium is provided with an annular channel for this medium running over the inner circumference of the cylinder and the cylinder also has another ring channel also running over its inner circumference for another medium, which is located between the one ring channel for the one medium and a plunger drive device, the other ring channel being connected to a supply for the other medium, ⁇ is characterized in that at least one groove during the plunger pressure stroke with either one or the other ring channel is connected.
  • the other medium or the other ring channel is referred to below as oil or as an oil ring channel.
  • an oil ring channel connected to the oil supply is often attached to the inner circumference of the cylinder, as already stated.
  • the oil ring channel filled with the so-called sealing oil z ⁇ is located between the fuel ring channel and the plunger drive.
  • a disadvantage of this known solution is that a special sealing oil system has to be attached and that even at a relatively high sealing oil pressure of 20 to 30 bar there is still a fuel leakage flow from the fuel ring channel to the oil ring channel
  • a further embodiment of the plunger pumping device according to the present invention is characterized in that the plunger is provided with an upper and a lower groove, both of which run over the outer circumference of the plunger and, during a piston pressure stroke, in each case the upper or the lower groove with the one or the other ring channel is connected.
  • Figure 1 shows a plunger guided in a cylinder according to the present invention, the cylinder being drawn in longitudinal section;
  • Figure 2 shows the principle of operation of the plunger pump device according to the present invention corresponding to I of Figure 1;
  • Figure 3 is a longitudinal section of the plunger pump device according to the present invention.
  • Figures 4 and 5 show some embodiments of a plunger pump device according to the present invention in longitudinal section.
  • Figure 1 shows a plunger 2 movable in a cylinder 1.
  • the inner circumference of cylinder 1 is provided with a fuel ring channel 3 and an oil ring channel 4.
  • the plunger 2 has an upper groove 5 and a lower groove 6.
  • At the height of the upper groove 5 there is, for example, diesel oil in the cylinder 1.
  • At the level of the lower groove 6 there is, for example, lubricating oil.
  • the two media may possibly be identical in both ring channels. ⁇ 6-
  • Figure 2a shows the situation that occurs shortly before the pressure stroke of the pump is ended.
  • the plunger 2 is under axial pressure.
  • the diameter of the plunger 2 has become larger and the gap 16 between the piston 2 and the cylinder 1 is smaller.
  • gap 16 becomes larger. This situation is shown in Figure 2b. This larger gap is filled with fuel and lubricating oil, the dividing line between the two media is shown in dashed lines. It should be noted here that it is a simplified representation and that in reality it is in a be ⁇
  • FIG. 3 shows a longitudinal section of a high-pressure plunger pump device according to the present invention in the form of a high-pressure fuel pump.
  • the pump comprises a cylinder 1, which is mounted in a pump housing 7.
  • the plunger 2 guided in the cylinder 1 can be moved back and forth by means of the drive device 8.
  • At the top of the plunger 2 there is a high-pressure chamber 9 which is connected to a high-pressure connection 11 via a check valve 10.
  • the fuel is supplied to the pump via supply line 12 and the excess fuel is removed again via the discharge line 13.
  • a fuel ring channel 3 provided in the cylinder 1 is connected to the discharge line 13. This contains fuel which has approximately the same pressure as that which prevails in the fuel discharge line 13.
  • an oil ring channel 4 is attached, through which the oil supply -8th-
  • An upper groove 5 is provided in the plunger 2. This upper groove 5 is wider than the fuel ring channel 3 and remains connected to the latter during the pressure stroke or, if the fuel ring channel 3 is not present, to a line 15.
  • a lower groove 6 is also provided in the plunger 2 . This lower groove 6 is wider than the oil ring channel 4 and remains connected to it during the pressure stroke. Between the upper groove 5 and the lower groove 6 is a cylindrical one
  • the fuel ring channel 3 can be omitted and one can be satisfied with the bore 15 (see Figure 4a).
  • fuel can also be supplied via the bore 14 according to " Figure 3.
  • the downward pumping action for the fuel is canceled according to the invention and then only a leakage flow occurs from the lower groove as a result of there prevailing pressure. It is therefore appropriate
  • FIG. 35 An embodiment is shown in Figure 4b, in which the plunger is only provided with an upper groove 5.
  • the leak rate is reduced to zero due to the pumping action in the gap.
  • a leakage flow only occurs as a result of a pressure possibly present in the groove 5.
  • This leakage flow can be reduced in that the channel 15 is not connected to the fuel supply or discharge of the pump, but rather to a leakage discharge which is approximately depressurized.
  • FIG. 4c Another embodiment is shown in Figure 4c.
  • the presence of the lower groove 6 reduces the leakage flow from the lower groove 6 to the drive side to zero.
  • the leakage rate of fuel downwards will be small.
  • the effect of the seal is based on the reduction of the game ate between the plunger and the cylinder during the pressure stroke of the pump. It has already been stated that this is caused by the transverse contraction of the material under the influence of the pressure stroke.
  • Figure 5a The plunger 2 is made hollow and this cavity 19 is connected to the pressure chamber of the pump;
  • Figure 5b A second cylinder 16 is fitted around cylinder 1, in which the plunger is guided. The space 20 between these two cylinders 1 and 16 is connected via a line 17 to the pressure chamber of the pump;
  • FIG. 5c A cylinder 18 is attached around the plunger 2 and the annular space 28 between the core of the plunger 2 and the cylinder 18 is connected via a line 27 to the pressure chamber of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Une pompe à piston plongeur comporte un plongeur (2) guidé dans un cylindre (1). Le cylindre est pourvu, au voisinage de son extrémité fermée, d'une canalisation d'amenée (12) et d'une canalisation d'évacuation (13) du milieu pompé, et est relié, au niveau de cette extrémité fermée, avec un raccord de pression (11). Le plongeur (2) possède au moins une rainure périphérique (5) qui, durant la course de compression dudit plongeur, communique avec un canal annulaire (3) s'étendant sur la circonférence intérieure du cylindre.
PCT/EP1989/000508 1988-05-09 1989-05-09 Pompe a piston plongeur WO1989011035A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL8801198A NL8801198A (nl) 1988-05-09 1988-05-09 Plunjerpompinrichting.
NL8801198 1988-05-09

Publications (1)

Publication Number Publication Date
WO1989011035A1 true WO1989011035A1 (fr) 1989-11-16

Family

ID=19852270

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1989/000508 WO1989011035A1 (fr) 1988-05-09 1989-05-09 Pompe a piston plongeur

Country Status (2)

Country Link
NL (1) NL8801198A (fr)
WO (1) WO1989011035A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0757173A2 (fr) * 1995-07-31 1997-02-05 WOODWARD GOVERNOR GERMANY GmbH Système d'injection de combustible
EP1234975A3 (fr) * 2001-02-26 2004-08-11 Wärtsilä Schweiz AG Unité cylindre-piston haute pression
WO2008115796A1 (fr) 2007-03-16 2008-09-25 Cummins Inc. Ensemble piston à faible fuite destiné à un système de fluide à haute pression
CN102536565A (zh) * 2011-12-30 2012-07-04 成都威特电喷有限责任公司 消除电控高压油泵柱塞偶件液压夹紧力的柱塞偶件
CN110219851A (zh) * 2019-04-02 2019-09-10 台州贝力特机械有限公司 一种液压破碎锤的活塞导向结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH231553A (de) * 1941-11-17 1944-03-31 Deckel Fa Friedrich Treibstoffeinspritzpumpe für Brennkraftmaschinen.
GB724986A (en) * 1953-04-02 1955-02-23 Crossley Premier Engines Ltd Improvements relating to fuel oil injection pumps of internal combustion engines
FR2389007A1 (fr) * 1977-04-30 1978-11-24 Lucas Industries Ltd Pompe d'injection de combustible
DE2920702A1 (de) * 1979-05-22 1980-11-27 Bosch Gmbh Robert Verteilerpumpe fuer brennkraftmaschinen
GB2123492A (en) * 1982-07-08 1984-02-01 Lucas Ind Plc Fuel injection pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH231553A (de) * 1941-11-17 1944-03-31 Deckel Fa Friedrich Treibstoffeinspritzpumpe für Brennkraftmaschinen.
GB724986A (en) * 1953-04-02 1955-02-23 Crossley Premier Engines Ltd Improvements relating to fuel oil injection pumps of internal combustion engines
FR2389007A1 (fr) * 1977-04-30 1978-11-24 Lucas Industries Ltd Pompe d'injection de combustible
DE2920702A1 (de) * 1979-05-22 1980-11-27 Bosch Gmbh Robert Verteilerpumpe fuer brennkraftmaschinen
GB2123492A (en) * 1982-07-08 1984-02-01 Lucas Ind Plc Fuel injection pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0757173A2 (fr) * 1995-07-31 1997-02-05 WOODWARD GOVERNOR GERMANY GmbH Système d'injection de combustible
EP0757173A3 (fr) * 1995-07-31 1997-12-03 WOODWARD GOVERNOR GERMANY GmbH Système d'injection de combustible
EP1234975A3 (fr) * 2001-02-26 2004-08-11 Wärtsilä Schweiz AG Unité cylindre-piston haute pression
KR100773437B1 (ko) * 2001-02-26 2007-11-05 베르트질레 슈바이츠 악티엔게젤샤프트 실린더 유닛 내의 고압 피스톤
WO2008115796A1 (fr) 2007-03-16 2008-09-25 Cummins Inc. Ensemble piston à faible fuite destiné à un système de fluide à haute pression
EP2129869A1 (fr) * 2007-03-16 2009-12-09 Cummins Inc. Ensemble piston à faible fuite destiné à un système de fluide à haute pression
EP2129869A4 (fr) * 2007-03-16 2011-10-12 Cummins Inc Ensemble piston à faible fuite destiné à un système de fluide à haute pression
US8757047B2 (en) 2007-03-16 2014-06-24 Cummins Inc. Low leakage plunger assembly for a high pressure fluid system
CN102536565A (zh) * 2011-12-30 2012-07-04 成都威特电喷有限责任公司 消除电控高压油泵柱塞偶件液压夹紧力的柱塞偶件
CN110219851A (zh) * 2019-04-02 2019-09-10 台州贝力特机械有限公司 一种液压破碎锤的活塞导向结构
CN110219851B (zh) * 2019-04-02 2024-04-26 台州贝力特机械有限公司 一种液压破碎锤的活塞导向结构

Also Published As

Publication number Publication date
NL8801198A (nl) 1989-12-01

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