EP1834089B1 - Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne - Google Patents

Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne Download PDF

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Publication number
EP1834089B1
EP1834089B1 EP05797277A EP05797277A EP1834089B1 EP 1834089 B1 EP1834089 B1 EP 1834089B1 EP 05797277 A EP05797277 A EP 05797277A EP 05797277 A EP05797277 A EP 05797277A EP 1834089 B1 EP1834089 B1 EP 1834089B1
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EP
European Patent Office
Prior art keywords
piston
piston pump
pump
working space
sleeve part
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Application number
EP05797277A
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German (de)
English (en)
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EP1834089A1 (fr
Inventor
Heinz Siegel
Thomas Jakisch
Siamend Flo
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1834089A1 publication Critical patent/EP1834089A1/fr
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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons

Definitions

  • the invention relates to a piston pump, in particular a fuel pump high-pressure pump for an internal combustion engine, with a housing and with a piston which defines a working space and has a pointing away from the working space paragraph.
  • a piston pump of the type mentioned is from the DE 101 34 066 A1 known.
  • the piston can be offset by an eccentric shaft in a reciprocating motion.
  • the piston has a region with a larger diameter and a region with a smaller diameter, wherein the region of larger diameter is in the installed position adjacent to the working space.
  • the piston is guided in the known pump with the larger diameter region directly in the housing and inserted with this area ahead of the working space forth in the housing.
  • the opening through which the piston is inserted into the housing is closed by a quantity control valve after insertion of the piston.
  • Object of the present invention is to provide a piston pump of the type mentioned in such a way that it can be made faster and easier.
  • the piston can be introduced with the working space end in front of the housing, the piston can be inserted through the same opening in which it is later performed in operation in the housing. An additional opening for the assembly of the piston can thus be omitted.
  • This increases the freedom in the design of the piston pump, reduces the cost of the housing, and reduces assembly costs. After insertion of the piston into the housing and before assembly of the piston pump, for example on an internal combustion engine, falling out is still reliably prevented by the stop element.
  • the pump can therefore be supplied in preassembled state to the manufacturer of the internal combustion engine. This simplifies storage, transport and integration into the internal combustion engine.
  • the shoulder is formed by an annular step on the piston.
  • a stepped piston can be easily and inexpensively manufactured.
  • the proposed annular step on the piston still has the advantage that in this area, the piston pump can build a total of smaller, which further facilitates their installation in the engine.
  • the annular step delimits a compensation chamber which is fluidically separated from the working chamber and which is connected to a region of an inlet-side volume control valve remote from the working chamber.
  • a pressure damper is arranged between the equalization chamber and the quantity control valve in such a piston pump. Due to the presence of the compensation chamber of the pressure damper can build smaller, which contributes to a total reduction of the dimensions of the piston pump according to the invention. Due to the compensation volume provided in the compensation room In addition, pressure peaks, which can occur in the event of failure of the pressure damper, are reduced. As a result, the inlet side parts of the piston pump and also a low pressure system connected to the inlet of the piston pump can be designed for maximum pressures, which also contributes to simplification and cost reduction.
  • the hydraulically effective area of the annular step is approximately half the size of the hydraulically effective area of the piston projecting into the working space. "About half the size” includes a range of 40-60% of the hydraulic effective area of the piston projecting into the working space.
  • the stop element comprises a sleeve part which is coaxial to the piston and has a radially inner region on which the stop is formed.
  • a sleeve part can be produced inexpensively, for example, as a sheet metal part.
  • the stop element may comprise a sleeve part which is coaxial with the piston and which has an axially extending fastening section on a radially outer region, on which the sleeve part is connected to the housing, preferably pressed in and / or welded.
  • the attachment of the stop element is moved to the housing in a radially comparatively far outboard area, which is at most far away from the piston and the piston seal.
  • the risk of damage to these sensitive parts during assembly or manufacture of the piston pump according to the invention is thus reduced. This is especially true for attachment of the stop element to the housing by a weld, in the production of which welding spatter can occur and In addition, there may be a delay of lying in the vicinity of the weld components.
  • a particularly advantageous embodiment of the piston pump according to the invention is characterized in that it comprises a housing-fixed piston seal, which rests against a lateral surface of the piston and a conveying region separated from a drive region, and that the piston seal is held by a holding portion of the stop element.
  • the stop element thus has a dual function, namely it additionally holds the piston seal.
  • the circumference to be sealed is also reduced, which directly translates into reduced leakage from the fuel to a drive region and vice versa (the drive region is usually at least one with lubricant) partly filled or contaminated area).
  • the stop element may comprise a first sleeve part on which the stopper is present, and a second sleeve part which holds the piston seal. These can be produced with little effort.
  • the holding section comprises a receiving chamber, in which the piston seal is received, and which is formed between the first sleeve part and the second sleeve part.
  • a receiving chamber allows a simple and safe and beyond a protected mounting of the piston seal.
  • a simple joining method for the two sleeve parts is that they are pressed together. In contrast to a welded connection, a delay of the stop element is also avoided.
  • the two sleeve parts and the piston seal form a preassembled module.
  • This pre-assembled assembly is postponed after insertion of the piston in the guide opening of the housing on the piston as a whole, whereby assembly time is saved.
  • the piston spring can be placed and then attached to the end remote from the working space of the piston, a spring plate, for example by a press connection.
  • the piston can be pressed with its working space end against the opposite boundary wall of the working space without the risk of damage, for example, a quantity control valve.
  • a fuel system carries in FIG. 1 overall, the reference numeral 10. It comprises a fuel tank 12, from which a prefeed pump 14 conveys the fuel to a piston pump designed as a high-pressure fuel pump 16. This compresses the fuel to a very high pressure and conveys it to a fuel rail 18, to which a plurality of injectors 20 are connected. These inject the fuel directly into their associated combustion chambers 22 a.
  • the piston pump 16 is mechanically driven by the internal combustion engine, as indicated by the connection 24. To control the Flow rate of the piston pump 16 includes this inlet side a quantity control valve 26th
  • the piston pump 16 is in FIG. 2 It is shown in more detail in detail: Thereafter, it comprises a total of approximately cylindrical housing 28, which in FIG. 2 is closed at the top by a cover 30. Under the lid, as will be explained below, an in FIG. 2 invisible pressure damper arranged.
  • a stepped bore 32 is introduced into the housing 28, into which a piston bushing 34 is inserted. In the latter, in turn, a piston 36 is guided axially displaceable with very little play.
  • the piston 36 and the in FIG. 2 Upper end of the stepped bore 32 define a working space 38, in which the fuel from the side of the housing 28 arranged quantity control valve 26 passes through an inlet 40 during a suction stroke. During a compression stroke of the piston 36, the fuel is expelled from the working space 38 via an outlet 42 to the fuel rail 18.
  • the piston 36 is formed as a stepped piston with a working space 38 toward the area 44 of larger diameter and a remote from the working space 38 area 46 with a smaller diameter. Between the two regions 44 and 46 of the piston 36, an annular step 48 is provided through which a shoulder is formed, which will be discussed in more detail below. Typical diameters for the regions 44 and 46 are 9 and 6 mm, respectively. How out FIG. 2 it can be seen, the housing 28 is inserted with a connecting piece 50 in a receiving opening 52 in an engine block 54 of the internal combustion engine. That of the work space 38 remote end of the piston 36 cooperates with an eccentric portion 56 of the drive shaft 24 together.
  • FIG. 3 Assembly 58, shown in greater detail, is mounted to housing 28, which includes a stop member 60 and a piston seal 62.
  • the stop element 60 in turn consists of a first sleeve part 64 and a second sleeve part 66. Both sleeve parts 64 and 66 and the piston seal 62 are arranged coaxially with the piston 36.
  • the piston seal 62 rests in the installed position on the lateral surface of the piston 36 and separates a fuel-side delivery region 68 from a motor oil-side drive region 70 (cf. FIG. 2 ).
  • the first sleeve part 64 comprises a radially inner and tubular axially extending inner portion 72, a radially extending central portion 74, which is integrally formed on the working space 38 and the conveying area 68 towards the end of the inner portion 72, and a radially outwardly to the central portion 74 formed outer portion 76 which extends in the axial direction to the drive portion 70 through.
  • the second sleeve part 66 comprises an annular and radially inner inner portion 78, a radially outwardly formed on the inner portion 78 central portion 80 which extends in the axial direction of the working space 38 and the conveying region 68 and an integrally formed on the central portion 80 outer portion 82, which extends radially outward.
  • the outer diameter of the central portion 80 of the second sleeve portion 66 and the inner diameter of the inner portion 72 of the first sleeve portion 64 are at least partially coordinated so that the inner portion 78 and the central portion 80 of the second sleeve portion 66 are held by a press fit within the first sleeve portion 64.
  • a short, radially inwardly directed turn 84 is present at the free end of the inner portion 72 of the first sleeve portion 64 facing away from the working space 38 and from the conveying area 68.
  • This bend 84 together with a portion of the inner portion 72 of the first sleeve portion 64 and the inner portion 78 of the second sleeve portion 66, forms a retainer portion for the piston seal 62 in the form of an annular receiving chamber 86.
  • the assembly 58 is pushed onto the region 46 of the piston 36 after the assembly of the piston 36.
  • the outside of the outer portion 76 of the first sleeve part 64 is then pressed in 88 and welded to the connection piece 50 of the housing 28.
  • a piston spring 90 is mounted, the diameter of which is selected so that it is supported axially at one end to the inner portion 72 of the first sleeve portion 64 adjacent region of the central portion 74.
  • the portion of the inner portion 72 adjacent to the central portion 74 has a slightly increased diameter, by which the piston spring 90 is centered without its free mobility being restricted by the inner portion 72 as a whole.
  • the shoulder 48 Since the outer diameter of the portion 44 of the piston 36 is greater than the inner diameter of the inner portion 78 of the second sleeve member 66, the shoulder 48, as long as the piston pump 16 is not yet inserted into the receiving opening 52, in abutment against the inner portion 78 of the second sleeve member 66th This thus forms a stop for the shoulder 48 of the piston 36 and prevents the piston 36 from falling out of the fully assembled piston pump 16, as long as it is not yet attached to the engine block 54 of the internal combustion engine. It is understood that after installation of the piston pump 16 in the receiving opening 52 in the engine block 54, a contact between the stopper 78 and the shoulder 48 is excluded, as in FIG. 2 shown.
  • FIG. 2 It is also apparent that the piston 36, the second sleeve part 66, and the central portion 74 of the first sleeve member 64, and the housing 28, a compensation chamber 94 is limited, via a channel 96 with the pressure damper (reference numeral 98 in the FIGS. 4 and 5 ) connected is. With the pressure damper 98 is further connected via a channel 100 remote from the working space 38 portion of the quantity control valve.
  • the function of the compensation chamber 94 results from the FIGS. 4 and 5 : During a suction stroke ( FIG. 4 ) The piston 36 moves in the direction of arrow 102. Through the combined intake and quantity control valve 26, fuel flows from the pressure damper 98 and from the compensation chamber 94 via the channel 96 into the working space 38 Pressure damper 98 connected via a channel 104 to the outlet of the feed pump 14.
  • the inlet / quantity control valve 26 is opened during the compression stroke, whereby high-pressure fuel flows out of the working space 38 in accordance with the arrows 110.
  • a resulting pressure pulsation is reduced on the one hand by the pressure damper 98, on the other hand, the outflowing fuel volume is also absorbed by the volume of the expansion chamber 94 which increases during a compression stroke.
  • the corresponding stroke volume in the compensation chamber 94 is determined by the area of the shoulder 48 between the two regions 44 and 46 of the piston 36. It is in FIG. 5 indicated by a dotted line 112 and is approximately 40-60% of the stroke volume in the working space 38 (reference numeral 114 in FIG. 4 ).
  • the filling of the working space 38 is supported during the suction stroke by the decreasing volume of the compensation chamber 94. This leads to an improvement of the dynamics and also of the efficiency of the piston pump 10.

Claims (14)

  1. Pompe à piston (16), en particulier pompe à carburant haute pression pour un moteur à combustion interne, comprenant un boîtier (28) et un piston (36), qui délimite un espace de travail (38) et qui présente un épaulement (48) détourné de l'espace de travail (38), caractérisée en ce que le piston (38) est introduit avec l'extrémité côté espace de travail en avant dans le boîtier (28) et un élément de butée (60) est fixé sur le boîtier (28), lequel élément de butée présente une butée (78) qui coopère au moins temporairement avec l'épaulement (48).
  2. Pompe à piston (16) selon la revendication 1, caractérisée en ce que l'épaulement est formé par un gradin annulaire (48) sur le piston (36).
  3. Pompe à piston (16) selon la revendication 2, caractérisée en ce que le gradin annulaire (48) délimite un espace d'équilibrage (94) séparé fluidiquement de l'espace de travail (38), lequel espace d'équilibrage est connecté à une région éloignée de l'espace de travail (38), d'une soupape de commande quantitative (26) du côté de l'entrée.
  4. Pompe à piston (16) selon la revendication 3, caractérisée en ce qu'entre l'espace d'équilibrage (94) et la soupape de commande quantitative (26) est disposé un amortisseur de pression (98).
  5. Pompe à piston (16) selon l'une quelconque des revendications 2 à 4, caractérisée en ce que la surface hydrauliquement active du gradin annulaire (48) est approximativement deux fois plus petite que la surface hydrauliquement active du piston (36) saillant dans l'espace de travail (38).
  6. Pompe à piston (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de butée (60) comprend une partie de douille (66) coaxiale au piston (36) avec une région située radialement à l'intérieur, sur laquelle est réalisée la butée (78).
  7. Pompe à piston (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de butée (60) comprend une partie de douille (64) coaxiale au piston (36), qui présente, sur une région située radialement à l'extérieur, une portion de fixation (76) s'étendant axialement au niveau de laquelle la partie de douille (64) est connectée au boîtier (28), de préférence par pressage et/ou soudage (88).
  8. Pompe à piston (16) selon la revendication 8, caractérisée en ce qu'un ressort de piston (90) s'appuie sur une portion (74) de la partie de douille (64) s'étendant radialement, laquelle est disposée radialement à l'intérieur de la portion de fixation axiale (76).
  9. Pompe à piston (16) selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle comprend un joint d'étanchéité de piston (62) fixé au boîtier, qui s'applique contre une surface d'enveloppe du piston (36) et qui sépare une région de refoulement (68) d'une région d'entraînement (70), et en ce que le joint d'étanchéité de piston (62) est maintenu par une portion de retenue (86) de l'élément de butée (60).
  10. Pompe à piston (16) selon la revendication 9, caractérisée en ce que l'élément de butée (60) comprend une première partie de douille (64) qui retient le joint d'étanchéité de piston (62) et une deuxième partie de douille (66) sur laquelle est prévue la butée (78).
  11. Pompe à piston (16) selon la revendication 10, caractérisée en ce que la portion de retenue comprend une chambre d'échangeur de chaleur (86) dans laquelle est reçu le joint d'étanchéité de piston (62), et qui est formée entre la première partie de douille (64) et la deuxième partie de douille (66).
  12. Pompe à piston (16) selon l'une quelconque des revendications 10 ou 11, caractérisée en ce que les deux parties de douille (64, 66) sont pressées l'une contre l'autre.
  13. Pompe à piston (16) selon l'une quelconque des revendications 10 à 12, caractérisée en ce que les deux parties de douille (64, 66) et le joint d'étanchéité de piston (62) constituent un module prémonté (58).
  14. Pompe à piston (16) selon l'une quelconque des revendications précédentes, caractérisée en ce qu'à l'extrémité du piston (36) opposée à l'espace de travail (38) est pressé un élément de support (92) pour un ressort de piston (90), et en ce que le piston (36) peut s'appuyer sur une paroi de l'espace de travail (38) pendant le pressage de l'élément de support (92).
EP05797277A 2004-12-28 2005-10-05 Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne Active EP1834089B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004063075.5A DE102004063075B4 (de) 2004-12-28 2004-12-28 Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine mit einem Stufenkolben und einem Mengensteuerventil
PCT/EP2005/055002 WO2006069818A1 (fr) 2004-12-28 2005-10-05 Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1834089A1 EP1834089A1 (fr) 2007-09-19
EP1834089B1 true EP1834089B1 (fr) 2012-12-12

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EP05797277A Active EP1834089B1 (fr) 2004-12-28 2005-10-05 Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne

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EP (1) EP1834089B1 (fr)
JP (1) JP4664989B2 (fr)
CN (1) CN101094988B (fr)
DE (1) DE102004063075B4 (fr)
ES (1) ES2395942T3 (fr)
WO (1) WO2006069818A1 (fr)

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DE102013224797A1 (de) 2013-12-04 2015-06-11 Robert Bosch Gmbh Kraftstoffpumpe mit einem Kolben, an dessen einem Antrieb zugewandten Endabschnitt ein Federteiler angeordnet ist
US9709055B2 (en) 2008-04-25 2017-07-18 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism

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JP4736142B2 (ja) * 2009-02-18 2011-07-27 株式会社デンソー 高圧ポンプ
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JP4941688B2 (ja) 2009-11-09 2012-05-30 株式会社デンソー 高圧ポンプ
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JP5352646B2 (ja) * 2011-01-27 2013-11-27 株式会社日本自動車部品総合研究所 高圧ポンプ
JP5319713B2 (ja) * 2011-01-28 2013-10-16 株式会社デンソー 高圧ポンプ
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JP5668978B2 (ja) * 2011-02-25 2015-02-12 株式会社デンソー 高圧ポンプ
JP5703893B2 (ja) * 2011-03-28 2015-04-22 株式会社デンソー 高圧ポンプ
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EP2935859B1 (fr) * 2012-12-20 2016-12-21 Robert Bosch GmbH Pompe à carburant alternative pour moteur à combustion interne
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JP6225648B2 (ja) * 2013-11-12 2017-11-08 株式会社デンソー 高圧ポンプ
DE102014209288A1 (de) * 2014-05-16 2015-11-19 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoffpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine
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JP6369337B2 (ja) * 2015-01-20 2018-08-08 株式会社デンソー 高圧ポンプ及びその製造方法
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DE102016202211A1 (de) * 2016-02-12 2017-08-31 Continental Automotive Gmbh Kraftstoffhochdruckpumpe und Verfahren zur Herstellung einer Kraftstoffhochdruckpumpe
DE102016206366A1 (de) * 2016-04-15 2017-05-11 Continental Automotive Gmbh Kraftstoffhochdruckpumpe
CN109937297A (zh) * 2016-11-18 2019-06-25 日立汽车系统株式会社 高压燃料供给泵
KR101986018B1 (ko) 2017-09-20 2019-06-04 주식회사 현대케피코 고압연료펌프
KR101986017B1 (ko) 2017-09-20 2019-09-03 주식회사 현대케피코 고압연료펌프
CN110195673B (zh) * 2018-02-27 2021-05-14 纬湃汽车电子(长春)有限公司 高压泵
DE102018203319A1 (de) * 2018-03-06 2019-09-12 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
KR102107462B1 (ko) * 2018-12-14 2020-05-07 주식회사 현대케피코 고압펌프의 패킹캐리어 변형 방지 구조
KR102098376B1 (ko) 2018-12-21 2020-05-26 주식회사 현대케피코 고압펌프용 압력해제밸브
DE102020200596A1 (de) 2019-12-23 2021-06-24 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe
DE102020215458A1 (de) 2020-12-08 2022-06-09 Robert Bosch Gesellschaft mit beschränkter Haftung Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
DE102021202359A1 (de) 2021-03-11 2022-09-15 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe
DE102021208296A1 (de) * 2021-07-30 2023-02-02 Robert Bosch Gesellschaft mit beschränkter Haftung Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe
DE102021214498A1 (de) 2021-12-16 2023-06-22 Robert Bosch Gesellschaft mit beschränkter Haftung Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine

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US9709055B2 (en) 2008-04-25 2017-07-18 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
US10107285B2 (en) 2008-04-25 2018-10-23 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
DE102013224797A1 (de) 2013-12-04 2015-06-11 Robert Bosch Gmbh Kraftstoffpumpe mit einem Kolben, an dessen einem Antrieb zugewandten Endabschnitt ein Federteiler angeordnet ist

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JP4664989B2 (ja) 2011-04-06
ES2395942T3 (es) 2013-02-18
CN101094988B (zh) 2010-09-29
JP2008525713A (ja) 2008-07-17
DE102004063075B4 (de) 2015-11-26
CN101094988A (zh) 2007-12-26
WO2006069818A1 (fr) 2006-07-06
EP1834089A1 (fr) 2007-09-19
DE102004063075A1 (de) 2006-07-13

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