EP2141346A1 - Thermische Kompensationsanordnung und Einspritzventil - Google Patents

Thermische Kompensationsanordnung und Einspritzventil Download PDF

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Publication number
EP2141346A1
EP2141346A1 EP08012064A EP08012064A EP2141346A1 EP 2141346 A1 EP2141346 A1 EP 2141346A1 EP 08012064 A EP08012064 A EP 08012064A EP 08012064 A EP08012064 A EP 08012064A EP 2141346 A1 EP2141346 A1 EP 2141346A1
Authority
EP
European Patent Office
Prior art keywords
piston
front surface
thermal compensation
actuator unit
longitudinal axis
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.)
Granted
Application number
EP08012064A
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English (en)
French (fr)
Other versions
EP2141346B1 (de
Inventor
Ivano Izzo
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Priority to DE200860004641 priority Critical patent/DE602008004641D1/de
Priority to EP20080012064 priority patent/EP2141346B1/de
Publication of EP2141346A1 publication Critical patent/EP2141346A1/de
Application granted granted Critical
Publication of EP2141346B1 publication Critical patent/EP2141346B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the invention relates to a thermal compensation arrangement and an injection valve.
  • Injection valves are in wide spread use, in particular for internal combustion engines where they may be arranged in order to dose the fluid into an intake manifold of the internal combustion engine or directly into the combustion chamber of a cylinder of the internal combustion engine.
  • Injection valves for an internal combustion engine comprise actuator units.
  • the actuator unit In order to inject fuel, the actuator unit is energized so that a fluid flow through the fluid outlet portion of the injection valve is enabled.
  • the respective injection valve may be suited to dose fluids under very high pressures.
  • the pressures may be in case of a gasoline engine, for example in the range of up to 200 bar or in the case of diesel engines in the range of up to 2,000 bar.
  • the injection of fluids under such high pressures has to be carried out very precisely.
  • the object of the invention is to create a thermal compensation arrangement and an injection valve that are simply to be manufactured and which facilitate a reliable and precise function of the injection valve.
  • the invention is distinguished by a thermal compensation arrangement comprising a housing including a first central longitudinal axis, the housing comprising a cavity, a solid state actuator unit being arranged in the cavity and having a first axial end and a second axial end, the second axial end acting as a drive side of the actuator unit and a thermal compensation unit being arranged in the cavity and being coupled to the first axial end of the actuator unit.
  • the thermal compensation unit comprises a casing being coupable to the housing and comprising a recess, a piston axially movable in the recess and being coupable to the actuator unit, the piston having a first front surface facing the solid state actuator unit and a second front surface facing away from the first front surface, a gap being formed in the recess and extending in radial direction between the piston and the casing and a piston channel being arranged in the piston and extending from the first front surface to the second front surface of the piston thereby enabling a fluid flow through the piston channel.
  • the piston channel comprises a converging section, which converges towards the first front surface of the piston.
  • the thermal compensation arrangement may be easy to be manufactured. Due to the shape of the piston channel comprising the converging section, the thermal compensation arrangement has the advantage that a mechanical component to regulate a fluid flow, for example a flapper valve, is not required. Thereby, the assembly process line may be simplified. For example, a welding of a flapper valve to the piston may be obsolete. Thus, low production costs may be enabled. By leaving out a mechanical component such as a flapper valve, one source of faultiness of the thermal compensation arrangement may be left out due to a possible wearing of the mechanical component.
  • the recess of the casing is a cylindrical bore hole.
  • the piston channel comprises a second central longitudinal axis and is inclined in a direction of the second central longitudinal axis relative to the first central longitudinal axis.
  • the piston channel comprises a second central longitudinal axis, wherein the second central longitudinal axis extends at least partly parallel to the first central longitudinal axis.
  • the piston channel may be easy to be manufactured.
  • the invention is distinguished by an injection valve comprising the thermal compensation arrangement in accordance with the first aspect of the invention.
  • An injection valve 10 ( figure 1 ) that is used as a fuel injection valve for an internal combustion engine, comprises a thermal compensation arrangement 12, which comprises a housing 14, a solid state actuator unit 16 with a first axial end 16a and a second axial end 16b acting as a drive side of the actuator unit and a thermal compensation unit 18.
  • the housing 14 has a tubular shape.
  • the actuator unit 16 is inserted into the housing 14 and comprises a piezo actuator, which changes its axial length depending on a control signal applied to it.
  • the actuator unit 16 may, however, also comprise another type of actuator, which is known to person skilled in the art for that purpose.
  • Such an actuator may be, for example, a solenoid.
  • the injection valve 10 comprises a valve body 20 with a first central longitudinal axis A.
  • the housing 14 has a cavity 22 which is axially led through the valve body 20.
  • a fluid outlet portion 24 is formed which is closed or open depending on the axial position of a valve needle 26.
  • the injection valve 10 further has a fluid inlet portion 28 which is arranged in the housing 14 and which is hydraulically coupled to the cavity 22 and a not shown fuel connector.
  • the fuel connector is designed to be connected to a high pressure fuel chamber of an internal combustion engine, the fuel is stored under high pressure, for example, under the pressure above 200 bar.
  • the valve body 20 has a valve body spring rest 30 and the valve needle 26 comprises a valve needle spring rest 32, both spring rests 30, 32 supporting a main spring 34 being arranged between the valve body 20 and the valve needle 26.
  • the injection valve 10 is of an outward opening type. In an alternative embodiment, the injection valve 10 may be of an inward opening type.
  • a bellow 36 is arranged which is sealingly coupling the valve body 20 with the valve needle 26. By this a fluid flow between the cavity 22 and a chamber 38 is prevented. Furthermore, the bellow 36 is formed and arranged in a way that the valve needle 26 is actuable by the actuator unit 16.
  • Figure 2 shows a longitudinal sectional view of the thermal compensation arrangement 12 arranged in the housing 14 and coupled to the actuator unit 16.
  • the thermal compensation unit 18 has a casing 40 of a cylindrical shape which has a recess 42, in which a piston 44 is arranged.
  • the piston 44 is of a cylindrical shape and extends in the axial direction of the casing 40 and is coupled to the actuator unit 16 by a connecting bar 45.
  • the recess 42 of the casing 40 is a cylindrical bore hole.
  • the thermal compensation unit 18 comprises a sealing element 46 arranged in a piston rest 48 being part of the casing 40 and supporting the piston 44 in an initial state of the thermal compensation unit 18 as described below.
  • a spring retaining element 50 is mechanically coupled to the thermal compensation unit 18 by the connecting bar 45.
  • a compensation spring 52 is arranged between the sealing element 46 of the thermal compensation unit 18 and a spring retaining element spring rest 54 of the spring retaining element 50 to support the compensation spring 52.
  • the thermal compensation arrangement 12 is rigidly coupled to the housing 14 of the injection valve 10 by a welding seam 56 extending circumferentially over a side surface 57 of the casing 40 of the thermal compensation arrangement 12.
  • Figure 3 and 4 show the thermal compensation unit 18 of the thermal compensation arrangement 12 in a longitudinal sectional and in large detailed view.
  • the piston 44 of the thermal compensation arrangement 12 has a first front surface 58 facing the solid state actuator unit 16 and a second front surface 59 facing away from the first front surface 58 thereby facing away from the solid state actuator unit 16.
  • the cylindrical shaped piston 44 furthermore has a lateral surface 60 extending between the first front surface 58 and the second front surface 59.
  • a gap 62 is formed being a part of the recess 42 of the casing 40.
  • a recess section 64 is extending in axial direction.
  • a bottom recess section 66 is arranged between the first front surface 58 of the piston 44 and the sealing element 46 . The recess section 64 and the bottom recess section 66 are part of the recess 42 of the casing 40.
  • a piston channel 68 is arranged in the piston 44 and extends from the first front surface 58 of the piston 44 to the second front surface 59 of the piston 44.
  • the piston channel 68 allows a hydraulic coupling of the recess section 64 between the second front surface 59 of the piston 44 and the casing 40 and the bottom recess section 66 extending between the sealing element 46 and the first front surface 58 of the piston 44.
  • the diameter of the gap 62 is much smaller than the diameter of the piston channel 68. In figure 3 and 4 , the gap 62 is depicted with a much bigger diameter than it is compared to the dimensions of further depicted components in figure 3 and 4 to illustrate a fluid flow.
  • the piston channel 68 comprises a converging section 70, which converges towards the first front surface 58 of the piston 44.
  • the diminution of the diameter of the piston channel 68 along the converging section 70 ranges from 40% to 95% compared to the diameter of further parts of the piston channel 68.
  • the converging section 70 comprises an angle in the range of 3° to 15° compared to further parts of the piston channel 68.
  • the piston channel 68 comprises a second central longitudinal axis B and may be inclined in a direction of the second central longitudinal axis B relative to the first central longitudinal axis A.
  • the second central longitudinal axis B extends at least partly parallel to the first central longitudinal axis A. This allows a good performance of the fluid flow from the bottom recess section 66 facing the first front surface 58 to the recess section 64 facing the second front surface 59.
  • the fuel is led from the fluid inlet portion 28 in the housing 14 towards the valve body 20 and then towards the fluid outlet portion 24.
  • the valve needle 26 prevents a fluid flow through the fluid outlet portion 24 in the valve body 20 in a closing position of the valve needle 26. Outside of the closing position of the valve needle 26, the valve needle 26 enables the fluid flow through the fluid outlet portion 24.
  • the piezo electric actuator may change its axial length if it gets energized. By changing its length the actuator unit 16 may exert a force on the valve needle 26. Due to the elasticity of the bellow 36 the valve needle 26 is able to move in axial direction out of the closing position. Outside the closing position of the valve needle 26 there is a gap between the valve body 20 and the valve needle 26 at an axial end of the injection valve 10 facing away from the actuator unit 16. The gap is forming a valve nozzle 72.
  • the main spring 34 can force the valve needle 26 via the valve needle spring rest 32 towards the actuator unit 16. In the case the actuator unit 16 is de-energized the actuator unit 16 shortens its length. Due to the elasticity of the bellow 36 the main spring 34 can force the valve needle 26 to move in axial direction in its closing position. It is depending on the force balance between the force on the valve needle 26 caused by the actuator unit 16 and the force on the valve needle 26 caused by the main spring 34 whether the valve needle 26 is in its closing position or not. If the valve needle 26 is not in its closing position a fuel flow is enabled through the valve nozzle 72.
  • the thermal compensation arrangement 12 serves two purposes: first the compensation of changes of the length of the actuator unit 16 due to thermal variations, which are comparably slow changes, and second providing stiffness against impulsive forces of the actuator unit 16 due to an energizing and a de-energizing of the actuator unit 16 to avoid an energy loss.
  • the thermal compensation arrangement 12 concerning the compensation of changes of the length of the actuator unit 16 due to thermal variations will be described in detail. If the temperature of the injection valve 10 increases during its operation, the injection valve 10, especially the housing 14, expands its axial length. In general, the housing 14, which is preferably made of stainless steel, expands more with the temperature than the actuator unit 16, which may comprise ceramic. The thermal compensation unit 18 is arranged in order to compensate that thermal expansion, especially of the housing 14 of the injection valve 10.
  • the recess section 64 and the bottom recess section 66 are filled with fluid, preferably oil.
  • the fluid in the recess section 64 and the bottom recess section 66 is pressurized by the compensation spring 52, which is arranged in such a way that the compensation spring 52 acts on the sealing element 46 and therewith the piston 44.
  • the second front surface 59 of the piston 44 has a larger surface than the first front surface 58 of the piston 44 because of the connecting bar 45.
  • the thermal compensation unit 18 is arranged in the injection valve 10, it is arranged in such a way that the thermal compensation unit 18 is preloaded. So, the actuator unit 16 never loses contact to the connecting bar 45.
  • the piston 44 in the recess 42 of the casing 40 is moved in axial direction in a first piston movement direction P1 ( Fig. 3 ) away from the sealing element 46.
  • the fluid in the recess 42 flows in a fluid flow direction F from the recess section 64 to the bottom recess section 66 via the piston channel 68 and the gap 62.
  • the piston 44 looses contact with the piston rest 48 allowing the fluid flowing from the gap 62 and the piston channel 68 to the bottom recess section 66 adjacent to the sealing element 46.
  • the volume of the bottom recess section 66 is increasing while the volume of the recess section 64 is decreasing.
  • the piston 44 of the thermal compensation arrangement 12 is forced to move in a second piston movement direction P2 ( Fig. 4 ) towards the sealing element 46.
  • P2 Fig. 4
  • the fluid flows through the piston channel 68 into the recess section 64 between the second front surface 59 of the piston 44 and the casing 40. So the thermal expansion of the housing 14 can be compensated.
  • thermal compensation arrangement 12 concerning the fast movements of the piston 44, for example due to energizing and de-energizing of the actuator unit 16, will be described in detail.
  • the actuator unit 16 may expand only for few microseconds before it gets de-energized in a typical application for dosing fluid. This duration is too short for a substantive amount of the fluid to pass the gap 62 or the converging section 70 of the piston channel 68 in order to level out the pressure differences between the recess section 64 and the bottom recess section 66 substantially. Thus, only small movements are possible. In that duration, the piston 44 stays nearly in its position and the actuator unit 16 has a nearly solid base to act on so that the actuator unit 16 acts on the valve needle 26 in order to move the valve needle 26 out of its closing position.
  • the thermal compensation arrangement 12 is shown in an exemplary state.
  • the shown state of the piston 44 is an ultimate state that is the lowest possible state of the piston 44 regarding the first longitudinal axis A in the illustration of figure 3 . This means that the piston 44 is in contact with the piston rest 48 due to the spring forces of the compensation spring 52.
  • the actuator unit 16 If the actuator unit 16 is energized and therefore changes its length to move the valve needle 26 out of the closing position simultaneously the piston 44 is subjected to an impulsive force in axial direction in the first piston movement direction P1 ( Fig. 3 ) away from the sealing element 46. Due to the impulsive force, a pressure wave is caused in the recess section 64 between the second front surface 59 of the piston 44 and the casing 40 of the thermal compensation unit 18.
  • the piston 44 stays nearly in its position, in particular also in view of the impulsive character of the impulsive force which the piston 44 is subjected to, and the actuator unit 16 has a nearly solid base to act on.
  • the piston 44 of the thermal compensation arrangement 12 is forced to move in a second piston movement direction P2 ( Fig. 4 ) towards the sealing element 46. Due to the short duration of the impulsive force acting in the first piston movement direction P1 on the piston 44, the de-energizing mainly results in the compensation of the prior to this existing pressure difference between the fluid in the recess section 64 and the bottom recess section 66 and further only results in a comparatively small further pressure difference of opposite sign due to the very small change of position of the piston 44 during the short duration of the impulsive force.
  • piston channel 68 and/or the converging section 70 of the piston channel 68 may comprise a different shape.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20080012064 2008-07-03 2008-07-03 Thermische Kompensationsanordnung und Einspritzventil Expired - Fee Related EP2141346B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200860004641 DE602008004641D1 (de) 2008-07-03 2008-07-03 Thermische Kompensationsanordnung und Einspritzventil
EP20080012064 EP2141346B1 (de) 2008-07-03 2008-07-03 Thermische Kompensationsanordnung und Einspritzventil

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20080012064 EP2141346B1 (de) 2008-07-03 2008-07-03 Thermische Kompensationsanordnung und Einspritzventil

Publications (2)

Publication Number Publication Date
EP2141346A1 true EP2141346A1 (de) 2010-01-06
EP2141346B1 EP2141346B1 (de) 2011-01-19

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ID=40137987

Family Applications (1)

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EP20080012064 Expired - Fee Related EP2141346B1 (de) 2008-07-03 2008-07-03 Thermische Kompensationsanordnung und Einspritzventil

Country Status (2)

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EP (1) EP2141346B1 (de)
DE (1) DE602008004641D1 (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1519035A1 (de) * 2003-09-17 2005-03-30 Robert Bosch GmbH Brennstoffeinspritzventil
EP1813805A1 (de) * 2006-01-27 2007-08-01 Siemens VDO Automotive S.p.A. Kompensationsvorrichtung für einen Injektor
EP1881189A1 (de) * 2006-07-21 2008-01-23 Siemens Aktiengesellschaft Kolben-Zylinder-Aggregat und hydraulisches kompensationsvorrichtung
EP1887216A1 (de) * 2006-08-02 2008-02-13 Siemens Aktiengesellschaft Anordnung zum thermischen Ausgleich in einem Einspritzventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1519035A1 (de) * 2003-09-17 2005-03-30 Robert Bosch GmbH Brennstoffeinspritzventil
EP1813805A1 (de) * 2006-01-27 2007-08-01 Siemens VDO Automotive S.p.A. Kompensationsvorrichtung für einen Injektor
EP1881189A1 (de) * 2006-07-21 2008-01-23 Siemens Aktiengesellschaft Kolben-Zylinder-Aggregat und hydraulisches kompensationsvorrichtung
EP1887216A1 (de) * 2006-08-02 2008-02-13 Siemens Aktiengesellschaft Anordnung zum thermischen Ausgleich in einem Einspritzventil

Also Published As

Publication number Publication date
DE602008004641D1 (de) 2011-03-03
EP2141346B1 (de) 2011-01-19

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