EP2141346A1 - Thermal compensation arrangement and injection valve - Google Patents
Thermal compensation arrangement and injection valve Download PDFInfo
- 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
Links
- 238000002347 injection Methods 0.000 title claims description 29
- 239000007924 injection Substances 0.000 title claims description 29
- 239000012530 fluid Substances 0.000 claims abstract description 43
- 239000007787 solid Substances 0.000 claims abstract description 12
- 238000007789 sealing Methods 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 8
- 239000000446 fuel Substances 0.000 description 8
- 230000004323 axial length Effects 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 239000000919 ceramic Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
Images
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
Abstract
Description
- 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. 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.
- In order to enhance the combustion process in view of the creation of unwanted emissions, 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.
- These objects are achieved by the features of the independent claims. Advantageous embodiments of the invention are given in the sub-claims.
- According to a first aspect 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.
- This has the advantage that a reliable and precise function of the thermal compensation arrangement is enabled. Moreover, 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. Moreover, in the case of an axial movement of the piston in direction to the actuator unit a high fluid flow rate from a bottom recess section facing the first front surface to a recess section facing the second front surface is possible. Preferably, the recess of the casing is a cylindrical bore hole.
- In an advantageous embodiment 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.
- This allows a good performance of the fluid flow from the bottom recess section facing the first front surface to the recess section facing the second front surface.
- In a further advantageous embodiment 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.
- This allows a good performance of the fluid flow from the bottom recess section facing the first front surface to the recess section facing the second front surface. Moreover, the piston channel may be easy to be manufactured.
- According to a second aspect the invention is distinguished by an injection valve comprising the thermal compensation arrangement in accordance with the first aspect of the invention.
- This has the advantage that a reliable and precise function of the injection valve is enabled.
- Exemplary embodiments of the invention are explained in the following with the help of schematic drawings. These are as follows:
- Figure 1,
- an injection valve in a longitudinal section view,
- Figure 2,
- an enlarged view of a part of the injection valve according to
figure 1 with a thermal compensation arrangement, - Figure 3,
- an enlarged view of a thermal compensation unit of the thermal compensation arrangement for the injection valve in a first operating condition, and
- Figure 4,
- an enlarged view of the thermal compensation unit of the thermal compensation arrangement for the injection valve in a second operating condition.
- Elements of the same design and function that appear in different illustrations are identified by the same reference characters.
- An injection valve 10 (
figure 1 ) that is used as a fuel injection valve for an internal combustion engine, comprises athermal compensation arrangement 12, which comprises ahousing 14, a solidstate actuator unit 16 with a firstaxial end 16a and a secondaxial end 16b acting as a drive side of the actuator unit and athermal compensation unit 18. - The
housing 14 has a tubular shape. Theactuator unit 16 is inserted into thehousing 14 and comprises a piezo actuator, which changes its axial length depending on a control signal applied to it. Theactuator 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 avalve body 20 with a first central longitudinal axis A. Thehousing 14 has acavity 22 which is axially led through thevalve body 20. On one of the free ends of thecavity 22, afluid outlet portion 24 is formed which is closed or open depending on the axial position of avalve needle 26. Theinjection valve 10 further has afluid inlet portion 28 which is arranged in thehousing 14 and which is hydraulically coupled to thecavity 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 valvebody spring rest 30 and thevalve needle 26 comprises a valveneedle spring rest 32, both spring rests 30, 32 supporting amain spring 34 being arranged between thevalve body 20 and thevalve needle 26. - The
injection valve 10 is of an outward opening type. In an alternative embodiment, theinjection valve 10 may be of an inward opening type. Between thevalve needle 26 and the valve body 20 abellow 36 is arranged which is sealingly coupling thevalve body 20 with thevalve needle 26. By this a fluid flow between thecavity 22 and achamber 38 is prevented. Furthermore, thebellow 36 is formed and arranged in a way that thevalve needle 26 is actuable by theactuator unit 16. -
Figure 2 shows a longitudinal sectional view of thethermal compensation arrangement 12 arranged in thehousing 14 and coupled to theactuator unit 16. - The
thermal compensation unit 18 has acasing 40 of a cylindrical shape which has arecess 42, in which apiston 44 is arranged. Thepiston 44 is of a cylindrical shape and extends in the axial direction of thecasing 40 and is coupled to theactuator unit 16 by a connectingbar 45. Preferably, therecess 42 of thecasing 40 is a cylindrical bore hole. - The
thermal compensation unit 18 comprises asealing element 46 arranged in apiston rest 48 being part of thecasing 40 and supporting thepiston 44 in an initial state of thethermal compensation unit 18 as described below. - A
spring retaining element 50 is mechanically coupled to thethermal compensation unit 18 by the connectingbar 45. Acompensation spring 52 is arranged between the sealingelement 46 of thethermal compensation unit 18 and a spring retainingelement spring rest 54 of thespring retaining element 50 to support thecompensation spring 52. - The
thermal compensation arrangement 12 is rigidly coupled to thehousing 14 of theinjection valve 10 by awelding seam 56 extending circumferentially over aside surface 57 of thecasing 40 of thethermal compensation arrangement 12. -
Figure 3 and4 show thethermal compensation unit 18 of thethermal compensation arrangement 12 in a longitudinal sectional and in large detailed view. Thepiston 44 of thethermal compensation arrangement 12 has a firstfront surface 58 facing the solidstate actuator unit 16 and a secondfront surface 59 facing away from the firstfront surface 58 thereby facing away from the solidstate actuator unit 16. The cylindrical shapedpiston 44 furthermore has alateral surface 60 extending between the firstfront surface 58 and the secondfront surface 59. - Between the
lateral surface 60 of thepiston 44 and thecasing 40 of thethermal compensation unit 18, agap 62 is formed being a part of therecess 42 of thecasing 40. Between the secondfront surface 59 of thepiston 44 and the casing 40 arecess section 64 is extending in axial direction. Between the firstfront surface 58 of thepiston 44 and the sealing element 46 abottom recess section 66 is arranged. Therecess section 64 and thebottom recess section 66 are part of therecess 42 of thecasing 40. - It will be described in the following that the
recess section 64 and thebottom recess section 66 are changing their volumes in the case of an axial movement of thepiston 44 in thecasing 40. - A
piston channel 68 is arranged in thepiston 44 and extends from the firstfront surface 58 of thepiston 44 to the secondfront surface 59 of thepiston 44. Thepiston channel 68 allows a hydraulic coupling of therecess section 64 between the secondfront surface 59 of thepiston 44 and thecasing 40 and thebottom recess section 66 extending between the sealingelement 46 and the firstfront surface 58 of thepiston 44. The diameter of thegap 62 is much smaller than the diameter of thepiston channel 68. Infigure 3 and4 , thegap 62 is depicted with a much bigger diameter than it is compared to the dimensions of further depicted components infigure 3 and4 to illustrate a fluid flow. - The
piston channel 68 comprises a convergingsection 70, which converges towards the firstfront surface 58 of thepiston 44. Preferably, the diminution of the diameter of thepiston channel 68 along the convergingsection 70 ranges from 40% to 95% compared to the diameter of further parts of thepiston channel 68. For example, the convergingsection 70 comprises an angle in the range of 3° to 15° compared to further parts of thepiston 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. In a further exemplary embodiment, 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 thebottom recess section 66 facing the firstfront surface 58 to therecess section 64 facing the secondfront surface 59. - In the following, the function of the
injection valve 10 will be described: - The fuel is led from the
fluid inlet portion 28 in thehousing 14 towards thevalve body 20 and then towards thefluid outlet portion 24. - The
valve needle 26 prevents a fluid flow through thefluid outlet portion 24 in thevalve body 20 in a closing position of thevalve needle 26. Outside of the closing position of thevalve needle 26, thevalve needle 26 enables the fluid flow through thefluid outlet portion 24. - In the case that the
actuator unit 16 has a piezo electric actuator, the piezo electric actuator may change its axial length if it gets energized. By changing its length theactuator unit 16 may exert a force on thevalve needle 26. Due to the elasticity of thebellow 36 thevalve needle 26 is able to move in axial direction out of the closing position. Outside the closing position of thevalve needle 26 there is a gap between thevalve body 20 and thevalve needle 26 at an axial end of theinjection valve 10 facing away from theactuator unit 16. The gap is forming avalve nozzle 72. - The
main spring 34 can force thevalve needle 26 via the valveneedle spring rest 32 towards theactuator unit 16. In the case theactuator unit 16 is de-energized theactuator unit 16 shortens its length. Due to the elasticity of thebellow 36 themain spring 34 can force thevalve needle 26 to move in axial direction in its closing position. It is depending on the force balance between the force on thevalve needle 26 caused by theactuator unit 16 and the force on thevalve needle 26 caused by themain spring 34 whether thevalve needle 26 is in its closing position or not. If thevalve needle 26 is not in its closing position a fuel flow is enabled through thevalve nozzle 72. - The
thermal compensation arrangement 12 serves two purposes: first the compensation of changes of the length of theactuator unit 16 due to thermal variations, which are comparably slow changes, and second providing stiffness against impulsive forces of theactuator unit 16 due to an energizing and a de-energizing of theactuator unit 16 to avoid an energy loss. - In the following the function of the
thermal compensation arrangement 12 concerning the compensation of changes of the length of theactuator unit 16 due to thermal variations will be described in detail. If the temperature of theinjection valve 10 increases during its operation, theinjection valve 10, especially thehousing 14, expands its axial length. In general, thehousing 14, which is preferably made of stainless steel, expands more with the temperature than theactuator unit 16, which may comprise ceramic. Thethermal compensation unit 18 is arranged in order to compensate that thermal expansion, especially of thehousing 14 of theinjection valve 10. - During the operation of the
thermal compensation arrangement 12, therecess section 64 and thebottom recess section 66 are filled with fluid, preferably oil. The fluid in therecess section 64 and thebottom recess section 66 is pressurized by thecompensation spring 52, which is arranged in such a way that thecompensation spring 52 acts on the sealingelement 46 and therewith thepiston 44. There is the same pressure of the fluid in therecess section 64 and thebottom recess section 66 due to thepiston channel 68 and thegap 62. The secondfront surface 59 of thepiston 44 has a larger surface than the firstfront surface 58 of thepiston 44 because of the connectingbar 45. The pressure acting on the larger surface of the secondfront surface 59 of thepiston 44 causes a bigger force on thepiston 44 then the pressure acting on the firstfront surface 58 of thepiston 44. So, if there is no force acting on thethermal compensation unit 18 from the outside of thethermal compensation unit 18, thepiston 44 is pressed towards theactuator unit 16. In that way, the connectingbar 45 never loses contact to theactuator unit 16. - If the
thermal compensation unit 18 is arranged in theinjection valve 10, it is arranged in such a way that thethermal compensation unit 18 is preloaded. So, theactuator unit 16 never loses contact to the connectingbar 45. - If the
housing 14 reduces its axial length more with the changing temperature than theactuator unit 16, the force on thepiston 44 is increasing. Simultaneously, thepiston 44 in therecess 42 of thecasing 40 is moved in axial direction in a first piston movement direction P1 (Fig. 3 ) away from the sealingelement 46. The fluid in therecess 42 flows in a fluid flow direction F from therecess section 64 to thebottom recess section 66 via thepiston channel 68 and thegap 62. When thepiston 44 starts to move in the first piston direction P1, thepiston 44 looses contact with thepiston rest 48 allowing the fluid flowing from thegap 62 and thepiston channel 68 to thebottom recess section 66 adjacent to the sealingelement 46. During this the volume of thebottom recess section 66 is increasing while the volume of therecess section 64 is decreasing. - If the
housing 14 expands more with the changing temperature than theactuator unit 16, the force on thepiston 44 is decreasing. The fluid presses thepiston 44 towards theactuator unit 16. Consequently, thepiston 44 of thethermal compensation arrangement 12 is forced to move in a second piston movement direction P2 (Fig. 4 ) towards the sealingelement 46. During this the volume of therecess section 64 is increasing and the volume of thebottom recess section 66 is decreasing. The fluid flows through thepiston channel 68 into therecess section 64 between the secondfront surface 59 of thepiston 44 and thecasing 40. So the thermal expansion of thehousing 14 can be compensated. - In the following the function of the
thermal compensation arrangement 12 concerning the fast movements of thepiston 44, for example due to energizing and de-energizing of theactuator unit 16, will be described in detail. - If the
actuator unit 16 gets energized, it 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 thegap 62 or the convergingsection 70 of thepiston channel 68 in order to level out the pressure differences between therecess section 64 and thebottom recess section 66 substantially. Thus, only small movements are possible. In that duration, thepiston 44 stays nearly in its position and theactuator unit 16 has a nearly solid base to act on so that theactuator unit 16 acts on thevalve needle 26 in order to move thevalve needle 26 out of its closing position. - In
figure 3 , thethermal compensation arrangement 12 is shown in an exemplary state. The shown state of thepiston 44 is an ultimate state that is the lowest possible state of thepiston 44 regarding the first longitudinal axis A in the illustration offigure 3 . This means that thepiston 44 is in contact with thepiston rest 48 due to the spring forces of thecompensation spring 52. - If the
actuator unit 16 is energized and therefore changes its length to move thevalve needle 26 out of the closing position simultaneously thepiston 44 is subjected to an impulsive force in axial direction in the first piston movement direction P1 (Fig. 3 ) away from the sealingelement 46. Due to the impulsive force, a pressure wave is caused in therecess section 64 between the secondfront surface 59 of thepiston 44 and thecasing 40 of thethermal compensation unit 18. As the convergingsection 70 of thepiston channel 68 converges towards the firstfront surface 58 of thepiston 44, the molecules of the fluid interact strongly, which prevents a sliding of the molecules of the fluid apart of each other, and a high viscous resistance is caused for the fluid flowing from therecess section 64 through thepiston channel 68 to thebottom recess section 66. In addition, the comparatively small diameter of thegap 62 supports the high viscous resistance for the fluid flowing from therecess section 64 to thebottom recess section 66. Thus, a high damping coefficient is caused for the fluid flowing from therecess section 64 through thepiston channel 68 or thegap 62 to thebottom recess section 66. Therefore, thepiston 44 stays nearly in its position, in particular also in view of the impulsive character of the impulsive force which thepiston 44 is subjected to, and theactuator unit 16 has a nearly solid base to act on. - If the
actuator unit 16 is de-energized and consequently, theactuator unit 16 shortens its length to force thevalve needle 26 to move in axial direction into its closing position, thepiston 44 of thethermal compensation arrangement 12 is forced to move in a second piston movement direction P2 (Fig. 4 ) towards the sealingelement 46. Due to the short duration of the impulsive force acting in the first piston movement direction P1 on thepiston 44, the de-energizing mainly results in the compensation of the prior to this existing pressure difference between the fluid in therecess section 64 and thebottom 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 thepiston 44 during the short duration of the impulsive force. Thus, occurring forces return into their state as before energizing of theactuator unit 16 and thepiston 44 returns into its position as it was before theactuator unit 16 was energized. As the convergingsection 70 of thepiston channel 68 diverges towards the secondfront surface 59 of thepiston 44, a lower viscous resistance is caused for the fluid flowing from thebottom recess section 66 through thepiston channel 68 to therecess section 64 than flowing from therecess section 64 through thepiston channel 68 to thebottom recess section 66. Therefore, a lower damping coefficient is caused for the fluid flowing from thebottom recess section 66 to therecess section 64 than from therecess section 64 to thebottom recess section 66 and a higher fluid flow rate is possible. Thus, a fluid flow is enabled such that thepiston 44 returns into its position as it was before theactuator unit 16 was energized. Consequently, in view of the impulsive character of the impulsive force, which thepiston 44 is subjected to, thepiston 44 nearly stays in its position during an energizing and de-energizing of theactuator unit 16 such that theactuator unit 16 has a nearly solid base to act on. - The invention is not restricted by the explained embodiments. For example, the
piston channel 68 and/or the convergingsection 70 of thepiston channel 68 may comprise a different shape.
Claims (4)
- Thermal compensation arrangement (12) comprising- a housing (14) including a first central longitudinal axis (A), the housing (14) comprising a cavity (22),- a solid state actuator unit (16) being arranged in the cavity (22) and having a first axial end (16a) and a second axial end (16b), the second axial end (16b) acting as a drive side of the actuator unit (16),- a thermal compensation unit (18) being arranged in the cavity (22) and being coupled to the first axial end (16a) of the actuator unit (16), the thermal compensation unit (18) comprising- a casing (40) being coupable to the housing (14) and comprising a recess (42),- a piston (44) axially movable in the recess (42) and being coupable to the actuator unit (16), the piston (44) having 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),- a gap (62) being formed in the recess (42) and extending in radial direction between the piston (44) and the casing (40),- a piston channel (68) being arranged in the piston (44) and extending from the first front surface (58) to the second front surface (59) of the piston (44) thereby enabling a fluid flow through the piston channel (68), wherein the piston channel (68) comprises a converging section (70), which converges towards the first front surface (58) of the piston (44).
- Thermal compensation arrangement (12) in accordance with claim 1, with the piston channel (68) comprising a second central longitudinal axis (B) being inclined in a direction of the second central longitudinal axis (B) relative to the first central longitudinal axis (A).
- Thermal compensation arrangement (12) in accordance with claim 1, with the piston channel (68) comprising a second central longitudinal axis (B), wherein the second central longitudinal axis (B) extends at least partly parallel to the first central longitudinal axis (A).
- Injection valve (10) comprising the thermal compensation arrangement (12) in accordance with one of the preceding claims.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20080012064 EP2141346B1 (en) | 2008-07-03 | 2008-07-03 | Thermal compensation arrangement and injection valve |
DE200860004641 DE602008004641D1 (en) | 2008-07-03 | 2008-07-03 | Thermal compensation arrangement and injection valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20080012064 EP2141346B1 (en) | 2008-07-03 | 2008-07-03 | Thermal compensation arrangement and injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2141346A1 true EP2141346A1 (en) | 2010-01-06 |
EP2141346B1 EP2141346B1 (en) | 2011-01-19 |
Family
ID=40137987
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20080012064 Expired - Fee Related EP2141346B1 (en) | 2008-07-03 | 2008-07-03 | Thermal compensation arrangement and injection valve |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2141346B1 (en) |
DE (1) | DE602008004641D1 (en) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1519035A1 (en) * | 2003-09-17 | 2005-03-30 | Robert Bosch GmbH | Fuel injection valve |
EP1813805A1 (en) * | 2006-01-27 | 2007-08-01 | Siemens VDO Automotive S.p.A. | Compensation assembly for an injector |
EP1881189A1 (en) * | 2006-07-21 | 2008-01-23 | Siemens Aktiengesellschaft | Piston-cylinder system and hydraulic compensation device |
EP1887216A1 (en) * | 2006-08-02 | 2008-02-13 | Siemens Aktiengesellschaft | Thermal compensation arrangement in an injection valve |
-
2008
- 2008-07-03 DE DE200860004641 patent/DE602008004641D1/en active Active
- 2008-07-03 EP EP20080012064 patent/EP2141346B1/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1519035A1 (en) * | 2003-09-17 | 2005-03-30 | Robert Bosch GmbH | Fuel injection valve |
EP1813805A1 (en) * | 2006-01-27 | 2007-08-01 | Siemens VDO Automotive S.p.A. | Compensation assembly for an injector |
EP1881189A1 (en) * | 2006-07-21 | 2008-01-23 | Siemens Aktiengesellschaft | Piston-cylinder system and hydraulic compensation device |
EP1887216A1 (en) * | 2006-08-02 | 2008-02-13 | Siemens Aktiengesellschaft | Thermal compensation arrangement in an injection valve |
Also Published As
Publication number | Publication date |
---|---|
EP2141346B1 (en) | 2011-01-19 |
DE602008004641D1 (en) | 2011-03-03 |
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