EP3494291B1 - Hydraulic tappet - Google Patents
Hydraulic tappet Download PDFInfo
- Publication number
- EP3494291B1 EP3494291B1 EP17748575.2A EP17748575A EP3494291B1 EP 3494291 B1 EP3494291 B1 EP 3494291B1 EP 17748575 A EP17748575 A EP 17748575A EP 3494291 B1 EP3494291 B1 EP 3494291B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cavity
- plunger
- valve unit
- main body
- hydraulic tappet
- 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.)
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- 238000002485 combustion reaction Methods 0.000 claims description 12
- 238000007789 sealing Methods 0.000 claims description 6
- 230000010355 oscillation Effects 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 3
- 238000003860 storage Methods 0.000 claims description 3
- 238000004891 communication Methods 0.000 claims description 2
- 230000008901 benefit Effects 0.000 description 7
- 238000003754 machining Methods 0.000 description 4
- 230000009471 action 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
- 230000000694 effects Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- This invention relates to a hydraulic tappet.
- hydraulic tappet normally means a tappet equipped with a hydraulic telescopic device, connected to the lubricating circuit of the motor, which, with its travel, is able to automatically recover the clearance existing between the tappet and the valves actuated by it.
- the above-mentioned clearance is to be considered the result of multiple components such as, for example, machining tolerances, thermal expansion and wear of parts after their normal use.
- this invention relates to a hydraulic tappet for internal combustion engines comprising a rocker arm supporting a plunger designed to actuate a valve.
- It is basically plungers integrated in telescopic hydraulic means.
- hydraulic telescopic elements of known type are in the form of an assembled cartridge which comprises an outer jacket and an inner plunger engaged slidably with each other.
- the aim of this invention is provide a hydraulic tappet which is able to overcome the drawbacks of the prior art and which is at same time inexpensive to make, practical to operate and simple to install.
- the reference numeral 1 denotes in its entirety a hydraulic tappet for an internal combustion engine (not illustrated), made in accordance with this invention.
- the hydraulic tappet 1 comprises a rocker 2 and a device 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it.
- the rocker 2 has a central hole 4 designed to house a shaft, not illustrated, for oscillation of the rocker 2 about a respective axis A1 of oscillation.
- the rocker 2 has a first arm B1 and a second arm B2 positioned, respectively, on opposite sides relative to the central hole 4.
- the first arm B1 is designed to support a follower element, not illustrated, configured for engaging, in known manner, with a cam, which is also not illustrated, in a cam-follower mechanism.
- the second arm B2 has, at a distal end relative to the central hole 4, a through cavity 5 extending with axial symmetry.
- the through cavity 5 extending with axial symmetry has a central axis A2 skew relative to the above-mentioned axis A1 of oscillation of the rocker.
- the through cavity 5 has an inner wall 5a, a lower outlet 6 and an upper outlet 7, the latter being longitudinally opposite each other.
- the lower outlet 6 of the cavity 5 advantageously has a smaller diameter than that of the upper mouth 7.
- the inner wall 5a has a threaded portion F.
- the device 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it.
- the device 3 for recovering the clearance comprises a plunger 8 slidably engaged inside the above-mentioned cavity 5 and emerging from it partially at the relative lower outlet 6.
- the portion of the plunger 8 emerging from the lower outlet 6 of the cavity 5 supports an articulated member 9 for pushing the one or more valves, not illustrated, of the internal combustion engine.
- the above-mentioned pushing element 9 is advantageously configured, in known manner, in a bell-bottom fashion, and connected to the plunger 8 by means of an articulated ball joint S.
- the device 3 for recovering the clearance comprises, in the proximity of the above-mentioned upper mouth 7 of the cavity 5, a check valve unit 10 for adjusting a flow of oil circulating inside the above-mentioned cavity 5, a plunger 8 and a first helical spring M1 interposed between the above-mentioned valve unit 10 and the plunger 8.
- the valve unit 10 comprises a main body 11 having cylindrical dimensions which is located inside the cavity 5 closing the upper mouth 7.
- the main body 11 has an outer threaded wall 11a and is designed to engage by screwing with the above-mentioned threaded portion F of the wall 5a inside the cavity 5.
- the main body 11 is fixed inside the cavity 5 by friction connection through forced insertion (also known as pressing).
- the main body 11 protrudes above the cavity 5 so as to allow the screwing of a ring nut 13 for clamping on the relative outer threaded wall 11a.
- the ring nut 13 is defined by a locknut.
- the ring nut has an external thread designed to engage by screwing with the threaded portion F of the wall 5a of the cylindrical cavity 5.
- the tank 14 is advantageously cylindrical in shape.
- the tank 14 is covered by a specific cover 15 applied at the top, towards the outside.
- the cover 15 has the shape of a dome.
- a housing 16 is made on the main body 11 for a ball 17 for retaining the oil.
- the ball 17 is retained inside the housing 16 by a containment cage 16a of substantially known type.
- the valve unit 10 comprises a second helical spring M2 positioned at least partly inside the housing 16 and designed to apply a relative elastic action against the ball 17, for pushing the latter away from the tank.
- the plunger 8 has a lower portion 8a (with reference to the relative configuration with respect to the rocker 2) with an approximately hemispherical shape, to engage with the above-mentioned articulated pushing element 9 of the one or more or valves, not illustrated, of the internal combustion engine.
- the plunger 8 has an upper end portion 8b with diametric dimensions greater than the lower portion 8a.
- the plunger 8 also has an intermediate portion 8c interposed between the above-mentioned upper 8a and lower 8b portions.
- the intermediate 8c portion slidably engages with the lower outlet 6 of the cavity 5.
- the intermediate portion 8c has diametric dimensions less than the upper portion 8b.
- the plunger 8 supports an annular sealing element 18 mounted on it externally and designed to guarantee the dynamic seal between the plunger 8 and the inside wall 5a of the cavity 5 during the sliding of the plunger 8 along the axis A2.
- the plunger 8 is positioned with the elative upper portion 8b facing the main body 11 of the valve unit 10.
- the plunger 8 at the relative above-mentioned upper portion 8b, has inside it a cavity 19 for housing and guiding the above-mentioned first helical spring M1, the housing cavity 19 being shaped in the form of a cylindrical crown.
- housing cavity 19 in the shape of a cylindrical crown, is delimited, in the respective internal diameter, by a cylindrical pin 20 coaxial with the plunger 8.
- the cylindrical pin 20 is returned inside a hole 21 made in the plunger 8.
- the cylindrical pin 20 is made of plastic material.
- the plunger 8 and the main body 11 of the valve unit are mechanically separate, and physically separated along the direction of the axis A2.
- a high pressure chamber 22 between the plunger 8 and the main body 11 is defined a high pressure chamber 22, the chamber 22 having a variable volume as a function of the sliding of the plunger 8.
- the chamber 22 is defined by high pressure since the oil in it reaches maximum pressure values due to the compression action to which it is subjected in use.
- the above-mentioned high pressure chamber 22 has the shape of a disc. With reference to Figures 2 , 5 and 6 , the disc-shaped chamber 22 has diameter substantially equal to that of the plunger 8 at its above-mentioned upper end portion 8b facing the valve unit 10.
- connecting conduit 23 configured to place them in fluid communication with each other.
- the above-mentioned ball 17 is located along the above-mentioned connecting conduit 23 and is designed to obstruct it, under certain operating conditions, that is to say, when the pressure of the oil in the chamber 22 becomes such as to exceed the opposing elastic action exerted on the ball 17 by the second helical spring M2.
- the ball 17 is designed to close the connecting conduit 23 when the pressure in the high pressure chamber 22 is greater than that existing in the tank 14, the second spring helical M2 performing basically the function of preventing unwanted blockages of the ball 17 in its cavity 16.
- the spring M2 is designed to keep the ball 17 in a position such as not to obstruct the channel 23 when the pressure in the tank 14 is greater than or equal to the pressure in the high pressure cavity 22.
- the check valve unit 10 is of the type normally open.
- the spring M2 is configured in such a way as to delay the closing of the check valve unit 10, to allow the plunger 8 to move along the cavity 5 to compensate for any wear and thermal expansion.
- the tank 14 is formed integrated in the valve unit 10.
- This feature allows a modular and rapid assembly of the hydraulic tappet 1.
- the tank 14 is formed integrated in the main body 11 of the valve unit 10.
- Figures 5 and 6 illustrate, relative to the second embodiment of the tappet 1 equipped with clamping ring nut 13, two different positions adopted by the main body 11 of the valve unit 10.
- Figure 5 shows a condition of maximum screwing of the body 11 whilst Figure 6 shows a condition of only partial screwing of the body 11.
- the position of the main body 11 inside the cavity 5 can be adjusted through different degrees of screwing.
- minimising its volume means guaranteeing greater rigidity to the system in its entirety, taking into account the inevitable presence of air in the oil contained inside it (at least in certain operating phases of the motor) and the consequent compressibility.
- a contribution is also provided by the cylindrical pin 20, having, on the one hand, the function of guiding the first spring M1 during the movements of the plunger 8 and, on the other hand, the purpose of occupying the space inside the spring M1, preventing that this is occupied by an equivalent volume of oil.
- a first advantage provided by the tappet 1 according to this invention is due to the fact that the plunger 8 is slidable directly on the through cavity 5 made on the rocker, without requiring the presence of any containment jacket as in prior art solutions.
- the making of the through cavity 5 is therefore particularly inexpensive, as it is performed by boring fully in the rocker 2 and does not even require, as mentioned, a machining tolerance which is particularly precise, resulting in less costly machining that would be required in the absence of the annular sealing unit 18.
- Another advantage resulting from this invention is due to the limitation of the number of components of the tappet: sliding the plunger 8 directly on the inner wall 5a of the cavity 5 means that no additional jacket is in fact required.
- a greater surface of the high pressure chamber 22 implies small pressures on the components with the same force.
- a direct consequence of this circumstance is less stress on the components, such as, for example, the valve unit 10 or the annular sealing unit 18 which will also be subjected to less wear.
- the main body 11 of the valve unit is stationary relative to the rocker 2 which it supports, thus guaranteeing a greater overall rigidity of the system.
- a further advantage results from the construction of the intermediate portion 8c of the plunger 8 with diametric dimensions less than the upper portion 8b.
- This configuration allows, in effect, a smaller overall size of the rocker 2 at the lower outlet 6 whilst guaranteeing a considerable diametric size of the high pressure chamber 22. In this way, that is to say, with a large chamber 22, it is possible, with the same force acting on the plunger 8, to lower the pressure value reached inside it, thereby limiting the general mechanical stress of the system.
- Yet another advantage is due to the possibility of assembling the same in a modular fashion: inside the cavity 5 there are in fact basically inserted only two components, that is to say, the valve unit 10 and the plunger 8.
- the ease of assembly of the tappet according to the invention is also due to the fact that the valve unit 10 is physically separate from the plunger 8.
- the valve unit 10 is pre-assembled and advantageously its operation may also be tested before being mounted inside a specific tappet.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Lubricants (AREA)
Description
- This invention relates to a hydraulic tappet.
- The expression hydraulic tappet normally means a tappet equipped with a hydraulic telescopic device, connected to the lubricating circuit of the motor, which, with its travel, is able to automatically recover the clearance existing between the tappet and the valves actuated by it.
- The above-mentioned clearance is to be considered the result of multiple components such as, for example, machining tolerances, thermal expansion and wear of parts after their normal use.
- More specifically, this invention relates to a hydraulic tappet for internal combustion engines comprising a rocker arm supporting a plunger designed to actuate a valve.
- In the distribution systems, which control through the valves the fluid flow into and out from the cylinders of the internal combustion engine, prior art teaches the use of plungers mounted on the rockers to reduce the clearance between the rockers themselves and the valves.
- It is basically plungers integrated in telescopic hydraulic means.
- The patent documents
US 5,622,147 andUS 5,758,613 show two examples of these hydraulic telescopic elements. - These hydraulic telescopic elements of known type are in the form of an assembled cartridge which comprises an outer jacket and an inner plunger engaged slidably with each other.
- There is also a valve unit integral movement with the plunger.
- Another example of plunger mounted on the rocker arm is disclosed in patent document
GB 909707 A - These prior art solutions, even though operatively effective, have been seen to not be free from drawbacks.
- Especially in the assembly on a rocker, as a result of the dimensional limitations imposed by this architecture, these prior art solutions do not allow the making of large high pressure chambers, this implying the reaching of very high pressures with the same force transmitted to the valves.
- Moreover, the sliding between the jacket and the plunger, which must occur substantially in a sealed fashion, requires the production of a coupling between the two with extremely fine tolerances, thus implying high costs for making these elements.
- The aim of this invention is provide a hydraulic tappet which is able to overcome the drawbacks of the prior art and which is at same time inexpensive to make, practical to operate and simple to install.
- The technical features of the invention, with reference to the above aims, are clearly described in the appended claims and its advantages are more apparent from the detailed description which follows, with reference to the accompanying drawings which illustrate preferred, non-limiting example embodiments of it, and in which:
-
Figure 1 is a schematic top plan view of a preferred embodiment of the hydraulic tappet made according to this invention; -
Figure 2 is a cross-sectional view of the hydraulic tappet ofFigure 1 , according to the plane through the line II-II ofFigure 1 ; -
Figure 2a is an enlarged view, with some parts cut away in order to better illustrate others, of a detail ofFigure 2 ; -
Figures 3 and 4 are enlarged views of two respective details of the tappet ofFigure 2 ; -
Figures 5 and 6 are respective cross-sectional views, with some parts cut away, of a variant embodiment of the tappet of the preceding drawings, in two different operating configurations. - As illustrated in the accompanying drawings, the
reference numeral 1 denotes in its entirety a hydraulic tappet for an internal combustion engine (not illustrated), made in accordance with this invention. - The
hydraulic tappet 1 comprises arocker 2 and adevice 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it. - The
rocker 2 has acentral hole 4 designed to house a shaft, not illustrated, for oscillation of therocker 2 about a respective axis A1 of oscillation. - The
rocker 2 has a first arm B1 and a second arm B2 positioned, respectively, on opposite sides relative to thecentral hole 4. - The first arm B1 is designed to support a follower element, not illustrated, configured for engaging, in known manner, with a cam, which is also not illustrated, in a cam-follower mechanism.
- The second arm B2 has, at a distal end relative to the
central hole 4, a throughcavity 5 extending with axial symmetry. - The through
cavity 5 extending with axial symmetry has a central axis A2 skew relative to the above-mentioned axis A1 of oscillation of the rocker. - As illustrated in
Figure 2a , thethrough cavity 5 has aninner wall 5a, alower outlet 6 and an upper outlet 7, the latter being longitudinally opposite each other. - The
lower outlet 6 of thecavity 5 advantageously has a smaller diameter than that of the upper mouth 7. - At the upper outlet 7 the
inner wall 5a has a threaded portion F. - As clearly illustrated in
Figures 2 ,5 and 6 , inside the above-mentioned throughcavity 5 is housed thedevice 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it. - The
device 3 for recovering the clearance comprises aplunger 8 slidably engaged inside the above-mentionedcavity 5 and emerging from it partially at the relativelower outlet 6. - As illustrated in
Figures 2 and5 , the portion of theplunger 8 emerging from thelower outlet 6 of thecavity 5 supports an articulatedmember 9 for pushing the one or more valves, not illustrated, of the internal combustion engine. - As illustrated in
Figure 2 , the above-mentioned pushingelement 9 is advantageously configured, in known manner, in a bell-bottom fashion, and connected to theplunger 8 by means of an articulated ball joint S. - The
device 3 for recovering the clearance comprises, in the proximity of the above-mentioned upper mouth 7 of thecavity 5, acheck valve unit 10 for adjusting a flow of oil circulating inside the above-mentionedcavity 5, aplunger 8 and a first helical spring M1 interposed between the above-mentionedvalve unit 10 and theplunger 8. - The
valve unit 10 comprises amain body 11 having cylindrical dimensions which is located inside thecavity 5 closing the upper mouth 7. - The
main body 11 has an outer threadedwall 11a and is designed to engage by screwing with the above-mentioned threaded portion F of thewall 5a inside thecavity 5. - According to alternative embodiments of the invention, not illustrated, the
main body 11 is fixed inside thecavity 5 by friction connection through forced insertion (also known as pressing). - In the preferred embodiment illustrated in
Figure 1 , on the upper annular face of themain body 11 there are twoholes 12, which are diametrically opposite each other, designed to define respective gripping points of a tool for clamping themain body 11. - On the other hand, according to the variant embodiment illustrated in
Figures 5 and 6 , themain body 11 protrudes above thecavity 5 so as to allow the screwing of aring nut 13 for clamping on the relative outer threadedwall 11a. - Advantageously, with reference to
Figures 5 and 6 , thering nut 13 is defined by a locknut. - According to further alternative embodiments, not illustrated, the ring nut has an external thread designed to engage by screwing with the threaded portion F of the
wall 5a of thecylindrical cavity 5. - Inside the
main body 11 there is a space defining anoil storage tank 14. Thetank 14 is advantageously cylindrical in shape. - The
tank 14 is covered by aspecific cover 15 applied at the top, towards the outside. - In the preferred embodiments illustrated in the accompanying drawings, the
cover 15 has the shape of a dome. - In its lower part axially opposite the
cover 15, ahousing 16 is made on themain body 11 for aball 17 for retaining the oil. - The
ball 17 is retained inside thehousing 16 by acontainment cage 16a of substantially known type. - The
valve unit 10 comprises a second helical spring M2 positioned at least partly inside thehousing 16 and designed to apply a relative elastic action against theball 17, for pushing the latter away from the tank. - As illustrated in the accompanying drawings and in detail in
Figure 4 , theplunger 8 has alower portion 8a (with reference to the relative configuration with respect to the rocker 2) with an approximately hemispherical shape, to engage with the above-mentioned articulatedpushing element 9 of the one or more or valves, not illustrated, of the internal combustion engine. - The
plunger 8 has anupper end portion 8b with diametric dimensions greater than thelower portion 8a. - The
plunger 8 also has anintermediate portion 8c interposed between the above-mentioned upper 8a and lower 8b portions. - The intermediate 8c portion slidably engages with the
lower outlet 6 of thecavity 5. - The
intermediate portion 8c has diametric dimensions less than theupper portion 8b. - At the relative above-mentioned
upper portion 8b theplunger 8 supports anannular sealing element 18 mounted on it externally and designed to guarantee the dynamic seal between theplunger 8 and theinside wall 5a of thecavity 5 during the sliding of theplunger 8 along the axis A2. - As illustrated in
Figures 2 ,5 and 6 with reference to both the embodiments of this invention, inside thethrough cavity 5 theplunger 8 is positioned with the elativeupper portion 8b facing themain body 11 of thevalve unit 10. - The
plunger 8, at the relative above-mentionedupper portion 8b, has inside it acavity 19 for housing and guiding the above-mentioned first helical spring M1, thehousing cavity 19 being shaped in the form of a cylindrical crown. - In detail, the above-mentioned
housing cavity 19, in the shape of a cylindrical crown, is delimited, in the respective internal diameter, by acylindrical pin 20 coaxial with theplunger 8. - Advantageously, the
cylindrical pin 20 is returned inside ahole 21 made in theplunger 8. - Advantageously, the
cylindrical pin 20 is made of plastic material. - More specifically, the
plunger 8 and themain body 11 of the valve unit are mechanically separate, and physically separated along the direction of the axis A2. - In other words, between the
plunger 8 and themain body 11 is defined ahigh pressure chamber 22, thechamber 22 having a variable volume as a function of the sliding of theplunger 8. - The
chamber 22 is defined by high pressure since the oil in it reaches maximum pressure values due to the compression action to which it is subjected in use. - The above-mentioned
high pressure chamber 22 has the shape of a disc. With reference toFigures 2 ,5 and 6 , the disc-shapedchamber 22 has diameter substantially equal to that of theplunger 8 at its above-mentionedupper end portion 8b facing thevalve unit 10. - The variability of the volume of the
high pressure chamber 22, consequent to the sliding of the plunger along thecavity 5 according to the direction of the axis A2, advantageously allows, in a substantially known manner, the recovery of any clearance existing between thetappet 1 and the valves, not illustrated, of the internal combustion engine. - Between the
tank 14 and thehigh pressure chamber 22 there is a connectingconduit 23 configured to place them in fluid communication with each other. - The above-mentioned
ball 17 is located along the above-mentioned connectingconduit 23 and is designed to obstruct it, under certain operating conditions, that is to say, when the pressure of the oil in thechamber 22 becomes such as to exceed the opposing elastic action exerted on theball 17 by the second helical spring M2. - In other words, the
ball 17 is designed to close the connectingconduit 23 when the pressure in thehigh pressure chamber 22 is greater than that existing in thetank 14, the second spring helical M2 performing basically the function of preventing unwanted blockages of theball 17 in itscavity 16. - The spring M2 is designed to keep the
ball 17 in a position such as not to obstruct thechannel 23 when the pressure in thetank 14 is greater than or equal to the pressure in thehigh pressure cavity 22. - The
check valve unit 10 is of the type normally open. - The spring M2 is configured in such a way as to delay the closing of the
check valve unit 10, to allow theplunger 8 to move along thecavity 5 to compensate for any wear and thermal expansion. - Advantageously, the
tank 14 is formed integrated in thevalve unit 10. - This feature allows a modular and rapid assembly of the
hydraulic tappet 1. - More specifically, according to the preferred embodiments illustrated, the
tank 14 is formed integrated in themain body 11 of thevalve unit 10. - In use, during the normal operation of the internal combustion engine in which the
tappet 1 is integrated, oil is fed into thehigh pressure chamber 22; following this flow of oil, theplunger 8 is pushed to move away from thevalve unit 10 until annulling any clearances existing between the rocker and the other components of the internal combustion engine (valves, cams) with which it operates in conjunction. -
Figures 5 and 6 illustrate, relative to the second embodiment of thetappet 1 equipped with clampingring nut 13, two different positions adopted by themain body 11 of thevalve unit 10. - In particular,
Figure 5 shows a condition of maximum screwing of thebody 11 whilstFigure 6 shows a condition of only partial screwing of thebody 11. - In short, the position of the
main body 11 inside thecavity 5 can be adjusted through different degrees of screwing. - The possibility of varying the relative position of the
body 11 of the valve unit in the throughcavity 5 makes it possible, advantageously, on the one hand, to be able to adapt thetappet 1 to internal combustion engines characterised by different clearances and, on the other hand, to be able in any case to minimise the volume of thehigh pressure chamber 22. - Different clearances translate, in effect, into different excursions required for the
plunger 8 for their compensation and, if the average clearance present in an internal combustion engine for automobiles with average engine sizes is typically about 2.5 mm, the clearance normally present in large diesel engines for lorries is much higher. - With regard to the size of the high pressure chamber, minimising its volume means guaranteeing greater rigidity to the system in its entirety, taking into account the inevitable presence of air in the oil contained inside it (at least in certain operating phases of the motor) and the consequent compressibility.
- In other words, the smaller the volume of the high pressure chamber the smaller is the risk of triggering compressive phenomena of the elastic type. For this purpose, that is to say, limiting the volume of oil inside the
chamber 22, a contribution is also provided by thecylindrical pin 20, having, on the one hand, the function of guiding the first spring M1 during the movements of theplunger 8 and, on the other hand, the purpose of occupying the space inside the spring M1, preventing that this is occupied by an equivalent volume of oil. - The invention described above achieves the preset aims and brings important advantages.
- A first advantage provided by the
tappet 1 according to this invention is due to the fact that theplunger 8 is slidable directly on the throughcavity 5 made on the rocker, without requiring the presence of any containment jacket as in prior art solutions. - This circumstance, that is to say, the use of the
inner wall 5a of thecavity 5 as the sliding surface of theplunger 8, is permitted by the adoption of the dynamicannular sealing unit 18, thanks to which this sliding occurs in a sealed fashion. - Moreover, thanks to the presence of the
annular sealing unit 18, a particularly precise machining tolerance (which is costly to achieve) for theinner wall 5a of thecavity 5 is not even necessary, because theunit 18 can compensate for any imprecisions in the coupling with theplunger 8. - The making of the through
cavity 5 is therefore particularly inexpensive, as it is performed by boring fully in therocker 2 and does not even require, as mentioned, a machining tolerance which is particularly precise, resulting in less costly machining that would be required in the absence of theannular sealing unit 18. - Another advantage resulting from this invention is due to the limitation of the number of components of the tappet: sliding the
plunger 8 directly on theinner wall 5a of thecavity 5 means that no additional jacket is in fact required. - The absence of the jacket results in a further advantage: a greater surface area of the
high pressure chamber 22 which may in fact extending diametrically to theinner wall 5a of thecavity 5. - A greater surface of the
high pressure chamber 22 implies small pressures on the components with the same force. - In other words, since the surface of the
high pressure chamber 22 is greater, the force transmitted by therocker 2 to the valves will result in less pressure inside thechamber 22. - A direct consequence of this circumstance is less stress on the components, such as, for example, the
valve unit 10 or theannular sealing unit 18 which will also be subjected to less wear. - From another viewpoint, the circumstance described above also makes it possible, with an equal surface area of the high pressure chamber, to have overall dimensions less than there would be with a hydraulic telescopic unit of known type with an assembled cartridge (due to the presence, precisely, of the jacket outside the plunger). This reduced size translates into a smaller dimension required for the rocker on which the clearance recovery device is installed, with consequent reduction in weight and cost of the rocker, which may also be more easily integrated in an existing system.
- Moreover, advantageously, with the hydraulic tappet according to the invention, the
main body 11 of the valve unit is stationary relative to therocker 2 which it supports, thus guaranteeing a greater overall rigidity of the system. - A further advantage results from the construction of the
intermediate portion 8c of theplunger 8 with diametric dimensions less than theupper portion 8b. This configuration allows, in effect, a smaller overall size of therocker 2 at thelower outlet 6 whilst guaranteeing a considerable diametric size of thehigh pressure chamber 22. In this way, that is to say, with alarge chamber 22, it is possible, with the same force acting on theplunger 8, to lower the pressure value reached inside it, thereby limiting the general mechanical stress of the system. - Yet another advantage, again relative to limiting the number of components of the tappet, is due to the possibility of assembling the same in a modular fashion: inside the
cavity 5 there are in fact basically inserted only two components, that is to say, thevalve unit 10 and theplunger 8. The ease of assembly of the tappet according to the invention is also due to the fact that thevalve unit 10 is physically separate from theplunger 8. Moreover, thevalve unit 10 is pre-assembled and advantageously its operation may also be tested before being mounted inside a specific tappet.
Claims (12)
- A hydraulic tappet of an internal combustion engine, comprising:- a rocker (2) oscillating about a respective axis (A1) of oscillation to control the movement of at least one valve, the rocker (2) having, at a relative arm (B2), a through cavity (5) extending with axial symmetry having a central axis (A2) skew relative to the axis (A1) of oscillation, the cavity (5) having an inner wall (5a), a lower outlet (6) and an upper outlet (7) longitudinally opposite each other,- a plunger (8) slidably engaged in the cavity (5) and emerging from it partially at the relative lower outlet (6), the plunger (8) being configured to engage with a respective pushing element (9) of the at least one valve,- a check valve unit (10) designed to adjust a flow of oil circulating inside the cavity (5), the valve unit (10) comprising a main body (11) positioned inside the cavity (5) for closing the relative upper outlet (7),- an annular sealing unit (18) mounted outside the plunger (8) and designed to guarantee the dynamic seal between the plunger (8) and the inner wall (5a) of the cavity (5) during the sliding of the plunger (8), wherein the check valve unit (10) is of the normally open type.
- The hydraulic tappet according to claim 1, wherein the through cavity (5) has a portion (F) threaded internally made close to the upper outlet (7), characterised in that the main body (11) of the valve unit (10) has a cylindrical shape, is at least partly threaded externally and engages by screwing with the threaded portion (F) of the through cavity (5).
- The hydraulic tappet according to claim 2, characterised in that the position of the main body (11) of the valve unit (10) inside the cavity (5) can be adjusted by means of screwing.
- The hydraulic tappet according to claim 2 or 3, characterised in that it comprises a threaded ring nut (13) for fastening the main body (11) relative to the through cavity (5) of the rocker, the fastening ring nut (13) being designed to engage by screwing with one or the other of the main body (11) of the valve unit (10) and the threaded portion (F) of the through cavity (5).
- The hydraulic tappet according to any one of the preceding claims, wherein the plunger (8) and the main body (11) of the valve unit (10) are mechanically separate, characterised in that between the plunger (8) and the main body (11) there is a high pressure chamber (22), the chamber (22) having a variable volume as a function of the sliding of the plunger (8).
- The hydraulic tappet according to claim 4, characterised in that the high pressure chamber (22) has the shape of a disc.
- The hydraulic tappet according to claim 6, characterised in that the disc-shaped chamber (22) has diameter substantially equal to that of the plunger (8) at an upper end portion (8b) of the latter facing the valve unit (10).
- The hydraulic tappet according to claim 7, wherein the plunger (8) has an intermediate portion (8c) which is slidably engaged with the lower outlet (6) of the cavity (5), characterised in that the intermediate portion (8c) has a diametric size smaller than that of the upper portion (8b).
- The hydraulic tappet according to any one of claims 5 to 8, wherein there is a first spring (M1) interposed between the plunger (8) and the main body (11) of the valve unit (10), characterised in that the plunger (8) has inside a cavity (19) for housing the first spring (M1), the cavity (19) being shaped in the form of a cylindrical crown.
- The hydraulic tappet according to any of claims 5 to 9, characterised in that the valve unit (10) has an oil storage tank (14) formed in the relative main body (11) and a connecting conduit (23) configured in such a way as to put the tank (14) in fluid communication with the high pressure chamber (22).
- The hydraulic tappet according to claim 10, characterised in that the valve unit (10) has a retaining ball (17) interposed between the storage tank (14) and the high pressure chamber (22), the ball (17) being designed to close the connecting conduit (23) when the pressure in the chamber (22) is higher than that in the tank (14).
- An internal combustion engine comprising a plurality of hydraulic tappets according to any one of claims 1 to 11.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102016000083173A IT201600083173A1 (en) | 2016-08-05 | 2016-08-05 | HYDRAULIC PUNTER. |
PCT/IB2017/054642 WO2018025149A1 (en) | 2016-08-05 | 2017-07-31 | Hydraulic tappet |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3494291A1 EP3494291A1 (en) | 2019-06-12 |
EP3494291B1 true EP3494291B1 (en) | 2021-02-17 |
Family
ID=58159290
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17748575.2A Active EP3494291B1 (en) | 2016-08-05 | 2017-07-31 | Hydraulic tappet |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3494291B1 (en) |
CN (1) | CN109790764B (en) |
IT (1) | IT201600083173A1 (en) |
WO (1) | WO2018025149A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017008857A1 (en) * | 2015-07-16 | 2017-01-19 | Eaton Srl | An arrangement for a valve train assembly |
US11242774B2 (en) | 2019-09-20 | 2022-02-08 | Caterpillar Inc. | Rocker assembly with a hydraulic lash adjuster |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR752332A (en) * | 1932-04-04 | 1933-09-20 | Improvements to the valve control mechanism of internal combustion engines | |
DE1123865B (en) * | 1957-07-12 | 1962-02-15 | Renault | Valve lash adjuster on internal combustion engines |
GB909707A (en) * | 1958-02-05 | 1962-10-31 | Renault | Improvements in or relating to hydraulic devices for taking up axial play in valve gears, notably of internal combustion engines |
DE4422080A1 (en) * | 1994-06-24 | 1995-09-21 | Audi Ag | IC engine valve=rocker lever |
US5758613A (en) * | 1997-01-30 | 1998-06-02 | Eaton Corporation | Hydraulic lash adjuster and biased normally open check valve system therefor |
WO2005113942A1 (en) * | 2004-05-13 | 2005-12-01 | Schaeffler Kg | Hydraulic play compensation device |
JP2011157843A (en) * | 2010-01-29 | 2011-08-18 | Isuzu Motors Ltd | Solenoid valve used for valve operating characteristic changing device of engine |
JP5567856B2 (en) * | 2010-02-24 | 2014-08-06 | トヨタ自動車株式会社 | Sealed lash adjuster |
CN202140128U (en) * | 2011-02-25 | 2012-02-08 | 奚勇 | Integrated air-leakage type engine brake device |
CN103696822B (en) * | 2013-12-23 | 2016-04-06 | 宁波华液机器制造有限公司 | A kind of driver with hydraulic tappet |
-
2016
- 2016-08-05 IT IT102016000083173A patent/IT201600083173A1/en unknown
-
2017
- 2017-07-31 CN CN201780059810.6A patent/CN109790764B/en active Active
- 2017-07-31 WO PCT/IB2017/054642 patent/WO2018025149A1/en unknown
- 2017-07-31 EP EP17748575.2A patent/EP3494291B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
IT201600083173A1 (en) | 2018-02-05 |
CN109790764B (en) | 2021-04-30 |
EP3494291A1 (en) | 2019-06-12 |
CN109790764A (en) | 2019-05-21 |
WO2018025149A1 (en) | 2018-02-08 |
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