DE1751481A1 - Hydraulic valve lifter - Google Patents

Description

PATENTANWÄLTE 8902 augsburg-göggingen; the ^ 0.5.1968

v. Eidiendörff- Strasse 10

DR. ING. E. UEBAU unseen Dr.Lb/p Az. E 7o81

DIPLING. G. UEBAU ^{(please indicate in the case of backlog)} : ■

, HRZeichen 175148

Your message from

Eaton YaIe & Towne, Inc. 1oo Erieview Plaza, Cleveland, Ohio, USA

Hydraulic valve lifter.

The invention relates to hydraulic valve lifters in particular of the type in which oil is also upward is metered by the push rods to lubricate the valve timing.

The main field of application of the invention is lubrication ^

the valve control of internal combustion engines, at! ^ calibrations Valves arranged in the cylinder head are opened by assigned push rods and rocker arms, and hydraulic valves Tappets can be used between the camshaft and the ends of the pushrods. The purpose is that Supply of oil from the oil line or Ilauptö 1 supply, which is effected by the engine pump pressures to the tappets

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for the tappet lubrication and then additionally the separate one Metering of oil through the tappets for lubrication upwards through the shafts of the hollow pushrods to the rocker arms, which require adequate lubrication for a long service life.

In the past, it was common practice to pull the rocker arm arms from the engine lubricating oil pump through the tappets and tappets rods separate means to lubricate. However, development has then led to this separate oil supply device thereby avoiding the task of supplying lubricating oil was carried over onto the pushrods and the oil was moved up through the hollow pushrods.

The earlier hydraulic tappets had this dual function however, difficulties arose. In particular, this hydraulic ram either an excessive supply of lubricating oil to the rocker arms at high engine operating speeds with a corresponding Loss caused by the valve guides to the engine cylinders or they were unable to work satisfactorily to maintain the minimum requirement for oil supply at low speeds, if measures have been taken, to prevent excessive oil supply at high speeds.

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For example, in a known device 7 1 / 2.Mi *. utes after starting of the motor to the rocker arms ein.Hlfluß using CAH ZOI ¹ J 'oil of 27 ⁰ C (Sun ⁰ F) causes v / ground. Far, in this earlier execution, a check valve element remains up to an engine speed of about 160 o / min. essentially closed. These 'the fact numbers is clearly visible that it is in the earlier designs not possible to obtain satisfactory VJeise the I lindestbedarf upright on oil supply in niedricren speeds when' measures have been taken to prevent excessive intake at high speeds .

The main object of the invention is therefore to provide one improved hydraulic ram for use with ICippn ebelsclmiersystene.

The invention is also intended to provide an improved hydraulic Valve tappets for use in valve rocker arm lubrication systems be created, in which a new type of compulsory metering "is obtained - to correct oil supply meniren to the rocker arms arms over the entire operating speed range of the engine.

The invention makes a significant contribution to the Construction of hydraulic ram and lubricating oil metering devices through an improved, simplified, more accurate and

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Failure-free system in which non-return valves are avoided. In addition, the invention provides for the oil increase in the hydraulic tappets through the use of a new type of fixed oil with a constant flow rate, so that the oil flow is always proportionate to the engine's need for lubrication, depending on the operating speed of the same. There is also a resistance to clogging due to the relative rotation that takes place between the pan and the body of the pod. In addition, the invention has a high level of stability and service life, because the number of parts used has a high degree of stability. Ueni ^ e parts wear v. ^r at aterial for ease Ilerstellunn. In the following, the invention is described in more detail for a better understanding on the basis of exemplary embodiments, namely:

1 shows a view in axial section of a first embodiment an invention combined Device made of hydraulic ί-tappet and Cchnierölzumeßvorrichtun, ^, in which the piston and the Gtösselstanfren pan consist of one piece;

Fi.i.la a schenatic representation of the? .Ev; enunp of the canal 84 with bezupt at the anger 4P. and step 5o;

Fi.'j. 2 a side view, partly in ir, i axial section, a second embodiment of V. rfindim ^, polygamy

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the execution horn of Fig. 1 is similar in which However, the joint socket does not have the piston from one Piece consists;

Fig. 3 is a side view, partly in axial section, of a third embodiment of the invention, in which the The piston and the pushrod joint socket are separate elements and in which a part of the oil reservoir is formed in the joint socket, in contrast to the embodiment according to FIG. 2, in which the entire oil container is located in the piston;

FIG. 4 is a sectional view similar to FIG. 3, but which Bars according to the state of the art are formed on the joint socket and on the interior of the body and the piston in a relatively depressed position is shown, thereby showing the manner in which the length of the control web is shortened has been, through which in turn the flow to the valve control is accelerated in an undesirable manner, from which the problem solved by the invention can be seen will;

Fig. 5 is a view similar to Fig. 2, partially in elevation

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in axial section, of a ram according to the invention with a two-part piston and a joint socket, however, the (ilverteilunnsnut of the piston after below with reference to the (live distribution groove of the bore of the body is offset to a greater distribution to obtain the oil over the palm of the drill;

6 is a side view, partially broken away in the axial direction Section, a further embodiment of the invention, which also uses a two-part piston and a joint socket, with part of the (31 container chamber is arranged in the joint socket, as in the embodiment of FIG. 3, however Furthermore, a reversal of the invention is provided in that the metering web is of constant length is formed on the outer surface of the socket instead of being carried by the bore, as in the previous embodiments, and besides a sealing ring is used on the socket;

Fig. 7 is a side view, partly broken away in axial section, of another embodiment of the invention in which all of the incoming oil moves up to the constant length metering web and then into the

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Äolbenbehfliter means in the bottom surface of the joint socket provided! "anal;

Fig. Ο a view in section along the line 8-8 in FIs. 7;

Fiq. 9 a .Ansicht, partly in section, which shows a part λ of an internal combustion engine with an indunr * snewässen tappet.

In Fi ^. 1 designates generally the 2o erfindunrrs.itemässe hydraulic valve stem and C'lzunne ^ vorrichtun.r ^1;. The plunger 2o has an essentially cup-shaped isomer 22 with an annular side wall 24 which has a cylindrical outer surface 26. In -'litt el part of the cylindrical outer surface 26 a recessed rim receiving groove 28 is formed. M One end of the body 22 is closed by a transverse head 3o, while the other end 32 is open. During operation, the head is supported by a free crouch on a control shaft in a manner known per se in the case of the notorious designs.

The interior of the body 22 is designed as a stepped bore 54 which has its deepest diameter 36 at the open end has its next largest diameter 3 "length of the middle part

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and have the smallest diameter 40 at the head end. nine .Schulter 41 limits the downward movement of the piston 52. In ^{the> r} itte of nächstnröAten diameter 3 · ° - there is formed a Olverteilunpsnut 42 errenzunpen within the axial j ^ the iiusseren ülaufnahmenut 2 ?. is located. Through the side wall.

24 extends a radial oil supply channel 44, which the grooves

5S and 42 connects with each other. This system, made up of the receiving groove 28, the oil supply channel 44 and the oil distribution groove 42, forms the supply from a suitable oil supply channel, which is schematically enabled at 46. An oil pump and a sump of a type known per se supply the IM for the (Ilkanal 46.

At a distance from the inner (distribution groove 42 in the Bore 38 of the body 2 2 a Fimmelnut 48 is formed. This takes the lubricating oil for the Xipphebclnrmschmierunr as described in more detail below.

Between the oil distribution groove 42 and the Fammelnut 48 is a star so of fixed length provided its function is very important for the invention and initially follows the description of the movable control piston, which is generally designated by 52, is explained in more detail.

In the case of the Fip. 1 shown embodiment of the P.r-

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the piston 52 is in one piece and within the center part of the body 22 with the diameter 38 slidable. Within the largest diameter part 36 is a groove formed, in which a snap ring 37a is inserted, -der holds the piston 52 in its working position within the body 22. The piston 52 is cylindrical in shape and its outer surface has two carefully measured diameters. The head end diameter 54 has a tight fit with a clearance of about o, oo5 to o, oo76 mm (o, ooo2 to o, ooo3 ") less than diameter 38. This allows "downward licking" (leak-down) in more detail, as described below will.

The clearance between the fixed length web 50 is essential larger and is about 0.03o to 0.056 mm (0.02 to o, oo22 "). As you can see, this difference is in the Big about ten times bigger than the downward lick game. As a result this larger clearance can lubricate oil to the oil collecting groove 48 arrive in an appropriate manner. The upper socket diameter 56 is also of the same size as the diameter of the web So of a fixed length and is o, o3o to o, o56 mm (o, ool2 to o, oo22 ") less than that Diameter of the bore 38 of the body 22. This is to mention that the clearance between the diameter of the upper joint socket and the body can vary,

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The head end of the piston 52 has a shoulder 60 which is further stepped to form an annular valve seat 62 which surrounds a channel 64.

The head part of the piston 52 is with a hollow ßehälta: - chamber 66 provided, which is between the channel 64 and the oil inlet supply channel 44 extends. A radial Einfe let 68 is within the confines of a Ulaufnähmenut 7o is provided, which is formed around the outside of the piston. The container chamber 66 takes above the Channel 64 an oil supply for the supply of ram working oil on.

A pressure chamber 72 is provided between the head end of the piston 52 and the transverse head 3o of the body 22. A bowl-shaped, stamped metallic cold element 74 has a radial flange 76 at one end thereof which extends on the shoulder 60 of the piston 52 is held in support by means of a compression spring which is supported on the transverse head 3o. The holding element 74 is bent upward in the form of two spring spikes 80, which are a disk-shaped check valve element 8 press 2 against the annular seat 62. This acts as a check valve against an oil flow from the pressure chamber 72 back into the container chamber 66, while a free flow of oil through the channel 64 and can take place in the pressure chamber 72 as required

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is. Uic ■ Expensive thorns Co also limit the amount by which the disc-shaped ■ J'üclcscü.lacventi.lelenent. G2 in the üffnunrdas Ilanals ö4 can move. The check valve shown is shown for the purposes of description and only other types of non-return valves can also be provided.

as is well known; is with each valve stem stroke, which is caused by a Aufwrirts'jewepung of the hydraulic stem, -Ol in the pressure chamber 72 trapped by the fact that the disc-shaped jerk valve element "2 π & ίτοη the seat 62 'cebrp.cht and the piston 52 nit the body is bevreet 22 upward.! Jährend each such Kockenanhebe- and Vcntiloffnunpshubes occurs a small .'enjTe the trapped in the üruckkaniner 72 ( ^'1 is to the IColben around 52 from which leakage herein as "downward leakage" (leak -down) and is necessary to ensure that the Ilotortpellerventil comes fully seated on the subsequent return stroke ,! ', "enii this" downward licking "would not be and if one of the parts of the control linkage elongates as a result of the increase in the engine temperature, this would be greater For longer, keep the valve slightly lifted from its seat. This can burn the valves and cause the

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Run Ilotors.

After the valve has returned to its seat, the spring 78 keeps the piston 52 in contact with the lower end of the pushrod 58, as shown in Fig. 1, and the body 22 is held in contact with the cam surface so that a positive There is contact between the transverse head 3o and the 'cam surface, whereby any beating in the system is avoided. When the plunger 20 is back in contact with the base circle of the cam (not shown, but known per se), the piston 52 is removed from the body 22 by the spring 78 to compensate for the inward "downward leak" movement of the piston Valve lifting stroke moved out. This leads to a renewed expansion of the pressure chamber 72 and enables oil to flow past the disk-shaped check valve element 82, which is then opened, out of the container chamber 66.

The upper end or the joint socket of the piston 52 is provided with a transverse channel 84 which intersects an axial channel 86. The transverse channel 84 is always in at least partial overlap with the collecting groove 48 during operation of the hydraulic ram and is therefore of such a width that an uninterrupted overlap is obtained. The axial channel 86 opens at the base of a

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hemispherical socket 83, which is the hemispherical End of the hollow push rod 58 receives. The hollow push rod 58 is provided at its lower end with an opening 9o which is located above the axial channel 86.

During operation, while the tappet 2o-

reciprocated to open the associated engine valve and to close, and when full with oil from the pump pressure

the oil line (arrow 46) held container chamber 66 and ^

öaufnahmut 7o the game between the web So of constant

Length a careful and precise metering of oil to the bread

groove 48. From the groove 48 dts oil flows into the channel 84 and then up through channel 86 and further up through the center of the hollow push rod 58 for lubrication of the

Rocker arm. As a result of the type of web 5o of constant length * takes place

tin · ZIMestation of the lubricating oil proportional to the engine *? · *! «*! m on a substantially rectilinear basis. Therefore, the higher the speed of the engine, the greater the need for lubrication and the greater the amount of lubricating oil supplied. The length of the Zumeßsteges 5o and the game between the web 5o of constant length and the body 22 can experience a corresponding change for a particular engine, to ensure correct lubrication for the rocker arm in all operating *

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to get three numbers.

It should be mentioned here that the length and the area of the web 50 always remain constant. As can be seen from FIG. 1, in the upper position of the piston 52, the upper edge of the oil receiving groove 7o is brought into alignment with the lower edge of the web So or below it. Furthermore, the channel 84 is located above the level at which the maximum depression of the piston 52 would result in the channel 84 coming out of connection with the collecting groove 48.

FIG. 1 a shows the end positions which the channel 84 can enter , but with a mostly constant length being maintained.

In the upper position of the joint socket , the cantl 84 just overlaps the upper edge of the wall that forms the surface 41. In the eberea SUUu »t 4 * * joint fe» me, the oil flow takes place via the Ziineftsteg fo into the Sajwelnut 48 and then into the channel 84. In the lower position of the joint socket, the channel 84 just overlaps the lower edge of the viand delimiting the groove 48. Most of the oil is, as indicated by the arrows a in Fig.la, metered over the web 5o of constant length. Something Ül moves, as indicated by the salvation b, over a distance smaller than that

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Length of the web is 5o. However, this oil is insofar rather localized than the channel 84 a small part represents the circumference of the VJand forming the web 5o. Therefore W ill be a metering of essentially constant length obtained when the joint socket is in the lower position and the channel 84 in the position shown in FIG is. The positions of the channel 84 shown in FIG intended to represent the end points of the movement of the piston serve to measure the measurement through a web of constant To maintain lungs. It is not necessary for the piston to assume these end positions. It is just required that the connection idschen the channel 84 and courage was not interrupted during the movement of the socket will.

From the above it follows that the number of parts in comparison to the multipart units of the last M

IjQ years of the prior art has been substantially reduced. In fact, apart from the piston 52 and the housing 22, which form the plunger 20, no further moving parts are provided for the supply of lubricant to the joint socket end of the unit. This represents a substantial and meaningful advance in the state of the art and results in an oil metering of an accuracy which has not previously been achievable.

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The invention therefore represents a substantial improvement over it the well-known designs, in which an undersupply at lower engine speeds was the result of efforts, to prevent excessive runs at high speeds.

The embodiment shown in FIG. 2 is that in FIG. 1 shown is substantially similar, however, the piston 92 forms a two-part unit that allows for easier manufacture and higher commercial efficiency in manufacture.

The body 22 is the same and the snap ring 37a serves to keep the piston 92 in its operating position, especially Mention should be made of the maintenance of the flow rate of constant length on the inner surface 3Π of the body 22 limited by the Ulverteilungsnut 42 and the '! lsar.nelnut 4 8 v.ird.

The head section 94 of the piston 92 corresponds essentially to the head end of the piston 52 of the embodiment according to FIG. 1 and ends at the top at the dividing line 96. In this embodiment, working out the container chamber 9Π is much easier because the tool can be accessed from any linden tree Get access lann. The joint socket loo is similar to the joint socket end of the piston 92 of the embodiment according to FIG. 1. ¹ IeT Ii in If) Io2, however, is cut out along the floor of the joint socket loo,

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While in the embodiment according to FIG. 1, an inlet channel 68 is provided.

The embodiment of FIG. 2 also shows that the metering web of constant length can also be provided in modified embodiments of the invention. '

The rirkungsveise of the embodiment of FIG. 2 is the same as according to the embodiment of FIG. 1, what that Lubricating oil concerns, which is about the metering bridge 5ο of constant length moved, then the transverse channel 84 to the axial Channel 86 follows and then through the push rod 58 upwards flows.

The embodiment of the invention shown in FIG. 3 is similar to that shown in Fig. 2, since the piston with socket Io4 is formed by two parts. A part of the oil reservoir Io6 is in the joint socket Io8 formed by the embodiment according to FIG. 2, in the latter case the whole oil container is in the piston.

In the embodiment according to FIG. 3, there is also a metering bar So provided of constant length, which is attached to the bore 38 of the body 22 through the oil distribution groove 42 and the Oil collecting groove 48 is limited. The snap ring 37a is used to

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Piston ιχηά pan Io4 within the working endpoints in the Hole 38 to hold.

The I-piston and socket unit Io4 has an I-piston portion Ho on, that shown in Fig. 1 with regard to the details of the check valve essentially is similar. The piston section Ho ends at the top of the separator ™ line 112. The larger part 114 of the oil container I06 is provided as a straight bore 116 in the piston section Ho. In the embodiment of FIG. 3, the processing is due easy access for the tool to each end of the head portion Ho.

The socket I08 is similar to that shown in FIG. However, a smaller section 118 of the oil container I06 is formed in the joint socket I08 by a blind hole 119. Further || is the inlet 12o across the floor over the full length of the Cut out diameter, as in the embodiment according to Fig. 2.

The embodiment according to FIG. 3, however, goes a step further in that there is an oil collecting groove 122 around the joint socket I08 is provided around. The length and the area of the metering web 5o always remains during the operation of the ram constant.

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From the representation of the execution form after Fi ^. 3 results

decrease, that for the most part a 50 of constant length

Forms of the invention provided in various embodiments can be,

The I '.' Intrinsic to the embodiment of the invention according to rifi. 3 is the same as that of the embodiments according to FIp., 1 and 2 with regard to the lubricating oil flow over the tin bar 50 of constant length, which then follows the cue channel 124 to the axial channel SG and then its ^T. '. ^r e <r takes the push rod 58 upwards. The advantages of ease of workability are evident.

Fig. 4 does not show a prior art example, though Nevertheless, it is an embodiment according to the prior art in the light of the invention, the one accurate comparison of the differences between the state of the Technology and the inventive, qemässen ■ Zume.C.-st.e. {R of constant Length should allow.

The ivürpa: 126 is essentially the same with the exception that the family 1 and 48 of the embodiments according to Ti%. -3 we ^ dropped is. In this exemplary embodiment from the prior art, there is therefore no metering device of constant length. The i .'- lsamiiielnut 122 aii

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IC piston 128 comes in different positions with respect to the Illverteilungsnut 42 depending on the impact setting (sash setting) of the ram.

This results in a "variable length web" - like indicated by the label, based on the on-; stroke division.

4 therefore clearly shows the: ^T irksanity of the inventive web of constant length shown in FIGS. 1, 2 and 3 on the precise oil metering to the rocker arms via the hollow tie rods 50 under all operating conditions of the Ilotor.

By applying the invention is therefore at low Speeds an adequate amount of oil to lubricate the rocker arms obtained, whereby the underdelivery conditions, which in the known designs, in which I'ittel, for example Complicated check valves, used to prevent over-delivery at high speeds, are avoided will.

Furthermore, when applying the invention, higher Engine speeds the oil supply appropriate, but regulated to avoid an excess. Therefore, if the The rotor speeds increase, a corresponding linear increase

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of the oil flow. 35er according to the invention metering bridge of constant length , however, prevents flooding. It therefore brings about a significant improvement over the plunger according to FIG. 4.

The invention provides all of the improved features in a new but very simple way an adjustment by means of a web of constant length and at the same time the number of parts of the mechanism greatly reduced compared to the prior art.

The embodiment of the invention shown in FIG. 5 is similar to that shown in FIG. 2 with regard to the use of a two-part piston and joint socket unit 13o and the oil container 132 provided in the piston 134. The body 22 of the plunger is the same and the snap ring 37a holds the piston and joint socket unit 13o within its intended working limits in the body 22. Furthermore, the maintenance of the metering web 5o of constant surface area, which is on the inside 38 of the body 22 through the oil distribution groove, should be mentioned 42 and the collecting groove 48 is limited .

The lower end of the piston 134 is the same as the lower end of the embodiment of FIG. 1 with regard to the check valve mechanism. The head portion 134 ends at the top

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the dividing line 136. The oil container 132 is formed in the piston 134 in the form of a straight bore 138. In this embodiment, the hole 138 and the Pückschlagventilsitz 62 are easy to manufacture because the ^r ool good access to the piston 134 has?.

The socket 14o is similar to that shown in Fig. 2 and the inlet 142 extends over the underside thereof full length of the diameter. ·

As can be seen, the oil receiving groove 144 is provided at the upper end of the piston 134 so that it is offset downwardly with respect to the oil distribution groove 42 of the body. This results in a greater liquid mass distribution along the outside of the piston and joint socket unit 13o in the area surrounding the Ou inlet 142 for an improved supply both to the web 5o of constant length for lubrication upwards and for filling the container 132 via the Ou inlet 142 oil flow from the oil line 46 into the oil reservoir 132.

From this embodiment, it is also apparent again that the Zumeßsteg can find of constant length, in various embodiments of the invention use 5o.

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The mode of operation of this embodiment is the same as with the others for the supply of Schraieröl over the metering bridge 5o of constant length, then following the Ouerkanal .54 to the axial channel 86 and from there the pushrod 58 up to the rocker arm.

The embodiment according to Fi / r. 6 represents an inversion of the Invention represents »The Zuraeßsteg: 146 is of constant length on the outside of the bulb 152 and not on the inside surface or bore of the body 154 as in the preceding described embodiments »Per web 146 of constant The length is limited between an annular groove 153 and a hat ISo. As a result of the avoidance of a sealing ring 156 at the upper end of the socket 158, the upper end of the The socket can be ground to a single diameter instead of requiring two diameters, one for the Metering and one for a relative seal like this In certain cases when using the embodiments 1, 2, 3 and 5 be the case l: am.

In the embodiment according to FIG. 6, the oil » distribution groove 16o with its upper edge in alignment; with the upper limit of the oil supply channel 162, which in the body 154 is provided, furthermore, the body 154 is a courage 164, which is adjacent to the open .End for receiving the

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Sealing ring 156 is formed.

The function of the snap ring 37a is to keep the piston 152 within its working clearances in the bore 166 of the body to keep.

The piston and joint socket unit 152 is in two parts, which makes it easier to manufacture and is more economical same enables. It has a piston 168 on which is substantially similar to the piston of the embodiment of FIG. 1 with regard to the details of the check valve. The piston 168 ends at the top at the dividing line 17o. The large part 171 of the oil container 172 is in piston 168 by a straight line Bore 174 is formed. This gives an essential Ease of processing, as the sign is on each one Jmde of the piston 168 has access. The socket 158 is similar to that shown in Fig. 3 and the inlet 176 extends the full length of the diameter on the Underside of the socket, i.e. at the treai line 17o.

The groove 15o is around the upper end of the piston 168 formed around and ends at the top of the "transverse inlet channel 176, The inlet 176 therefore intersects the lower Üaufnahmutut 15o,

The smaller portion 178 of the oil reservoir 172 is in the

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G & enkpfanne 158 formed by a blind hole 18o.

It follows from this that the metering web 146 of constant Length at the joint socket 158 between the annular groove 183 and the unteioa groove 15o is formed.

Since in the lower end position of the piston and joint socket unit 15 2, as shown, the upper edge of the grooves 15o and 16o are in alignment, becomes the constant 'length of the metering web 146 is never reduced. V / hen the unity 15 2 is in the upper position, the metering web 146 always lies on an uninterrupted wall surface of the bore 166 opposite to.

In this embodiment of the invention, too, it results that the metering land 146 of constant length may find use in various embodiments of the invention.

The mode of operation of the embodiment according to FIG. 6 for the Metering of lubricating oil via metering web 146 of constant length, then following transverse channel 182 to axial channel 86 and then the pushrod 58 upwards is therefore the same. . ~

The embodiment according to FIGS. 7 and 8 has several of the features

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times e of the embodiments described above. Furthermore, the invention is reversed as in FIG. 6 insofar as the metering device 184 of constant length is formed between two hats 1 "6 and 188 which are spaced apart from one another and which are provided on the outer surface of the joint socket 242 .

Be the embodiment of FIGS. 7 and 3, the body has 192 has a cylindrical outer surface and an oil receiving groove 28 in its middle part. One end of the body is closed off by a head 3o, while the other end is open.

The inside of the body 192 forms a stepped bore, which has its largest diameter 194 at the top, its next largest diameter 196 along the middle part and its smallest diameter 198 below. One shoulder limited to 2oo the downward movement of the koien 19o.

In the middle of the part of medium diameter 196 there is an oil distribution groove 2o4, which lies within the axial limits of the outer oil receiving groove 28. A radial oil supply channel 2o8 connects the grooves 2o4 and 28 for receiving oil from the oil line 46.

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BinSpren ^ rin ^ 37a in a hat 21c cold the piston 19o inside dos body 192 drain the pressure of a compression spring 212 from below.

The piston 214 and the socket joint 242 are made of ζτ / ei parts which slide as a unit within the mean bore diameter 1D6. The piston 214 ends at the top at the dividing line 216. At the bottom, it is formed with a shoulder 210 which is stepped even further into a valve seat 22o, the latter forming a channel 222. The oil container chamber 224 is fully formed within the body shape 214 as a stepped bore 226, many of which are in communication with the channel 222. The oil container carriage 224 extends from the channel 222 to the dividing line 216. On the outside of the piston 214 there is a ( ^; Laufnahraenut 23o provided. Measurement groove 23o extends in such a way that it overlaps the oil distribution groove 2o4 at the bore 196;

Hissing of the underside of the piston 214 and the head 3o is a pressure chamber 232 is provided. A stamped metal cup-shaped retaining element 234, which is the Iialteelement of the embodiment shape of Fig. 1 is similar, has a radial flange 236 which rests against the shoulder 218 of the piston 214. The compression spring 212 is supported against the radial flange 236 and the head 3o to hold the Iialteelement 234 in place

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and further around. the piston 214 out of the body 192 outward 2u burdens. Spring pins 238 load the disc-shaped check valve element 24o against the annular seat 22o, i / o-. by a non-return valve mechanism as in the filling form according to FIG. 1 is obtained. . .

The socket 242 extends upward from the parting line 216. The inlet 244 is formed by intersecting channels 246 cut into the underside over the full length of the diameter of the socket 242, as shown in FIG. 3. A chamfer 248 around the base delimits the lower end of the metering web 1? 4 \ ^r on constant area. This gives a courage 188, as shown in Fig. 7 on the left.

The constant length metering land 104 extends from the chamfer 248 (oil receiving groove 244) to the annular ΡΪ-collecting groove 186. A transverse channel 252 communicates with the courage 186 and cuts an axial channel 254 which runs into the The bottom of the hemispherical pan 256 opens, which receives the lower end of a push rod.

The ram works for lifting purposes at the lower end of this Embodiment in the same way as described above.

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The equation for Sc! I3aierzv / ecl-: e is, however, used around the entire sub- side of the socket 242 through the intersecting Channels 246 (Fig. 8) and the chamfer 248 which the Groove ISG and thus the inlet 244 forms, carefully distributed.

The metering web 184 of constant length therefore causes a careful and precise metering of oil to the collecting groove 186, from which it flows via the channels 252 and 254 to the joint socket Λ 256 and then via the push rod to the rocker arm. As. As can be seen, the length of the metering web 184 always remains constant. Therefore, in FIG. 7 the piston 19o is "bottomed"("bottomed^1" and the chamfer 24 "(oil inlet 244) is located above the upper limit of the oil distribution groove 2o4

! '/ Ie are - in this embodiment all features ebr invention retained. Furthermore, a lowest possible Number of parts provided and the ease of workability and economy of manufacture are instant recognizable. In addition, there are no moving parts with the Except for the movement of the piston 214 with respect to the body 192 and the movement of the socket 242 with respect to the Body 192 provided.

Fig. 9 shows part of an engine with a cylinder block 258 in which cylinders 26o are provided. The cylinders

10981 S / 0669 _BM}

175U81

-3ο-

are closed off by a cylinder head 262 on the upper linden tree. A camshaft 264 with cams 266 is mounted within the cylinder block 258. Adjacent to each wock 266 a bore 268 is provided in the cylinder block 258, in v / elcher a hydraulic tappet according to the invention 2o slidable is arranged. The form fit between the rotatable Cam 266 and the plunger 2o cause it to move back and forth in the bore 268.

The cylinder block 258 is provided with a line syst. 259 which comprises the oil channel 46 in the figures described above. This ^ line system 259 is connected to the bores 268. As can be seen, the oil receiving groove 28 of the tappet 2o is connected to the oil line system 259. ' The plunger 2o takes up oil in the manner described above, for example via the radial channel 44 shown in FIG. 1.

A poppet valve 27o is arranged for reciprocating movement in the cylinder head 262 and is loaded into a closed position by a compression spring 272. The valve 27o has a frictional connection with the plunger 2o via a rocker arm 274 and a hollow push rod 58.

The particular rocker arm 274 shown is in the form of a substantially U-shaped pressed sheet metal part or

109815/0659

BAD OF | IG, n _al

Cussing part with downwardly directed end faces 276 and 278, which are in contact with the upper linden of the valve 27o and on the upper end of the push rod 58, respectively. The intermediate part is designed with an upwardly directed bearing surface 2Πο which is mounted on a bearing element 28 2 for pivoting movement, the latter being fastened to the cylinder "liorif 26.2" by means of a screw 284 and a nut 286. The bearing surface 2 "o has rotatable""means for receiving the bearing element 282. The end surface 2 ³ B is hemispherically concave for receiving the hemispherically convex upper end of the hollow pushrod 58. Both the upper end of the pushrod 58 and the end face 278 of the rocker arm are provided with small oil openings 28B and 29o. The push rod 58 has a guide seat in a guide 292 the task of rotating the rocker arm wa the axis of the screw-284 by the amount necessary to keep the rocker arm supported on the stem of the valve 27o.

The upper end of the hydraulic ram 2o takes the lower one End of the push rod 58 in the manner shown in FIG. 1.

Purpose: the 'invention is, the rocker arm 274 in its pivoting

10981 5/06 59 bad original

He movement on its storage 282 not to supply with metered lubricating oil. The manner in which the plunger metering 20 oil up through the hollow pushrod is rod 58 at all hotor speeds has been described above. The metered oil flies through the two openings 288 and 29o and therefore lubricates the bearing surface between the upper end of the push rod and the rear end 278 of the rocker arm 274 to lubricate these in their guide 292. The main part of the (ils, however, splashes over the tilting bellacer surface 28o and the ¹ bearing element 232. The greatest stress and therefore the greatest need to walk is at this point. The oil then runs over the outer end 276 of the rocker arm 274 and flows around this herira to lubricate the valve ■■ chaft-Kitrnhebel-bearing surface 276. Something Ul also flows the valve stem down to this lubricate in its guide "on yen ti Is anyway. aft by leaking excess-f ) l is lost in the cylinder 26a and is burned by the combustion.

Γ lit consideration of the existing conditions ^ i.e. the The requirement of adequate but not excessive lubrication is important in this context explain why the correct /! tight lubricating oil at all Speeds is necessary. First, at low engine speeds

zalilen das (Il lubricate all the bearing points mentioned, in order to prevent scuffing or chafing when the bearing friction forces occur, which are considerable. The mentioned Parts wear out quickly when they run dry at low or other speeds.

At high speeds, the amount of? J1 must not be fed in enough to flood the lever compartment. In DIE λ sem Kipphebelabteil natüüch Rüclclaufkanäle are provided for the oil, which direct the oil back down through the Ilotorblock 250 to the crankcase sump and the oil pump. However, these airflow channels have a limited flow capacity, so that flooding can occur, as mentioned above, oil running down the valve stem is lost during the combustion process. When flooding occurs, excess oil takes its place down the valve stem and into cylinder 26o, in which it is burned. In the case of the design according to the invention, this is made possible by the

Oil flow accuracy prevented.

The valve control shown in FIG. 9 is only given by way of example in order to demonstrate the mode of operation of the oil metering properties of the valve stem according to the invention. Other types of rocker arms and rocker arm joints can also be provided within the scope of the invention, as the

109815/0059

175H81

General purpose for the lubrication of valve controls is applicable.

Due to the precise metering of oil according to the invention receive lubrication at low speeds. It is also not just the right amount of oil at high speeds but also prevents flooding and thus loss. The invention therefore became a made a significant contribution to the state of the art, what s I through the accuracy of the mode of action and the simplicity of the structure can also be proven.

Within the scope of the invention, the metering web of constant length can be provided as a smooth surface and also as a tortuous path. In the foregoing, the Zumeßsteg of constant length has been described as a smooth surface, which operates against a corresponding smooth surface. According to the invention, the metering web of constant length and the surface against which it works can both form a tortuous path or just one of these parts. The winding path can be obtained by fine knurling or fine knurling. The person skilled in the art is readily familiar with other possibilities.

As described, the can from one another located at a distance

109815/0659

BATH ORIGINAL

175148t

Grooves »velcae - the metering web of constant length be ?! reu ζ be provided either on the bore of the body or on the outside of the piston. The formulation of the patent claim bears the term "means on the bore or on the outside of the ICoIbens, which is an additional benefit
of icons: area content. form "Reclmung, Inventunris ^ e- tM?> unifaPt this definition iiiites which are at a distance from one another, which can be parallel to one another
the lines be parallel and in the original direction of the outside of the Ivo, lbcns or T ^r ,, cbr Bohruno: extend * In particular, the hats can liejeii in. Plains, which to the axes of the Boiirun «: t.ina des I pistons are perpendicular _r

F a tentan claims:

BATH ORIGINAL

Claims (1)

Patent claims: ly hydraulic ram for back and forth erbcwe ^ un ^ nit an approximate piston that can be ^{moved back and forth in a supporting or bearing l; ohrun r} : marked by a ": leinla. ⁿ i in clic nohrunf; and a '"lauslaP through the iniloii, a liler.ent on the outside of the Ptüsscls with a J.a'zerflache in flow connection with the projection, means for guiding pressure to the liinlaf: and"' ittcl on the axinside of the piston or on L> ohrunr that ⁿ a Zurie stc ". λ ^ οη constant flow between the Iiinlc-i ^p and deio Aus la ^ Ie- "renzen. 2. plunger according to claim 1, characterized by a cup-shaped body C22) with an inner v.'and (26) which is closed at one end (3o) and open at the other end and an inner boiirunq (34) is open, a first channel (44, 162 or 2o ") which opens into the bore (34) for introducing oil into this, a piston (52, D2, Io4, 13o, 152 or IDo) which reciprocates in the bore 3irrrev. ^T eqlich is an element (34a,) which the piston 'within the Rolirün "hiilt, 109815/0659 bathroom original which piston has a seat end adjacent the open end of the body (22) and a head end adjacent the closed end of the body, an oil reservoir (C6C / 98, 114, 132, 172 or 224) within the piston; a second channel (68, Io2, 12o, 142, 176 or 216), which extends from the container to the outside / the piston, in order to guide oil from the bore (34) into the container, a third channel (64 or 222) which opens into the container through the head end of the piston, a member (8 2 or 24o) at the head end of the piston connected to the third channel and operable with the body to form a check valve from the container into the bore, a fourth channel (84, 36; 124, 86; 132, 86 or 252, 254) in the seat end of the piston for directing metered oil from the surface of the piston through the seat end and means (So, 146 or 184) at the bore or on the outside of the piston, which form a metering web of constant length between the first and fourth channels. 3. Venti1stössei according to claim 2, characterized in that the piston slides in the bore (34) in a precisely pasτ send ratio to form an ⁿ downward leak "around the -ölfluß JColben around between the head end and the first 1098 15/0659 BADORIOiNAL 175U81 Channel and an oil measurement of lower pressure between the first channel and the fourth channel. 4. Valve tappet according to claim 2 or 3, characterized in that the means (5o, 146 or 184), which form a metering web of constant length, are in the form of hats (48, 42; 48, 12o; 16o, 183; or 186, 2O4), have 'extend in the circumferential direction on either the bore (34) of the body (22) or on the outside of the piston. 5. Valve tappet according to claim 4, characterized in that the spaced apart grooves are parallel to one another and lie in planes which are perpendicular to the axes of the piston and the bore. 6. Valve tappet according to claim 4, characterized in that the grooves between the first channel and the fourth Channel are arranged. 7. Valve tappet according to claims 2-6, characterized thereby 109815/0659 BATH ORIGINAL draws, "that? - the play between the part of the outside of the piston from the second channel to the head end and the pipe socket is sufficient for a" downward leakage "of oil, while the play between the outside of the piston and the bore in the area of the end of the pipe of constant length of a size. is that- °) a. ^ lzunessuni of lower s.ruckv. is obtained. ■ ° .. ■ oil ram according to the 'claims - 7, characterized in that the "piston (92)" is formed by a head section (94) and a socket section (loo), the head section - (9.4) itself. zti-n extends Xopfende yon first Ilanal (44), the oil reservoir (Sn) portion -Iin head is formed and the third channel (64) in front. container extends to the outer side of the piston through the Konfende, the socket portion (loo) ! to vow first channel (44) extends zim Celenkpfannenende and the second channel (Io2) s in Pel -plannen from cut before ^ eseKen, and the Zuiae ^r vsteJT * ( 'Sun)' from constant length at:. ^ e is formed by spaced parallel channels (42, 4P) which run in the periphery of the direction and are arranged between the first channel (44) and aevx fourth channel (04, 06). 1098 1 5 / 0e59 BAD ORIGINAL -4ο- 9. Valve tappet according to claims 2-7, characterized {^ indicates that the piston (104) is formed by a head section (Ho) and a Pelenkpfannenabschnitt (Io8), the Kqfabschnitt (Ho) from the first "(anal (44) extends to the head end, the oil container (114) is partially formed in the head section and the third channel (64) extends from the container to the outside of the piston through the head end of the latter, the celenk socket section (Io8) extends from the first channel (44) to the joint socket end and forms a part of the container, which part connects with the part formed in the head section, the second channel (12o) is arranged in the Helenkpfanncnabschnitt, and the channel q of constant length by spaced apart parallel grooves (42 , 48) is formed, which run in the Unfan; ^T srichtun "of the bore and are arranged between the created channel (44 and the fourth channel (86, 122, 124). Io. Valve tappet according to claims 2-7, characterized in that that the Kolen (13o) through a head section (134) and a socket section (14o) is formed, the Kqfabschnitt (134) from the first channel (44) extends to the head soil, the plbehölter (132) in the head section is formed and the third channel (64) 109815/0659 «AD ORIGINAL from the container to the outside of the piston through its Head end extends, the socket section (14o) from the first channel (44) to the end of the joint socket, the , second channel (142) partially in the joint socket section and partially molded on the outside of the head portion and the metering web (5o) of constant length from one another spaced parallel grooves (42, 48) extending in the circumferential direction on the bore and disposed between the first channel (44) and the fourth channel (84, 86). 11. Valve tappet according to claims 2-7, characterized in that that the piston (152) is formed by a head section (168) and a joint socket section (158), \ tfelcher head portion (168) extends from the first channel (162) to the head end, the oil reservoir (172) partially is formed in the head portion and the third channel (64) extends from the container to the outside of the piston the head end extends, the acetabular portion (158) extending from the first channel (44) to the acetabular end and a part of the container which part communicates with the part formed in the head portion, • the second canal (15o, 176) partially in the acetabulum 109815/0659 cut, partly on the outside of the acetabulum section and is partially formed on the outside of the head portion and all channels are in communication stand, and the metering web (146) of constant length by a groove (1S3) is limited in the circumferential direction extends on the outside of the piston and is arranged between the first channel (162) and the fourth channel (86, 18 2) is. 12. Valve tappet according to claim 11, characterized in that a seal (156) between the bore and the outside of the piston and is arranged between the fourth channel and the mentioned end of the piston. 13. Valve tappet according to claims 2-7, characterized in that that the piston (19o) is formed by a head section (214) and a joint socket section (242), the head section (214) extends from the first channel (2o8) to the head end, the oil container (224) in the head section is formed and the second channel (244) extends from the container to the outside of the piston for connection with the first channel extends, the third channel (222) extends from the container to the outside of the piston through its Kqfende 10981S / 06BÖ extends, a shoulder (218) is provided in the bore adjacent the closed end of the body, and a hat (2o2) is provided in the bore adjacent the shoulder, the socket section extends from the first channel (208) to the socket and an upper surface at the open End of the hole -has and a bottom side, which -per? en anlieft the lower portion · and is exposed to your oil tank, a fifth ICanal in - is formed ^r -elenkpfannenäbschnitt in ¹⁷ ORFI of intersecting muting (246) extending across the full diameter at the bottom of Gelenknfannenabschnitts and with the first \ ussenmit (23o) are in communication, rich in dor Umfannsrichtung to the outside of the joint socket portion around passes, the Zumeßsten (154) of constant Lan <* e of the by the first outer groove (23o) and a second external groove (18 6) on the outside Joint socket section, which is located at a distance from the first outer groove, is limited, and the second; Iut is connected to the fourth ICanal (252, 254). 14. Valve tappet according to claim 13, characterized in that that the first ICanal through a connecting groove in a radial Ausflugunp; is formed in the hole and the second 109815/0659 JAD ORIGINAL ICanal through a connection groove in a radial curse around the outside of the body, which grooves communicate with each other. 15. Valve tappet according to claims 2-14, characterized in that that an or? an (74 or 212) between the piston and the closed end of the body is provided to move the piston out of the bore towards to the outside load, a first hat (2C) on the Outer surface of the piston is provided, a second / side Courage (48) at the interface between the body (22) and. the piston is provided and at least partially continuously the fourth channel overlaps during the reciprocating movement of the piston, a third channel (42) at the interface is provided between the body and the piston at a distance from the second gutter, and means a fluid from the first channel (44) to the third groove, the interface between the body and the piston between the second groove (48) and the third groove (42) forms an area of constant length to allow the flow to restrict and regulate the fluid from the first channel to the seat. 10981S / 065Ö * A0 ORIGINAL Read 11 e