DE102006048845A1 - Hydraulic valve play compensation element for valve gear e.g. for vehicle internal combustion engine, has piston guided in piston housing and piston has low pressure chamber - Google Patents

Abstract

The hydraulic valve play compensation element has a piston (2) guided in a piston housing (4) and the piston has a low pressure chamber (3). A valve closure body (10) is connected with a flow guiding element (24), which adjusts the pressure generation. The valve closure body with a current conducting element is guided with a closed valve seat section (27) in to a medium pressure chamber (19). The control valve spring (11) is supported in the medium pressure chamber spaced in radial form the axial opening (7) and acts on the valve closure body through the flow guiding element with a force.

Description

Name of the invention

Field of the invention

The The invention relates to a hydraulic valve clearance compensation element for one Valve drive, for example a motor vehicle internal combustion engine, with a piston in a piston housing movably guided and is elastically supported against this, wherein the piston having a low pressure space, which via an axial opening in a piston bottom with one of the piston housing and the piston limited High-pressure chamber is connected, and with an effective between the pressure chambers Control valve, comprising a valve closing body, the one on the axial opening a valve seat surrounding the piston bottom underside can be applied in a sealing manner is and a valve closing body in the opening direction with a stroke limitation acting control valve spring, wherein the valve closing body over a Pressure build-up in the high pressure chamber during an axial collapse movement between the piston and the piston housing against the action of the control valve spring in the closing direction hydraulically can be acted upon.

Background of the invention

Such, for example from the WO 2006 010 413 A1 and the EP 1 298 287 A2 , known as Reverse Spring Hydraulic Lash adjusters (RSHVA) or Normally Open Lash Adjusters (NOLA) known lash adjusters differ from a conventional design in which the control valve spring acts on the valve closing body in the closing direction by a characteristic idle stroke, which must first be overcome before a Nockenbeaufschlagung the lash adjuster is passed to an actuated gas exchange valve.

In the conventional one Construction, the control valve spring is a closing element, which the valve closing body with a biasing force against the valve seat at the piston bottom bottom suppressed. The Control valve is thus when driving over of the associated Valve drive member through the cam of a rotating camshaft closed in cam base circle. At a following deflection by a cam lobe is a corresponding travel with a Force over the compensation element transferred directly to the gas exchange valve and this directly actuated, so open. Because the oil is incompressible in the high pressure chamber, the compensation element acts like a "rigid" actuator.

First at the subsequent axial expansion of piston and housing by the piston spring when the cam again reaches the base circle and the pressure in the high-pressure chamber sinks, opens the control valve against the control valve spring and there is a pressure equalization between the pressure chambers until the control valve spring closes the control valve again. there is due to the spring tension of the piston spring a valve clearance, which by thermal expansion, Manufacturing tolerances and wear of the transmission elements in a Nockenbeaufschlagung results on a gas exchange valve, independently balanced. In this construction, it can, especially during an incipient warm-up at still cold engine, to a so-called inflating the compensation element on the Control valve, so come to a negative valve clearance, which leads to high engine loads with increased wear.

These Disadvantages are avoided by RSHVAs. The control valve spring acts vice versa, so that the control valve ball or the closing body in the opening direction is applied, and thus the control valve in the cam base circle open is. To limit a Schließkörperhubes is a stroke limitation necessary. This is usually realized by a closing body cap, the the bottom of the piston is fixed and recesses for passing of the tax oil having.

at A RSHVA sets with the cam deflection initially a control oil flow from High-pressure chamber to low-pressure space, ie in the closing direction, wherein the compensating element collapses, so the piston and housing axially be pushed together. In this case, the closing body is flowed around by the control oil, whereby this hydrostatic and hydrodynamic against the action of the control valve spring is applied until a resultant axial force against him Valve seat presses and the control valve closes. The collapsing movement of the RSHVA manifests itself in the already mentioned characteristic idle stroke before the actual actuation of the gas exchange valve he follows. RSHVAs therefore act as "soft" control elements, which rule out a negative valve clearance.

Further Benefits offer the RSHVAs by the possibility of the idle stroke in the Include valve control. This can be the thermodynamic Potential of the internal combustion engine taking into account fuel consumption and pollutant emissions are used more effectively.

For this purpose, proposals have already been made by the applicant, for example in the not yet pre-published 10 2005 054 115.1 and 10 2005 043 947.0. In particular, by adjusting the speed dependent speed of the idle stroke and / or the consideration of the idle stroke in camshaft adjustments, the idle quality in Internal combustion engine to be improved.

When The comparatively sensitive operating behavior has a problem of the RSHVAs exposed. Research has shown that over the total engine oil temperature range (-40 ° C to + 160 ° C) an oil viscosity dependency of closing behavior the control valve occurs, which in particular in the warm-up phase the valve overlaps and thus affects the valve timing. The geometry and Arrangement of the control valve components (closing body, closing body stroke limitation, Valve seat and control valve spring) lead to a relatively heavy determinable hydrodynamics of the closing behavior of the control valve, so that hardly or only with considerable effort avoidable manufacturing and mounting differences to significant functional variations in RSHVAs lead can. Therefore, RSHVAs become permanent further developed with the aim of their advantages at the lowest possible To be able to use cost and design effort effectively, without the explained To accept disadvantages.

Examples of a simplification of the hydraulics and a compensation of the temperature dependence of the closing process are in the DE 10 2004 018 457 A1 and the WO 2006 010 413 A1 described.

The DE 10 2004 018 457 A1 shows a RSHVA with different closing body geometries and guide aids for guiding the respective closing body in a respective closing body cap. Therein, the valve closing body may be formed inter alia as a so-called needle, so as an elongated obturator, which is formed by a ball extended with a circular cylindrical spacer ball. Furthermore, the valve closing body may have a spherical cap as a sealing surface and / or a flattened cap bottom side end. As a guide, for example, Stufenför shaped recesses, cylindrical guide surfaces, centric guide lugs or Führungsseindenkungen and circular cylindrical pins may be provided on the mutually corresponding Schließkörper- and valve cap designs.

By the guiding means become particularly unfavorable Twists and lateral displacements of the valve closing body prevented. In this case, the valve closing body with guide play from a cylindrical parallel to the axis of the RSHVA Enclosed guide surface. This also causes the impinging oil flow is predominantly hydrostatic, so that the valve closing body like a piston is moved linearly.

In the from the WO 2006 010 413 A1 known RSHVA temperature-sensitive means, such as bimetal elements or memory metal elements are arranged in the low pressure chamber or in the axial opening of the piston, which changes the flowing from the high-pressure chamber to the low-pressure chamber oil flow with decreasing temperature. As a result, a comparison with the control oil temperature or engine oil temperature less sensitive closing time of the control valve and thus a substantial approximation of the idle stroke at different operating temperatures can be achieved.

deal the previous development stages of the RSHVAs essentially with the flow geometry dependence, the temperature dependence, the speed dependency and the manufacturing tolerance dependency the closing behavior of the Control valve or the consequent idle stroke, so is recently the desire came up, not only the speed-dependent Leerhubverlauf but also the absolute idle stroke depending on the application or user request to be able to adjust. To There are no indications in the known documents.

Object of the invention

Of the Invention has for its object to provide a RSHVA, the one possible viscosity- and manufacturing tolerant-independent Operating behavior shows, and at the same time a predetermined Leerhubeinstellung allows.

Summary of the invention

Of the The invention is based on the finding that with a simplified Control valve-closing mechanism, can be realized by means of a manufacturing tolerance-insensitive valve seat geometry, a largely viscosity-independent control valve hydraulics, Realizable by a predominantly hydrostatic acted upon valve needle-closing body, as well as a simplified Flow geometry, feasible by a streamlined displacement or arrangement of the control valve spring, in conjunction with high pressure chamber side arranged, the effective flow cross-section regulating means, a hydraulic valve clearance compensation element the Reverse Spring construction method can be provided its closing behavior with the help of the flow-conducting or flow-regulating Medium is adjustable, and its performance by the mentioned constructive activities at the same time largely viscous and manufacturing tolerance insensitive.

The invention is therefore based on a hydraulic valve clearance compensation element for a valve train, for example for a motor vehicle internal combustion engine, with a piston which is movably guided in a piston housing and elastically supported against this, in which the piston having a low-pressure space, which is connected via an axial opening in a piston head with a limited by the piston housing and the piston high-pressure chamber, and with an effective between these pressure chambers control valve, comprising a valve closing body, the voltage to a Axialöff surrounding on a piston bottom bottom valve seat tightly applied is, as well as with the valve closing body in the opening direction with a stroke limit acting control valve spring, the valve closing body is hydraulically acted upon by a pressure build-up in the high pressure chamber at an axial collapse between the piston and the piston housing against the action of the control valve spring in the closing direction.

to solution the task is also provided that the valve closing body as an elongated, piston-like body with a plate-shaped sealing surface, the corresponds with a correspondingly formed sealing surface of the valve seat, is formed, that the valve closing body with a radially projecting flow guide connected, over that the pressure build-up is adjustable, and that the valve closing body with the flow guide, at least with a valve seat near section, in one through the flow guide separated medium-pressure space is movably guided, wherein the control valve spring in the medium pressure space radially spaced from the axial opening and supports the valve closing body via the flow guide acted upon with a force.

By This structure succeeds, the closing behavior of a reverse-spring element largely independent of viscosity make and allow a Leerhubeinstellung. This is due to the valve closing body flow guide, preferably a flow baffle appropriate for that a separation of a high-pressure chamber, a medium-pressure chamber and Low pressure space ensures. The valve closing body forms with the flow baffle an axially movable unit, wherein the medium-pressure region substantially through the flow baffle is defined. The medium pressure space can be particularly simple as a be formed piston bottom underside, stepped extension of the axial opening. In this stepped piston recess the flow baffle is advantageous on the outside diameter guided.

There the flow baffle with the valve closing body a firmly linked entity whose leadership is guided by the leadership of the Strömungsleitbleches is fixed it between a conventional one Control valve ball and a corresponding ball valve seat to a unfavorable forced guidance come. This forced guidance presents relatively high demands on the manufacturing or assembly tolerances, to ensure proper functioning of the valve seat.

The execution of the valve closing body with a disc-shaped Sealing geometry leads In contrast to a ball valve seat not to a forced operation when Apply the sealing surfaces. This sealing geometry behaves in general and especially in conjunction with a leadership element such as the flow baffle less critical to manufacturing tolerances, which increases the reliability and saves costs in manufacturing.

Of the elongated valve closing body, a so called valve needle, in addition, by the control oil in contrast to a freely movable ball rather like a linear actuator moves, that primarily by a hydrostatic acting force component of the tax oil moves against the valve seat during the axial compression of the compensation element. investigations have shown that such a locking mechanism far less sensitive to the hardly avoidable temperature-induced viscosity changes of the engine oil or the control oil responds.

The Control valve spring supports axially in the medium pressure space, radially spaced from the axial opening and acts on the valve closing body via the flow guide according to the reverse-spring principle in the opening direction with a spring force. The attachment of the control valve spring as below and outlying, so below and radially spaced from the actual axial opening or piston bore arranged valve spring ensures that the spring or their Turns the flow transfer between the Druckräu men not hindered, which reduces fluctuations in performance and the Operational safety, in particular with regard to the closing time of the Control valve is further improved.

The flow guide causes a delayed High pressure build-up on actuation the lash adjuster, as through the valve seat near and thus low pressure space-adjacent medium-pressure space, the flow guide separates from the lower valve seat remote high-pressure chamber, in the axial collapse movement between piston and housing in the Medium pressure room first builds up a comparatively moderate pressure. This pressure buildup can be particularly effective through appropriately trained breakthroughs in the flow baffle be set.

In the simplest case, the flow guide may be formed as a perforated sheet metal disc, wherein the valve closing body is formed as a stepped circular cylinder, in which a tapered Stair extension forms the protruding into the medium-pressure chamber portion of the valve-closing body and the flow guide rests against the step of the stepped extension. Advantageously, the holes of the Strömungsleitblechs are radially within the spring coils of the control valve spring, so that the oil transfer is not affected by this, in particular not hindered.

The flow guide can also be made of other suitable materials, such as plastic or ceramics. There may also be other breakthrough geometries designed as holes or pressure-sensitive breakthroughs provided be, depending on the back pressure more or less open or react suddenly opening or closing.

The introduction the medium pressure in the control valve function allows a Setting the absolute idle stroke of the valve clearance compensation element. By a pre-determined, for example, in test series Determining attitude or configuration of breakthroughs, is throttled the high-pressure side pressure build-up such that a certain Leerhub is generated before the closing body applies to the valve seat, the control valve closes and becomes a rigid actuator. In particular, thus becomes a Leerhubeinstellung RSHVAs different piston diameter allows.

In principle, temperature-sensitive openings are also possible, which regulate the flow cross-section depending on the oil temperature and thus the oil viscosity, for example with the functional principle of the already mentioned above WO 2006 010 413 A1 known temperature-sensitive means, whereby a further reduction of the temperature dependence of the closing behavior and / or a targeted adjustment of this temperature dependence is made possible.

A simple and inexpensive Connection between the valve closing body and the flow guide may be formed as a press connection. For example, can the flow baffle be pressed onto the shoulder of the stepped valve needle. Of course they are Other types of connections or a one-piece design of closing body and flow guide possible.

to Setting the idle stroke can also be provided that on the valve closing body in the opening direction acting biasing force of the control valve spring via a correspondingly adapted Thickness of the flow guide and / or with the help of additional arranged in the medium-pressure space spacing means, for example a shim or washer, on which the control valve spring supported, is adjustable. For this purpose, for example, before mounting the existing Spring force measured and to adjust a correspondingly thick Washer mounted, with the additional shim useful is formed such that it does not obscure the openings of the Strömungsleitbleches.

Farther it can be provided that the valve closing body at least remove with a valve seat Section in a closing body cap is included, as the stroke limiter of the valve closing body and formed the flow guide Unit is effective.

The from the valve closing body and the flow baffle formed unit according to the invention, with the optionally adjusted by a washer valve spring, can by means of a conventional Closing body cap be fixed in a conventional manner on the piston head. The flow guide plate closes with open control valve preferably flush with a recess at the bottom of the piston, which serves as a support surface of a Cap flange of the closing body cap and serves to center them, the medium-pressure chamber. To the on this axial position of the flow guide previously set preload can actually achieve the Ventilschließkörperhub by a reprinting an advantageously plastically shaped cap bottom of the closing body cap in a final Installation step be tracked accordingly. For example this is a slightly inwardly arched cap base accordingly one.

The breakthroughs in the flow baffle can generally independent for aligning the closing body cap be positioned, with the influence of geometry and orientation the usual existing recesses in the closing body cap on the pressure build-up over the the tax oil acted upon the closing body, in relation to the breakthroughs, to take into account is.

Basically but instead of the closing body cap also a simple stop element, for example one on the piston bottom side pressed-in circlip, as stroke limitation possible, where the flow baffle supported on the stop.

Brief description of the drawings

The The invention will be described below with reference to the accompanying drawings Embodiments explained in more detail. In this shows

1 a section of a RSHVA with a valve closing body-Strömungsleitelement-Ein in a longitudinal section in the open control valve position, and

2 an enlarged section of the RSHVAs according to 1 with an additional washer.

Detailed description the drawings

This in 1 RSHVA shown is advantageous as a hydraulic ram 1 trained, as it is used as part of a valve train in internal combustion engines of motor vehicles to compensate for a valve clearance.

The pestle 1 has a cylindrical piston in a conventional manner 2 on that in a piston housing 4 is guided axially movable with a sealing play. A cylindrical recess in the interior of the piston 2 is a low-pressure room 3 designed as the oil reservoir of the compensation element 1 serves, which is supplied via an unillustrated oil supply with control oil or engine oil. The low pressure room 3 is over an axial opening 7 in a piston bottom 8th with a high pressure room 5 that by the piston 2 and the piston housing 4 limited, connected. piston 2 and piston housing 4 are supported against each other via a piston spring 6 between a piston bottom 18 and a caseback 22 of the piston housing 4 , which realizes the play compensation in the mechanical transmission chain between cam and gas exchange valve.

The axial piston bore 7 is high-pressure side of a reverse-spring control valve 9 dominated, coaxial and below the piston bore 7 at the bottom of the piston 18 of the piston crown 8th is arranged.

The control valve 9 has a valve closing body 10 on that in a closing body cap 12 , also known as a valve cap, is added. A cap ground 16 the closing body cap 12 serves as a stroke limiter of the valve closing body 10 , At least one recognizable in the right half of the drawing opening in the closing body cap 12 allows the passage of oil.

The closing body cap 12 is advantageous in the radial direction at least in the region of a collar-shaped cap flange 21 resiliently formed, so that these by means of Kappenflansches 21 in an inwardly tapered depression 20 in the piston bottom 8th can be clipped and thereby at the piston bottom bottom 18 is attached. At the same time the closing body cap 12 in the depression 20 with respect to the axial piston bore 7 radially centered. The piston spring 6 is supported on the control valve side on the cap flange 21 This additionally secures the stroke limitation of the control valve 9 ,

The valve closing body 10 is designed as a stepped cylindrical piston, hereinafter also referred to as a valve needle. The valve needle 10 has a valve seat side upper cylindrical portion 27 on to which a cap-side lower cylindrical section 28 connects with a larger diameter. The valve seat side section 27 juts into a medium-pressure room 19 , as a control valve-side stepped extension of the piston bore 7 is trained.

The valve seat side section 27 the valve needle 10 has at its end a plate-shaped sealing surface 13 on that with a flat sealing surface 14 one the piston bore 7 surrounding valve seat 15 corresponds. The cap-side section 28 the valve needle 10 is completely in the closing body cap 12 whose volume he approximately fills. It lies at the end with the control valve open 9 , as in 1 shown at the cap ground 16 on, causing a Schließkörperhub 17 corresponding opening gap between the valve seat 15 and the sealing plate 13 for oil transfer between the pressure chambers 3 and 5 is released.

At one through the sections 27 and 28 of different diameter formed step 29 the valve needle 10 is a flow guide 24 attached. The flow guide 24 is advantageously designed as a sheet steel disc, with a center hole 26 ( 2 ) on the upper closing body portion 27 , at the stage 29 fitting, is pressed on. In the flow baffle 24 are radially between the center hole 26 and the outer edge formed as holes breakthroughs 25 arranged. In 1 is a breakthrough in the left half of the drawing 25 indicated, with the center hole 26 connected is.

The flow baffle 24 forms with the stepped valve needle 10 According to the invention a firmly connected axially movable unit, the medium pressure space 19 from the rest of the high pressure room 5 spatially separated. The flow baffle 24 is at the outside diameter in the middle pressure space 19 guided with guide play, whereby at the same time the valve needle 10 centered and guided accordingly.

The construction unit 10 / 24 is from a control valve spring 11 (Reverse Spring) acted upon in the opening direction with a spring force. The advantageously designed as a helical compression spring control valve spring 11 rests in the middle pressure room 19 between the flow baffle 24 and a bearing surface formed by the frontal boundary of the medium-pressure space 23 from. Here is the diameter of the control valve spring 11 an inner diameter 30 of the medium-pressure space 19 adjusted so that on the one hand the control valve spring 11 at the radially outer edge of the Strömungsleitblechs 24 rests and the breakthroughs 25 lie radially within the spring diameter and on the other hand, the piston bore 7 is arranged radially within the spring diameter. The control valve spring 11 is thus also on the outside diameter in the medium pressure space 19 guided.

A bias of the control valve spring 11 is by an axial length 31 of the medium-pressure space 19 certainly. To adjust the valve spring force can be an additional shim 32 on the flow baffle 24 be placed, which is the available for the valve spring effective length of the medium-pressure space 19 shortened by its thickness and thus the bias of the control valve spring 11 increased accordingly. In the 2 is such a dial 32 in the medium-pressure room 19 shown.

The following is the function of the plunger 1 with regard to the mode of action of the medium-pressure valve circuit governing an idle stroke adjustment by attaching the flow-guiding element 24 to the valve closing body 10 explained in more detail:
The control valve 9 opens and closes during operation of the engine via an alternating high pressure build-up in the high-pressure chamber 5 or pressure equalization between the pressure chambers 3 and 5 the piston bore 7 , so that alternately a Nockenbeaufschlagung forwarded to the gas exchange valve or a valve clearance is compensated.

An actuation of the gas exchange valve is preceded by an idle stroke, by the closing operation of the control valve 9 is determined. When Nockenbeeaufschlagung the piston 2 and the piston housing 4 of the plunger 1 pushed together axially. It sets in the high pressure room 5 a pressure build-up, the valve closing body 10 charged, the control oil in the direction of low pressure space 3 the closing body 10 flows around. Due to the piston-like shape of the closing body 10 is the effective force on the control valve 9 essentially determined by a static hydraulic pressure of the control oil.

The axial collapse movement of the plunger 1 Expresses itself by the idle stroke, which extends until the closing of the control valve 9 by overcoming the biasing force of the control valve spring 11 continues with sufficient hydraulic pressure. The oil flow into the low-pressure space 3 is through the flow guide 24 throttled, so that the high pressure build-up is delayed and initially in the medium-pressure space 19 a range of mean oil pressure - between a low pressure in the oil reservoir and a high pressure in the high pressure chamber 5 below the flow guide 24 - arises. The breakthrough acts as a regulating agent 25 in the flow guide 24 , The result is an idle stroke, the size of the setting by the openings 25 in terms of their size, shape and / or number is adjustable.

1

tappet

2

piston

3

Low-pressure chamber

4

piston housing

5

High-pressure chamber

6

piston spring

7

axial opening

8th

piston crown

9

control valve

10

Valve closing body

11

Control valve spring

12

Closing body cap

13

sealing surface

14

sealing surface

15

valve seat

16

cap base

17

Schließkörperhub

18

Piston crown underside

19

Medium-pressure chamber

20

depression

21

cap flange

22

caseback

23

bearing surface

24

flow guide

25

breakthrough

26

center bore

27

section

28

section

29

step 30 Inner diameter

31

length 32 Shim, spacer

Claims (14)

Hydraulic valve clearance compensation element for a valve train, for example for a motor vehicle internal combustion engine, with a piston ( 2 ) housed in a piston housing ( 4 ) is movably guided and elastically supported against this, in which the piston ( 2 ) a low-pressure space ( 3 ), which via an axial opening ( 7 ) in a piston bottom ( 8th ) with one of the piston housing ( 4 ) and the piston ( 2 ) limited high-pressure space ( 5 ) and with one between these two pressure chambers ( 3 . 5 ) effective control valve ( 9 ), comprising a valve closing body ( 10 ), which at one the axial opening ( 7 ) on a piston bottom ( 18 ) surrounding valve seat ( 15 ) is sealingly applied, and with a valve closing body ( 10 ) in the opening direction with a stroke limitation acting control valve spring ( 11 ), where the valve closing body ( 10 ) via a pressure build-up in the high-pressure chamber ( 5 ) during an axial collapse movement between the piston ( 2 ) and the piston housing ( 4 ) against the action of the control valve spring ( 11 ) is hydraulically acted upon in the closing direction, characterized in that the valve closing body ( 10 ) as an elongated, piston-like body with a plate-shaped sealing surface ( 13 ), which with a correspondingly formed sealing surface ( 14 ) of the valve seat ( 15 ), is formed, that the valve closing body ( 10 ) with a radially projecting flow guide ( 24 ) is connected, via which the pressure build-up is adjustable, and that the valve closing body ( 10 ) with the flow guide ( 24 ), at least with a valve seat near section ( 27 ), in a through the flow guide ( 24 ) separate medium pressure space ( 19 ) is movably guided, wherein the control valve spring ( 11 ) in the medium-pressure space ( 19 ) radially spaced from the axial opening ( 7 ) and the valve closing body ( 10 ) via the flow guide ( 24 ) applied with a force. Hydraulic valve clearance compensation element according to claim 1, characterized in that the flow guide ( 24 ) at least one breakthrough ( 25 ), over which a delayed pressure build-up is adjustable. Hydraulic valve clearance compensation element according to claim 2, characterized in that the at least one breakthrough ( 25 ) radially within a diameter of the control valve spring ( 11 ) is positioned. Hydraulic valve clearance compensation element according to at least one of claims 1 to 3, characterized in that the flow guide ( 24 ) pressure-sensitive and / or temperature-sensitive means are assigned. Hydraulic valve clearance compensation element according to at least one of claims 1 to 4, characterized in that the flow guide ( 24 ) is formed as a perforated disc. Hydraulic valve clearance compensation element according to at least one of claims 1 to 5, characterized in that the medium-pressure space ( 19 ) as a piston bottom underside, stepped extension of the axial opening ( 7 ) is trained. Hydraulic valve clearance compensation element according to at least one of claims 1 to 6, characterized in that the valve closing body ( 10 ) is formed as a stepped circular cylinder, wherein a tapered stepped extension into the middle pressure space ( 19 ) protruding section ( 27 ) of the valve closing body ( 10 ) forms and the flow guide ( 24 ) at the stage ( 29 ) abuts the stepped extension. Hydraulic valve clearance compensation element according to at least one of claims 1 to 7, characterized in that the flow guide ( 24 ) on the valve closing body ( 10 ) is pressed. Hydraulic valve clearance compensation element according to at least one of claims 1 to 7, characterized in that the flow guide ( 24 ) with the valve closing body ( 10 ) is integrally connected. Hydraulic valve clearance compensation element according to at least one of claims 1 to 9, characterized in that a biasing force of the control valve spring ( 11 ) via a correspondingly adapted thickness of the flow guide element ( 24 ) is adjustable. Hydraulic valve clearance compensation element according to at least one of claims 1 to 10, characterized in that a biasing force of the control valve spring ( 11 ) with the help of additional in the medium-pressure space ( 19 ) arranged spacing means ( 32 ) on which the control valve spring ( 11 ) is supported, is adjustable. Hydraulic valve clearance compensation element according to claim 11, characterized in that a distance means ( 32 ) as at least one, on the flow guide ( 24 ) auflegbare shim is formed. Hydraulic valve clearance compensation element according to at least one of claims 1 to 12, characterized in that the valve closing body ( 10 ) at least with a valve seat remote section ( 28 ) in a closing body cap ( 12 ), which serves as a stroke limiter for the valve closing body ( 10 ) and the flow guide ( 24 ) is effective. Hydraulic valve clearance compensation element according to claim 13, characterized in that a Schließkörperhub ( 17 ) of the valve closing body ( 10 ) by pressing a plastically formed cap bottom ( 16 ) the closing body cap ( 12 ) is adjustable.