DE102017118236A1 - Hydraulic arrangement of a switchable valve drive - Google Patents

Abstract

The invention relates to a hydraulic arrangement (4) of a switchable valve drive, in which the valve lift of the gas exchange valves (EV1 - EV4, AV1 - AV4) is predetermined by cams of at least one camshaft and can be transferred to the gas exchange valves by means of assigned lift transmission elements, with two working pressure lines (28, 38 ), which are at least partially separated by a central web (54) separated from each other in a hollow shaft (50) or housing bore axially parallel to the camshaft, which are respectively connected via stubs with coupling elements of switchable Hubübertragungselemente associated gas exchange valves, each on the input side via a switching valve (34 , 44) alternately with a to a pressure-carrying main pressure line (18) connected switching pressure line (20, 22) or via a pressure relief valve (36, 46) with a non-pressurized return line (48) are connectable, and each on the output side via a throttle (30, 40 ) with egg ner connected to the main pressure line (18) Spülölleitung (24) are connected. It is provided that the throttles (30, 40) by a throttle body (56) are formed, which is inserted at the throttle end in the hollow shaft (50) or housing bore that the throttle body (56) in the installed state of two Connection (26) of the flushing oil line (24) in the respective working pressure line (28, 38) leading throttle channels (64, 72) together with the inner wall (52) of the hollow shaft (50) or housing bore encloses, and that this form-fitting secured against rotation and is axially fixed.

Description

The invention relates to a hydraulic arrangement of a switchable valve train of a combustion piston engine, wherein the valve lift of the gas exchange valves predetermined by cams at least one camshaft and mechanically transferable by means of associated Hubübertragungselemente to the gas exchange valves, with two working pressure lines, wherein the working pressure lines at least partially separated by a central web in a to the camshaft axis-parallel hollow shaft or housing bore are arranged, wherein the working pressure lines are respectively connected via stubs with coupling elements switchable Hubübertragungselemente associated gas exchange valves, the working pressure lines respectively on the input side via a switching valve alternately connected to a pressure-leading main pressure line switching pressure line or via a pressure relief valve with a non-pressurized Return line are connectable, and wherein the working d Return lines are connected on the output side via a throttle with a connected to the main pressure line Spülölleitung.

Switchable valve trains of internal combustion piston engines are known in various designs. Thus, valve trains of individual cylinders or groups of cylinders of a combustion piston engine can be deactivated by switching off the transferable valve lift and thus in conjunction with a shutdown of the fuel injection for the cylinders in question, the fuel consumption and the CO ₂ - and pollutant emissions of the internal combustion piston engine can be reduced in partial load operation. On the other hand, the lift characteristics transmittable by valve trains of intake and / or exhaust valves of a combustion piston engine may be changed by stroke switching and thus adjusted to the current operating state of the internal combustion engine depending on operating parameters such as engine speed and engine load, thereby increasing engine output and torque and the specific fuel consumption of the internal combustion piston engine can be reduced.

In turn-off valve drives usually two relatively displaceable or rotatable components of a switchable Hubübertragungselementes are provided, of which one component with the associated cam of a camshaft and the other component is in operative connection with the valve stem of the associated gas exchange valve. Both components can be coupled or decoupled via a coupling element, which is usually designed as a coupling pin. In the coupled state, the valve lift of the associated cam is transmitted to the respective gas exchange valve, in the decoupled state, however, not, so that the gas exchange valve then remains closed. The coupling pin is usually guided axially movable in a bore of a component and displaceable in a counterbore of the other component. By means of a spring element of the coupling pin is held in a rest position and moved by the application of a hydraulic actuating pressure against the restoring force of the spring element in an operating position and held there. In turn-off valve drives, the rest position of the coupling pin usually corresponds to the coupled state of the components of the Hubübertragungselementes and the operating position the decoupled state of the components. The turn-off Hubübertragungselementen may be switchable bucket tappets, roller tappet, rocker arm, drag lever or support elements.

At switchable valve drives at least two relatively displaceable or rotatable components of a switchable Hubübertragungselementes are provided, of which the one component with an associated first cam of a camshaft with a smaller valve lift and with the valve stem of the associated gas exchange valve and the other component with an associated second cam of Camshaft with larger valve lift is in a standby connection. Both components can be coupled or decoupled with one another via a coupling element which is usually designed as a coupling pin. In the decoupled state, the valve lift of the first cam is transmitted to the respective gas exchange valve, in the coupled state, however, the valve lift of the second cam is transmitted to the gas exchange valve. Again, the coupling pin is usually guided axially movable in a bore of a component and displaceable in a counterbore of the other component. By means of a spring element of the coupling pin is held in a rest position and moved by the application of a hydraulic actuating pressure against the restoring force of the spring element in an operating position and held there. When switchable valve drives the rest position of the coupling pin usually corresponds to the decoupled state of the components of the Hubübertragungselementes and the operating position of the coupled state of the components. The switchable Hubübertragungselementen are usually switchable bucket tappets, rocker arms or rocker arms.

In the case of a combustion piston engine, the stroke transmission to the gas exchange valves of a first group of cylinders, for example, in a four-cylinder in-line engine with the firing order 1-3-4-2, the Hubübertragung on the intake and exhaust valves of the second and third cylinder, to realize a cylinder deactivation and switched off the Hubübertragung on functionally identical gas exchange valves of a second group of cylinders, for example in the said in-line four-cylinder engine stroke transfer to the intake valves of all cylinders, to realize a Hubumschaltung to another valve is reversible, two separate working pressure lines are required.

These two working pressure lines are in each case via stubs with coupling elements switchable Hubübertragungselemente the associated gas exchange valves in combination. The working pressure lines are also connected on the input side via a switching valve alternately connected to a pressure-conducting main pressure line switching pressure line or via a pressure relief valve with a non-return line and connected on the output side via a throttle with a connected to the main pressure line Spülölleitung.

The restricted via the throttles connection of the working pressure lines with the purge oil line is used to flush the working pressure lines with lowered working pressure with a limited volume flow from the Spülölleitung in the direction of the return line and thus leakage due to replace escaping oil, thereby preventing the ingress of air and related malfunctions become.

With separate execution of the two working pressure lines in the form of largely parallel to the at least one camshaft in the cylinder head of the internal combustion piston engine arranged housing bores, these have a relatively small diameter and must therefore be manufactured with a relatively high production cost. In addition, such housing bores often can not be performed continuously straight due to the cramped conditions in the cylinder head, but extend over a plurality of transverse bores, which must be closed on the outside of the cylinder head by means of inserted plugs. To avoid such disadvantages, it has been proposed in various embodiments, two working pressure lines switchable Hubübertragungselemente a variable valve train at least partially separated by a central web to arrange or form in an axis parallel to the camshaft hollow shaft or housing bore.

So has already been in the DE 195 10 762 A1 a hydraulic arrangement of a switchable valve train proposed in which a plurality of working pressure lines switchable Hubübertragungselemente are arranged in a hollow shaft. The hollow shaft is provided as a bearing shaft for the pivotable mounting of towing or rocker arms of the valve train. In the version relevant here with two working pressure lines according to the local 1d the two working pressure lines are separated by a middle web inserted into the hollow shaft.

From the DE 195 35 498 A1 a similar hydraulic arrangement of a switchable valve train is known, in which a bearing shaft designed as a bearing shaft for the pivotable mounting of towing or rocker arms of the valve train bearing shaft is composed of several components to form two separate working pressure lines switchable Hubübertragungselemente. In the relevant here second embodiment of the bearing shaft according to the local there 4 to 6 this bearing shaft is composed of two semi-cylindrical shells and a central web arranged between them. The semi-cylindrical shells and the central web are materially connected to each other, for example, soldered or laser welded, and they include between each of the two half-shells and the central web each one of the two working pressure lines.

In the not pre-published EN 10 2016 208 470.4 In contrast, a hydraulic arrangement of a switchable valve train is proposed in which a plurality of working pressure lines switchable Hubübertragungselemente are arranged in a larger housing bore in the cylinder head of the internal combustion piston engine. In the relevant versions here with two working pressure lines according to the local 5 and 7 the working pressure lines are separated from each other either by a central web inserted into the housing bore or arranged in a provided with a central web tube, which is inserted into the housing bore.

Since the cited documents no information about the design and arrangement of the working pressure lines associated chokes can be seen, can be assumed by a separate arrangement of a throttle between each of the two working pressure lines and the Spülölleitung. To avoid the associated manufacturing and assembly of the invention, the object of the invention was to propose a simple and space-saving design and easy mountable design of the throttles for a hydraulic arrangement of a switchable valve train of the type mentioned. The chokes should also be designed so that they can have different throttle strengths for each of the two working pressure lines.

This object is achieved by a hydraulic system having the features of claim 1 solved. Advantageous developments are the subject of the dependent claims.

Accordingly, the invention is based on a hydraulic arrangement of a switchable valve drive of a combustion piston engine, in which the valve lift of the gas exchange valves is predetermined by cams of at least one camshaft and is mechanically transferable to the gas exchange valves by means of associated lift transmission elements. The hydraulic arrangement has two working pressure lines, which are arranged at least in sections by a central web separated from each other in an axis-parallel to the camshaft hollow shaft or housing bore. The working pressure lines are in each case via stubs with coupling elements switchable Hubübertragungselemente associated gas exchange valves in combination. In addition, the working pressure lines are each input side via a switching valve alternately connected to a connected to a pressurized main pressure line switching pressure line or via a pressure relief valve with a non-pressurized return line. In addition, the working pressure lines are each connected on the output side via a throttle with a connected to the main pressure line Spülölleitung.

To achieve a simple, space-saving and easy to assemble construction of the two throttles is provided according to a first embodiment that the two throttles are formed by a single cylindrical throttle body, which is inserted at the throttle end in the hollow shaft or housing bore, that the throttle body in built state two enclosing a connection of the flushing oil line in the respective working pressure line leading throttle channels together with the inner wall of the hollow shaft or housing bore, and that the throttle body is secured in the installed state positively against rotation and axially fixed.

The two throttle channels are preferably formed as two thread-shaped coiled outer grooves with the same pitch, which are arranged axially spaced from each other between an axially outer axial groove and an axially inner axial groove in the cylindrical outer wall of the throttle body.

The throttles formed in this way can, if required, be set relatively easily to different throttle intensities by means of cross-sections of different sizes and / or lengths of their throttle channels.

In a first embodiment of a form-locking rotation of the throttle body is secured by a disposed in its inner end wall Diagonalnut, engages in the assembled state, the adjacent end of the central web of the hollow shaft or housing bore, positively against rotation.

According to a second embodiment of a form-locking against rotation is provided that the throttle body is secured by two diagonally opposite in its cylindrical outer wall axial securing grooves, in the installed state in each case a radial web on the inner wall of the hollow shaft or housing bore, positively locked against rotation.

Thus, the two throttle channels are not affected by the axial securing grooves of the rotation is preferably provided that the securing grooves circumferentially offset from the outer and inner Axialnuten the throttle channels are arranged, and that the coiled outer grooves of the throttle channels are formed radially deeper than the latter in the region of the securing grooves ,

For their simplified manufacture, the radial webs on the inner wall of the hollow shaft or housing bore are preferably formed by the removal or omission of a central portion of the central web as leftover residual webs of the central web.

According to a first embodiment of an axial fixation of the throttle body, a hollow screw is provided, which is screwed in the assembled state in the throttle end of the hollow shaft or housing bore provided in this case with an internal thread and with its annular inner end wall on the outer end wall of the throttle body and with her Screw head rests against the throttle-side edge of the hollow shaft or housing bore.

Thus, the two throttle channels of the throttle body are not affected by the inner end wall of the hollow screw, the outer axial grooves of the throttle body in this case preferably in the installed state via a arranged between these in the outer end wall of the throttle body Diagonalnut fluidly connected to the central bore of the hollow screw.

For combined anti-rotation and axial fixation of the throttle body it is provided with at least two bending elastic tabs, which are arranged diagonally opposite and axially outwardly disposed on the outer edge of the outer end wall of the throttle body, and which in the mounted state, each with a radial projection in corresponding recesses in the Inner wall of the hollow shaft or housing bore engage.

To simplify the production of the recesses, it is preferably provided that the radial projections on the lugs of the throttle body are cylindrical and the associated recesses in the inner wall of the hollow shaft or housing bore are formed as radial, cylindrical bores.

With the mentioned features of the first embodiment of the throttles, a correspondingly designed throttle body for more than two working pressure lines can be formed, which are at least partially separated by radial webs separated from each other in an axis parallel to the camshaft hollow shaft or housing bore. In three working pressure lines, the radial webs are arranged in a star shape offset by 120 ° in the hollow shaft or housing bore and three throttle channels are arranged or formed on the throttle body. In four working pressure lines, the radial webs are arranged in a star shape offset by 90 ° in the hollow shaft or housing bore and four throttle channels arranged or formed on the throttle body.

The invention also encompasses a second embodiment of a hydraulic arrangement of a switchable valve drive of a combustion piston engine, in which the valve lift of the gas exchange valves is predetermined by cams of at least one camshaft and mechanically transferable to the gas exchange valves by means of associated lift transmission elements. This hydraulic arrangement also has two working pressure lines, which are at least partially arranged or formed separated from each other by a central web in a hollow shaft or housing bore that is parallel to the axis of the camshaft. These working pressure lines are just as in the first embodiment in each case via stubs with coupling elements switchable Hubübertragungselemente associated gas exchange valves in combination. In addition, the working pressure lines are each connected on the input side via a switching valve alternately connected to a pressure-leading main pressure line switching pressure line or a pressure relief valve with a non-return return line, and the working pressure lines are each connected on the output side via a throttle with a connected to the main pressure line flushing oil line.

To achieve the object is provided in this variant that the two throttles are each formed by a semi-cylindrical throttle body, said throttle body at the throttle end of the hollow shaft or housing bore in each case form-fitting in one of the interstices between the inner wall and the central web of the hollow shaft or housing bore are inserted, that the two throttle body in the installed state each enclosing a connection of the flushing oil line in the respective working pressure line throttle channel together with the inner wall of the hollow shaft or housing bore, and that the throttle body in the installed state are positively fixed axially and / or non-positively.

Due to the positive engagement of the two throttle body in the associated spaces of the hollow shaft or housing bore no separate rotation is required in this embodiment of the throttles.

The throttle channels are each preferably designed as a thread-like wound outer groove, which are each arranged between an axially outer axial groove and an axially inner axial groove in the semi-cylindrical outer wall of the respective throttle body.

The throttles formed in this way can, if required, be adjusted to different throttle intensities by means of different gradients of the wound outer grooves of their throttle channels and / or by different sized cross sections and / or lengths of their throttle channels.

To their axial fixation, the throttle body preferably axially on the outside each have a stop collar, which rests in the mounted state on the throttle-side edge of the hollow shaft or housing bore. In addition, the throttle body axially inwardly adjacent to the stop collar each have a cylindrical Übermaßbund with which they are pressed in the assembled state in the respective space between the inner wall and the central web of the hollow shaft or housing bore.

With the aforementioned features of the second embodiment of the throttles and more than two correspondingly shaped throttle body can be formed for more than two working pressure lines, which are at least partially separated by radial webs in an axis parallel to the camshaft hollow shaft or housing bore. In three working pressure lines, the radial webs are arranged in a star shape offset by 120 ° in the hollow shaft or housing bore and the throttle body each formed third cylindrical and positively inserted into one of the spaces between the outer wall and two radial webs of the hollow shaft or housing bore. In four working pressure lines, the radial webs are arranged in a star shape offset by 90 ° in the hollow shaft or housing bore and the throttle body each quarter cylindrically formed and positively inserted into one of the spaces between the outer wall and two radial webs of the hollow shaft or housing bore.

• 1 eine erfindungsgemäße erste Ausführungsvariante einer zweikanaligen Drossel einer Hydraulikanordnung eines schaltbaren Ventiltriebs und eine erste Ausführungsform einer formschlüssigen Verdrehsicherung der Drossel in einer teilweise aufgeschnittenen perspektivischen Ansicht,
• 1a die zweikanalige Drossel und deren Verdrehsicherung gemäß 1 in einer perspektivischen Teilansicht,
• 2 eine zweite Ausführungsform einer formschlüssigen Verdrehsicherung einer Drossel ähnlich der von 1 in einer teilweise aufgeschnittenen perspektivischen Ansicht,
• 2a die Drossel und die Verdrehsicherung gemäß 2 in einer perspektivischen Teilansicht,
• 3 eine erste Ausführungsform einer formschlüssigen Axialfixierung der Drossel gemäß 1 und 1a in einer teilweise aufgeschnittenen perspektivischen Ansicht,
• 3a die Drossel und die Axialfixierung gemäß 3 in einer perspektivischen Teilansicht,
• 4 eine weitere Ausführungsform einer kombinierten formschlüssigen Verdrehsicherung und Axialfixierung der Drossel gemäß 1 in einem Längsmittelschnitt,
• 4a die Drossel und die kombinierte Ausführung der Verdrehsicherung und Axialfixierung gemäß 4 in einer perspektivischen Teilansicht,
• 5 eine erfindungsgemäße zweite Ausführungsvariante einer zweikanaligen, zwei Drosselkörper aufweisenden Drossel einer Hydraulikanordnung eines schaltbaren Ventiltriebs in einer aufgeschnittenen perspektivischen Ansicht, und
• 5a die Drossel gemäß 5 in einer perspektivischen Teilansicht,
• 6 eine Hydraulikanordnung eines schaltbaren Ventiltriebs zur Anwendung der erfindungsgemäßen Drosseln gemäß den 1 bis 5a in einer schematischen Darstellung.

To further illustrate the invention, the description is accompanied by a drawing with exemplary embodiments. In this shows

• 1 1 shows a first variant of a dual-channel throttle according to the invention of a hydraulic arrangement of a switchable valve drive and a first embodiment of a form-locking rotation of the throttle in a partially cut-away perspective view,
• 1a the two-channel choke and its anti-rotation according to 1 in a perspective partial view,
• 2 a second embodiment of a positive rotation of a throttle similar to that of 1 in a partially cutaway perspective view,
• 2a the throttle and the anti-rotation device according to 2 in a perspective partial view,
• 3 a first embodiment of a positive axial fixation of the throttle according to 1 and 1a in a partially cutaway perspective view,
• 3a the throttle and the axial fixation according to 3 in a perspective partial view,
• 4 a further embodiment of a combined positive rotation and axial fixation of the throttle according to 1 in a longitudinal middle section,
• 4a the throttle and the combined version of the anti-rotation and axial fixation according to 4 in a perspective partial view,
• 5 a second embodiment of a dual-channel, two throttle body having throttle a hydraulic arrangement of a switchable valve train in a cutaway perspective view, and
• 5a the throttle according to 5 in a perspective partial view,
• 6 a hydraulic arrangement of a switchable valve train for the application of the throttles according to the invention according to the 1 to 5a in a schematic representation.

In the schematic representation of 6 is a hydraulic system 4 a non-illustrated switchable valve train of a combustion piston engine 2 pictured, the four cylinders arranged in series Z1 . Z2 . Z3 . Z4 and one inlet valve each EV1 . EV2 . EV3 . EV4 and an exhaust valve AV1 . AV2 . AV3 . AV4 per cylinder. The valve lift of the gas exchange valves EV1 - EV4 . AV1 - AV4 is predetermined by cams of at least one camshaft and mechanically transferable by means of associated Hubübertragungselemente to these gas exchange valves. The valve lift of the intake and exhaust valves EV2 . EV3 . AV2 . AV3 of the second and third cylinders Z2 . Z3 is for the realization of a cylinder deactivation by means of hydraulically switchable Hubübertragungselemente switched off. The valve lift of the intake valves EV1 - EV4 all cylinders Z1 - Z4 is to switch a Hubumschaltung between two cams with different lifting heights and Hubverläufen switchable. The Hubabschaltung and Hubumschaltung the gas exchange valves takes place in a conventional manner by a coupling element not shown in detail, which is hydraulically displaceable against the restoring force of a spring element from a coupling position or in a coupling position.

The hydraulic system 4 includes an oil pump drivable by the internal combustion engine 8th , by means of engine oil from an oil sump or reservoir 6 over an oil filter 10 and an oil cooler 12 into a main pressure line 18 is eligible. In front of the oil filter 10 one branches into the oil sump 6 return return line 14 from, in a trained as a check valve pressure relief valve 16 is arranged. Through the pressure relief valve 16 will be in the main pressure line 18 applied main pressure limited to a maximum pressure, thereby avoiding overloading and damage to connected loads and oil lines. To the main pressure line 18 are two switching pressure lines 20 . 22 and a flushing oil line 24 connected.

The measures provided for Hubabschaltung coupling elements of the intake valves EV2 . EV3 and the exhaust valves, AV2 . AV3 of the second and third cylinders Z2 . Z3 are on stub lines not further described with a first working pressure line 28 in connection. This working pressure line 28 is the input side via a trained as a 3/2-way magnetic switching valve first switching valve 34 alternately with the first switching pressure line 20 or via a designed as a check valve pressure relief valve 36 with one in the oil sump 6 recirculating return line 48 connectable. The pressure relief valve 36 can in the switching valve 34 be integrated and with this a valve unit 32 form. Through the pressure relief valve 36 will be in the first working pressure line 28 applied working pressure is limited to a minimum pressure, whereby a complete idling of the working pressure line 28 and prevents air from entering it.

With lowered working pressure in the first working pressure line 28 who joined in his in 6 pictured idle position of the assigned switching valve 34 is set, the working pressure line 28 Due to leakage escaping engine oil from the flushing oil line 24 via an output side arranged on this throttle 30 . 30 ' fed. At increased working pressure in the first working pressure line 28 which is opposite to the figure in 6 switched switching valve 34 adjusts, the coupling elements of the inlet and outlet valves EV2 . EV3 . AV2 . AV3 of the second and third cylinders Z2 . Z3 so hydraulically displaced or rotated, that the stroke transmission between the associated cam of the at least one camshaft and the respective gas exchange valves EV2 . EV3 . AV2 . AV3 is interrupted, causing the gas exchange valves EV2 . EV3 . AV2 . AV3 remain closed and the cylinders concerned Z2 , Z3 are switched off in connection with a shutdown of their fuel supply.

The measures provided for Hubumschaltung coupling elements of the intake valves EV1 - EV4 all four cylinders Z1 - Z4 are not further described stub lines with a second working pressure line 38 in connection. This working pressure line 38 On the input side via a trained as a 3/2-way solenoid valve second switching valve 44 alternately with the second switching pressure line 22 or via a pressure relief valve 46 with the in the oil sump 6 recirculating return line 48 connectable. The pressure relief valve 46 can in the switching valve 44 be integrated and with this a valve unit 42 form.

Through the pressure relief valve 46 is the in the second working pressure line 38 applied working pressure is limited to a minimum pressure, whereby a complete idling of the working pressure line 38 and prevents air from entering it. With lowered working pressure in the second working pressure line 38 who joined in his in 6 illustrated rest position of the associated switching valve 44 is set, the working pressure line 38 Due to leakage escaping engine oil from the flushing oil line 24 via an output side arranged on this throttle 40 . 40 ' fed. At increased working pressure in the second working pressure line 38 which is opposite to the figure in 6 switched switching valve 44 adjusts the coupling elements of the intake valves EV1 - EV4 all four cylinders Z1 - Z4 so hydraulically shifted or twisted that the stroke transmission to the intake valves EV1 - EV4 is switched by first associated cam of the at least one camshaft to second cam of the camshaft, whereby the lifting height and the stroke of the intake valves EV1 - EV4 to changed operating conditions of the internal combustion piston engine 2 are adjusted.

The two working pressure lines 28 . 38 are adjacent to the chokes 30 . 30 ' . 40 . 40 ' through a central pier 54 separated in a to the at least one camshaft axis-parallel hollow shaft 50 arranged. The following are based on the 1 to 5a two variants of the chokes 30 . 40 ; 30 ' . 40 ' and several embodiments of form-locking anti-rotation and positive and / or non-positive Axialfixierungen the throttles 30 . 40 ; 30 ' . 40 ' explained in more detail.

In the in the 1 and 1a pictured first embodiment of the two throttles 30 . 40 These are through a single cylindrical, two-channel throttle body 56 with an axially outer end wall 58 , a cylindrical outer wall 60 and an axially inner end wall 62 formed in the throttle-side end of the hollow shaft 50 is used. The throttle body 56 closes with its outer wall 60 and the inner wall 52 the hollow shaft 50 two from one connection 26 the flushing oil line 24 in the respective working pressure line 28 . 38 leading throttle channels 64 . 72 one. The two throttle channels 64 . 72 are as two thread-shaped coiled outer grooves 68 . 76 formed with the same pitch, the axially spaced from each other between an axially outer axial groove 66 . 74 and an axially inner axial groove 70 . 78 in the cylindrical outer wall 60 of the throttle body 56 are arranged. When installed, the throttle body 56 positively secured against rotation. For this purpose, the throttle body 56 one in his inner end wall 62 arranged diagonal groove 80 in, in the assembled state, the adjacent end of the central web 54 the hollow shaft 50 intervenes.

In the 2 and 2a is an alternative second embodiment of a positive rotation of the throttle body 56 displayed. The throttle body 56 now has two diagonally opposite in its cylindrical outer wall 60 trained axial securing grooves 82 . 84 in, in the installed state in each case a radial web 86 . 88 on the inner wall 52 the hollow shaft 50 intervenes. So that the two throttle channels 64 . 72 through the safety grooves 82 . 84 the rotation are not affected, these are Sicherungsuten 82 . 84 circumferentially offset to the outer and inner axial grooves 66 . 70 ; 74 . 78 the throttle channels 64 . 72 arranged, and the winding Außuten 68 . 76 the throttle channels 64 . 72 are in the range of safety grooves 82 . 84 radially recessed executed. For their simplified production are the radial webs 86 . 88 on the inner wall 52 the hollow shaft 50 by removing or omitting a central portion of the central web 54 as a leftover remainder of the Mittelstegs 54 educated.

In a first embodiment of a positive axial fixation of the throttle body 56 according to the 3 and 3a is a hollow screw 90 provided, one with an external thread 94 provided threaded shaft 92 , one screw head 96 and a central hole 98 having. When assembled, the banjo bolt is 90 in the throttle-side end in this case with an internal thread 102 provided hollow shaft 50 screwed in and lies with its annular inner end wall 100 on the axially outer end wall 58 of the throttle body 56 and with her screw head 96 at the throttle-side edge of the hollow shaft 50 at. So that the two throttle channels 64 . 72 of the dual-channel throttle body 56 through the inner end wall 100 the hollow screw 90 are not impaired in their effectiveness, are the outer axial grooves 66 . 74 of the throttle body 56 when installed, one between them in the outer end wall 58 of the throttle body 56 arranged diagonal groove 104 with the central hole 98 the hollow screw 90 connected.

In the 4 and 4a is an alternative to the above-described embodiments for positive rotation and axial fixation of the two-channel Droselkörpers 56 displayed. For this purpose, the throttle body 56 with two bending elastic tabs 106 . 110 provided, the diagonally opposite and axially and radially outwardly directed at the outer edge of the outer end wall 58 of the throttle body 56 are formed. When assembled, these tabs grip 106 . 110 each with a radial projection 108 . 112 in assigned recesses 114 . 116 in the inner wall 52 the hollow shaft 50 one.

To simplify the production of the recesses 114 . 116 and the assembly of the throttle body 56 are the radial projections 108 . 112 at the tabs 106 . 110 of the throttle body 56 cylindrically and axially bevelled inwardly. Thus, the recesses 114 . 116 in the inner wall 52 the hollow shaft 50 are designed as cylindrical, radial bores, and the radial projections 108 . 112 the tabs 106 . 110 can be during the axial insertion of the throttle body 56 in the hollow shaft 50 Do not get caught before reaching the set position.

In the in the 5 and 5a illustrated second embodiment of the two throttles 30 ' . 40 ' These are each by a semi-cylindrical throttle body 118 . 128 each with a radially outer stop collar 120 . 130 , an axially inwardly adjacent to this semi-cylindrical oversize collar 122 . 132 , a subsequent semi-cylindrical outer wall 124 . 134 and an axially inner end wall 126 . 136 educated. These two semi-cylindrical throttle bodies 118 . 128 are at the throttle end of the hollow shaft 50 each form-fitting in one of the two spaces between the inner wall 52 and the central pier 54 the hollow shaft 50 are used.

When installed, the throttle bodies close 118 . 128 one each from the port 26 the flushing oil line 24 in the respective working pressure line 28 . 38 leading throttle channel 138 . 146 with the inner wall 52 the hollow shaft 50 one. The throttle channels 138 . 146 are each as a thread-like wound outer groove 142 . 150 formed, each between an axially outer axial groove 140 . 148 and an axially inner radial groove 144 . 152 in the semi-cylindrical outer wall 124 . 134 the respective throttle body 118 . 128 are arranged.

Due to the positive engagement of the two throttle body 118 . 128 in the interstices of the hollow shaft 50 is in this second embodiment no special anti-rotation required. For their positive and non-positive axial fixation, the two throttle body 118 . 128 in the mounted state, each with its oversize collar 122 . 132 in the associated space between the inner wall 52 as well as the Mittelsteg 54 the hollow shaft 50 pressed in and lie with their respective stop collar 120 . 130 at the throttle-side edge of the hollow shaft 50 axially.

LIST OF REFERENCE NUMBERS

2

Combustion piston engine

4

hydraulic arrangement

6

Oil sump, storage tank

8th

oil pump

10

oil filter

12

oil cooler

14

Return line

16

Pressure relief valve, check valve

18

Main pressure line

20

First switching pressure line

22

Second switching pressure line

24

Spülölleitung

26

Connection of flushing oil line 24

28

First working pressure line

30, 30 '

First throttle

32

First valve unit

34

First switching valve

36

Pressure relief valve, check valve

38

Second working pressure line

40, 40 '

Second throttle

42

Second valve unit

44

Second switching valve

46

Pressure relief valve, check valve

48

Return line

50

hollow shaft

52

Inner wall of the hollow shaft

54

Central web of the hollow shaft

56

throttle body

58

Axial outer end wall of the throttle body

60

Cylindrical outer wall

62

Axial inner end wall of the throttle body

64

First throttle channel

66

External axial groove

68

Tortuous outer groove

70

Inner axial groove

72

Second throttle channel

74

External axial groove

76

Tortuous outer groove

78

Inner axial groove

80

diagonal groove

82

First axial safety groove

84

Second axial safety groove

86

Radial bar, remaining bar from Mittelsteg 54

88

Radial bar, remaining bar from Mittelsteg 54

90

Hohlschraube

92

Threaded shaft of the banjo bolt

94

External thread of the banjo bolt

96

Screw head of the banjo bolt

98

Central bore in the banjo bolt

100

Inner end wall

102

inner thread

104

diagonal groove

106

First tab

108

Radial advantage

110

Second tab

112

Radial advantage

114

Recess, bore

116

Recess, bore

118

First throttle body

120

Stop collar of the first throttle body

122

Oversize collar of the first throttle body

124

Semicylindrical outer wall of the first throttle body

126

Inner end wall of the first throttle body

128

Second throttle body

130

Stop collar of the second throttle body

132

Oversize collar of the second throttle body

134

Semicylindrical outer wall of the second throttle body

136

Inner end wall of the second throttle body

138

Throttling channel in the first throttle body

140

Axial outer axial groove

142

Tortuous outer groove

144

Axially inner radial groove

146

Throttling channel in the second throttle body

148

Axial outer axial groove

150

Tortuous outer groove

152

Axially inner radial groove

AV1

Exhaust valve of cylinder Z1

AV2

Exhaust valve of cylinder Z2

AV3

Exhaust valve of cylinder Z3

AV4

Exhaust valve of cylinder Z4

EV1

Intake valve of cylinder Z1

EV2

Intake valve of cylinder Z2

EV3

Intake valve of cylinder Z3

EV4

Intake valve of cylinder Z4

Z1

First cylinder of the combustion piston engine

Z2

Second cylinder of the combustion piston engine

Z3

Third cylinder of the combustion piston engine

Z4

Fourth cylinder of the combustion piston engine

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19510762 A1 [0009]
• DE 19535498 A1 [0010]
• DE 102016208470 [0011]

Claims (10)

Hydraulic arrangement (4) of a switchable valve drive of a internal combustion piston engine, in which the valve lift of the gas exchange valves (EV1, EV2, EV3, EV4, AV1, AV2, AV3, AV4) is predetermined by cams of at least one camshaft and by means of assigned stroke transmission elements mechanically to the gas exchange valves (EV1, EV1). EV4, AV1 - AV4) is transferable, with two working pressure lines (28, 38), wherein the working pressure lines (28, 38) at least partially by a central web (54) separated from each other in a to the camshaft axis parallel hollow shaft (50) or housing bore are arranged , wherein the working pressure lines (28, 38) in each case via stubs with coupling elements of switchable Hubübertragungselemente associated gas exchange valves (EV2, EV3, AV2, AV3, EV1 - EV4) are in communication, the working pressure lines (28, 38) respectively on the input side via a switching valve (34 , 44) alternately with a connected to a pressure-carrying main pressure line (18) Sc supply pressure line (20, 22) or via a pressure limiting valve (36, 46) with a non-pressurized return line (48) are connectable, and wherein the working pressure lines (28, 38) each output side via a throttle (30, 40; 30 ', 40') are connected to a flushing oil line (24) connected to the main pressure line (18), characterized in that the two throttles (30, 40; 30 ', 40') are formed by a single cylindrical throttle body (56) , which is inserted in the hollow shaft (50) or housing bore at the throttle end, that the throttle body (56) in the installed state two throttle channels (28, 38) leading from a connection (26) of the Spülölleitung (24) in the respective working pressure line ( 64, 72) together with the inner wall (52) of the hollow shaft (50) or housing bore encloses, and that the throttle body (56) is positively secured in the installed state against rotation and axially fixed. Hydraulic arrangement after Claim 1 , characterized in that the two throttle channels (64, 72) are formed as two thread-like coiled outer grooves (68, 76) with the same pitch axially spaced from each other between an axially outer axial groove (66, 74) and an axially inner axial groove ( 70, 78) in the cylindrical outer wall (60) of the throttle body (56) are arranged. Hydraulic arrangement after Claim 2 , characterized in that the throttles (30, 40) are set by different sized cross sections and / or lengths of their throttle channels (64, 72) to different throttle strengths. Hydraulic arrangement after Claim 2 or 3 , characterized in that the throttle body (56) by a in its inner end wall (62) arranged diagonal groove (80) engages in the mounted state, the adjacent end of the central web (54) of the hollow shaft (50) or housing bore, against a form fit Twisting is secured. Hydraulic arrangement after Claim 2 or 3 , characterized in that the throttle body (56) by two diagonally opposite in its cylindrical outer wall (60) arranged axial securing grooves (82, 84), in the installed state in each case a radial web (86, 88) on the inner wall (52) of Hollow shaft (50) or housing bore engages, positively secured against rotation, wherein the securing grooves (82, 84) circumferentially offset from the outer and inner Axialnuten (66, 74; 70, 78) of the throttle channels (64, 72) are arranged, and wherein the coiled outer grooves (68, 76) of the throttle channels (64, 72) in the region of the securing grooves (82, 84) are formed radially lower than the latter. Hydraulic arrangement after Claim 5 , characterized in that the radial webs (86, 88) on the inner wall (52) of the hollow shaft (50) or housing bore formed by the removal or omission of a central portion of the central web (54) as a remaining remainder webs of the central web (54). Hydraulic arrangement according to one of Claims 2 to 6 , characterized in that for axial fixing of the throttle body (56) a hollow screw (90) is provided which is screwed in the mounted state in the throttle end of the case in this case with an internal thread (102) provided hollow shaft (50) or housing bore and with its annular inner end wall (100) on the outer end wall (58) of the throttle body (56) and abuts with its screw head (96) on the throttle-side edge of the hollow shaft (50) or housing bore. Hydraulic arrangement after Claim 7 , characterized in that the outer Axialnuten (66, 74) of the throttle body (56) in the installed state via a between these in the outer end wall (58) of the throttle body (56) arranged diagonal groove (104) with the central bore (98) of the hollow screw (90) are fluidically connected. Hydraulic arrangement according to one of Claims 2 to 6 , characterized in that the throttle body (56) is provided for its rotation and axial fixation with at least two flexurally elastic tabs (106, 110) which diagonally opposite and axially outwardly directed at the outer edge of the outer end wall (58) of the throttle body (56). are arranged, and which in the mounted state, each with a radial projection (108, 112) engage in corresponding recesses (114, 116) in the inner wall (52) of the hollow shaft (50) or housing bore. Hydraulic arrangement after Claim 9 , characterized in that the radial projections (108, 112) on the flaps (106, 110) of the throttle body (56) cylindrical and the associated recesses (114, 116) in the inner wall (52) of the hollow shaft (50) or housing bore as cylindrical, radial bores are formed.

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