DE102010016037A1 - Switchover valve, particularly for controlling hydraulic fluid flow of internal combustion engine, has ballpoint mechanism, which is engaged by applying actuating impulse to actuating unit of ballpoint mechanism - Google Patents

Abstract

The switchover valve (1) has a ballpoint mechanism (2), which is engaged by applying an actuating impulse to an actuating unit (3) of the ballpoint mechanism and is coupled with the switchover valve in such way that the two engagement positions corresponds to a respective switching position of a control piston (6) of the switchover valve. The control piston of the switchover valve is displaceable in opposite direction of the actuating impulse around a predetermined path. An independent claim is also included for an internal combustion engine.

Description

The present invention relates to a switching valve, in particular for controlling a hydraulic fluid flow, and to an internal combustion engine with such a switching valve.

Although applicable to any vehicle, the present invention and its underlying problem is explained in more detail with respect to a passenger car.

In internal combustion engines, a high compression ratio has a positive effect on the efficiency of the internal combustion engine. Under compression ratio is generally understood the ratio of the entire cylinder space before compression to the remaining cylinder space after compression. In internal combustion engines with spark ignition, in particular gasoline engines, which have a fixed compression ratio, the compression ratio, however, may only be selected so high that so-called "knocking" of the internal combustion engine is avoided during full-load operation. However, for the much more frequently occurring partial load range of the internal combustion engine, ie with low cylinder filling, the compression ratio with higher values could be selected without "knocking" occurring. The important part load range of an internal combustion engine can be improved if the compression ratio is variably adjustable. Various systems are described for adjusting the compression ratio.

The DE 10 2005 055 199 describes a system in which the connecting rod length is variably adjustable. The variation of the connecting rod length is carried out by a rotation of an eccentric connecting rod eye. The rotation of the connecting rod eye is initiated by the action of mass and gas forces of the internal combustion engine, wherein the rotational movement is assisted by acted upon with engine oil piston in the connecting rod. To control the rotational movement of the eccentric connecting rod each one of the piston is pressurized with engine oil, while the other piston is depressurized. The pistons are controlled via a 3/2-way valve. To switch the 3/2-way valve, this must be operated mechanically. For this purpose, a complex solution of slide tracks, switching and push rods, which are driven by an electric motor, for example, provided from outside. However, this requires extensive changes to the internal combustion engine.

Thus, the present invention has for its object to provide an improved changeover valve, which eliminates the disadvantages mentioned above.

This object is achieved by a switching valve with the features of claim 1 and / or by an internal combustion engine with the features of claim 13.

Accordingly, it is provided:
A switching valve, in particular for controlling a hydraulic fluid flow, with a ballpoint pen mechanism, which is engageable by applying an actuating pulse to an actuating means of the ballpoint pen mechanism alternately in a first or in a second detent position and coupled to the switching valve, that the first or the second detent position of a respective first or second switching position of a control piston of the switching valve corresponds.

An internal combustion engine having an adjustable compression ratio, comprising: such a switching valve; and a connecting rod assembly with a arranged in a connecting rod eye and / or a Hublagerauge hydraulically adjustable eccentric means for adjusting an effective connecting rod length, wherein an adjustment of the eccentric means of the switching valve is controllable.

The basic idea of the present invention is to provide a change-over valve which is provided with a ball-point pen mechanism which switches the change-over valve alternately from a first to a second switching position and vice versa by applying an actuating pulse.

In the dependent claims are advantageous refinements and improvements of the specified in claim 1 switching valve or specified in claim 13 internal combustion engine.

According to a preferred development is for switching the switching valve from the first switching position to the second switching position by applying the actuating pulse to the actuating means of the ballpoint pen mechanism of the control piston of the switching valve in a direction opposite to a direction of the actuating pulse displaced by a predetermined distance. This advantageously allows a simple switching of the switching valve from the first switching position to the second switching position.

According to a further preferred embodiment, for switching the switching valve from the second switching position to the first switching position by applying the actuating pulse to the actuating means of the ballpoint pen mechanism of the control piston of the switching valve in approximately the direction of the actuating pulse by the predetermined distance displaced. This advantageously allows a simple switching of the switching valve from the second switching position to the first switching position.

According to a further preferred development, the ballpoint pen mechanism is designed in the manner of a Securit ^™ mechanism, in particular with: a control sleeve for the axial guidance of the actuating means and a torsion sleeve; and a spring device which axially prestresses the control piston, the rotary sleeve and the actuating means against the actuating pulse, wherein the rotary sleeve is in operative connection with the control sleeve and the actuating means such that when the actuating pulse is applied to the actuating means, this with respect to the control sleeve together with the rotary sleeve is axially displaceable, that the turning sleeve can be brought alternately from the first to the second detent position. In this way, upon actuation of the reversing valve from only one actuating direction, this can be brought reliably into the two switching positions, which simplifies the use of the reversing valve.

According to a further preferred embodiment, the changeover valve is characterized by a control sleeve, which arranged on an inner wall with respect to a longitudinal direction of the control sleeve axially extending control sleeve ribs, an end face of the control sleeve associated oblique control sleeve rib end faces and between each two adjacent control sleeve ribs arranged Steuerhülsennuten, which with respect to the longitudinal direction the control sleeve alternately have different control sleeve groove depths; an at least partially arranged in the control sleeve rotational sleeve having complementary to the control sleeve grooves Verdrehhülsenrippen and the oblique control sleeve rib end faces facing oblique Verdrehhülsenrippen-end faces; the control piston, which is in operative contact with an end face of the torque tube; the actuating means, which is feasible by means of actuating means ribs in the Steuerhülsennuten and having a toothed annular surface, which is in operative contact with the Verdrehhülsenrippen-end faces; and spring means biasing the control piston, the torque tube, and the actuating means against the actuating pulse. This ensures easy manufacturability of the switching valve.

According to a further preferred development, when the actuating pulse is applied to the actuating means, the latter is displaceable with the torsion sleeve into the control sleeve against a spring force of the spring device in such a way that the torsion sleeve ribs disengage from the associated control sleeve grooves with a first depth of the control sleeve groove, wherein the toothed Ring face and the Verdrehhülsenrippen-end faces are in operative contact, that the Verdrehhülse performs a first rotational movement, the Steuerhülsenrippen end faces and Verdrehhülsenrippen-end surfaces slide on each other such that the Verdrehhülse performs a second rotational movement, the Verdrehhülsenrippen in Steuerhülsennuten with a second Steuerhülsennuten Engage depth, the rotational sleeve engages in one of the locking positions, and wherein the control piston due to the operative connection with the rotary sleeve in one of the Schaltst is achievable. This allows a reliable and safe switching from the first to the second switching position and vice versa, whereby the reliability of the switching valve increases.

According to a further preferred embodiment, a number of Verdrehhülsenrippen the half of a number of Steuerhülsennuten. This reliably ensures that the torsion sleeve is guided in the control sleeve.

According to a further preferred development, the ballpoint pen mechanism is designed in the manner of a ball mechanism, in particular with: a control sleeve for the axial guidance of the actuating means; a ball which is slidably disposed in a radial groove of the control sleeve; and a spring device which axially prestresses the control piston and the actuating means against the actuating pulse, wherein the ball is in operative connection with a groove provided in the actuating means such that when the actuating pulse is applied to the actuating means, it is axially displaceable with respect to the control sleeve the actuating means due to the operative connection with the ball can be brought alternately from the first to the second detent position. This allows a particularly easy manufacturability of the switching valve.

According to a further preferred embodiment, the groove is formed as a heart-shaped groove. This allows a reliable guidance of the ball in the two detent positions of the ballpoint pen mechanism.

According to a further preferred development, the control sleeve is designed as a valve bore, in particular as a valve bore in a valve block with respective fluid grooves of the control piston associated with the valve bore through the fluid lines. As a result, the range of application of the changeover valve is advantageously extended.

According to a preferred embodiment, the actuating pulse can be applied by a fluid pressure, whereby the operation of the switching valve is simplified and its application area is expanded.

According to a preferred embodiment, the spring device is designed such that an actuation of the changeover valve takes place only at an actuation pulse above a predetermined threshold value. This reliably prevents accidental switching of the switching valve, thereby increasing its reliability.

According to a further preferred development, the changeover valve is integrated in the connecting rod arrangement, in particular in a region of the lifting bearing eye, whereby the changeover valve takes up only small installation space. As a result, the range of application of the changeover valve is advantageously extended.

According to a preferred embodiment, the actuating pulse can be applied by an engine oil pressure, wherein the internal combustion engine has means, for example a controllable oil pump or a pressure accumulator, for briefly increasing the engine oil pressure. This advantageously makes it possible to integrate the changeover valve into existing engine oil systems, thereby widening the range of use of the changeover valve.

The invention is explained in more detail below with reference to embodiments with reference to the accompanying schematic figures of the drawing.

From the figures show:

1 a partial sectional view of a switching valve according to a preferred embodiment of the present invention in a first switching position;

2 a partial view of the switching valve of the preferred embodiment of the present invention according to the 1 ;

3 a sectional view of the switching valve of the preferred embodiment of the present invention along the section line III-III of 1 ;

4 a further partial view of the switching valve of the preferred embodiment of the present invention according to the 1 in an intermediate switching position;

5 a partial sectional view of the switching valve of the preferred embodiment of the present invention according to the 1 in a second switching position;

6 a partial sectional view of a switching valve according to another preferred embodiment of the present invention in a first switching position;

7 a partial sectional view of the switching valve of the further preferred embodiment of the present invention according to the 6 in a second switching position;

8th a partial sectional view of a switching valve according to yet another preferred embodiment of the present invention in a first switching position;

9 a partial sectional view of the switching valve of the still another preferred embodiment of the present invention according to the 8th in a second switching position;

10 a side view of an exemplary application of a switching valve in a first operating condition;

11 a further side view of the exemplary application of a switching valve according to the 10 in a second operating state; and

12 an exemplary oil pressure curve for driving a switching valve.

In the figures of the drawing, the same reference numerals designate the same or functionally identical components, unless indicated otherwise.

The 1 to 5 , to which reference will be made hereinafter, show a first exemplary embodiment of a switching valve 1 with a ballpoint pen mechanism 2 , in particular for controlling a hydraulic fluid flow, in a first switching position. The changeover valve 1 has a control piston 6 with a fluid groove 28 on. The control piston 6 has a cylindrical basic shape, wherein in a lateral surface of the control piston 6 the fluid groove 28 in the form of an annular groove 28 is provided. The control piston 6 is for example in a valve bore 26 the changeover valve 1 preferably mounted axially displaceable. The valve bore 26 is preferably in a valve block 27 brought in. In the valve block 27 are fluid lines 30 . 31 provided, which through the valve bore 26 be broken. The fluid lines 30 . 31 are doing with respect to a central axis 39 the valve bore 26 Preferably arranged spaced apart in the axial direction. The valve bore 26 is preferably designed as a blind hole. Alternatively, the valve bore may also be formed as a through hole. Between a frontal area 40 the valve bore 26 and a face 41 of the control piston 6 is a spring device 10 , in particular in the form of a compression spring 10 arranged. The spring device 10 can instead of against the face 40 also against one in a corresponding annular groove of the valve bore 26 be mounted clamped circlip. The valve bore 26 can then be formed for example as a through hole. The fluid lines 30 . 31 are so in the axial direction of the valve bore 26 arranged that by an axial displacement of the control piston 6 in the valve bore 26 always one of the fluid lines 30 . 31 through the control piston 6 is closed. In 1 is exemplary the fluid line 31 by means of the control piston 6 locked. Through the fluid line 30 can flow a fluid, which means the arrows 4 . 5 is indicated.

At a second end face 42 of the control piston 6 fitting is the ballpoint pen mechanism 2 arranged, which may be performed for example in the manner of a so-called Securit ^TM mechanism. The ballpoint pen mechanism 2 has one at the end face 42 of the control piston 6 fitting torsion sleeve 9 and one with the torsion sleeve 9 operatively connected actuating means 3 on. Preferably, the control piston 6 with the torsion sleeve 9 integrally formed. The actuating means 3 is preferred as a printing stamp 3 educated. The torsion sleeve 9 and the actuating means 3 are at least partially from a control sleeve 8th the ballpoint pen mechanism 2 surround. The control sleeve 8th can for example be an integral part of the valve bore 26 be. The control sleeve 8th can in the valve bore 26 rotationally fixed but axially freely displaceable, for example, radialspielbehaftet be recorded.

The 2 illustrates the changeover valve 1 according to the 1 , wherein for better explanation, the control sleeve 8th and the valve block 27 with the fluid lines 30 . 31 not shown. The torsion sleeve 9 has a first cylinder portion 43 on, whose one end face 44 at the frontal area 42 of the control piston 6 is applied. The first cylinder section 43 has on its lateral surface Verdrehhülsenrippen 16 which is relative to a circumference of the first cylinder section 43 are regularly spaced from each other. At least, the torsion sleeve 9 a twist sleeve rib 16 on. For example, the torsion sleeve 9 however, four twist sleeve ribs 16 on. The torsion sleeve ribs 16 indicate to their face 44 of the first cylinder section 43 opposite end face 46 oblique torsion sleeve rib end faces 17 on. The torsion sleeve 9 has a second cylinder portion 45 up, extending from the frontal area 46 of the first cylinder section 43 extends. The second cylinder section 45 preferably has a smaller outer diameter than the first cylinder portion 43 on.

The second cylinder section 45 is at least partially from the actuating means 3 taken, for example, as a sleeve with a preferably closed end face 47 is trained. Parallel spaced from the end face 47 is a toothed ring surface 20 of the actuating means 3 provided, which in operative engagement with the oblique Verdrehhülsen end faces 17 the torsion sleeve 9 stands. On an outer surface of the actuating means 3 are actuating ribs 19 provided, which on a circumference of the actuating means 3 preferably arranged uniformly spaced from each other. The actuator ribs 19 preferably have a slightly smaller outer diameter than the Verdrehhülsenrippen 16 , The actuating means 3 still has a paragraph 48 on, which is starting from the end face 47 in the direction of the toothed ring surface 20 extends. Preferably, the paragraph comprises 48 in about one third of a length of the actuating means 3 , An outside diameter of the heel 48 of the actuating means 3 corresponds approximately to a bore diameter of the valve bore 26 , or a value greater than the bore diameter of the valve bore 26 , where the outside diameter of the paragraph 48 is configured such that the actuating means 3 in the valve bore 26 preferably sealingly displaceable is. The actuating means 3 can by means of the spring device 10 against an axial stop, for example in the form of an annular groove in the valve bore 26 arranged retaining ring, be biased.

The control sleeve 8th encloses, as already stated, the actuating means 3 and the torsion sleeve 9 at least in sections. The 3 shows the changeover valve 1 in a sectional view along the section line III-III according to the 1 , For simplified representation, only the control sleeve 8th shown. On an interior wall 11 the control sleeve 8th are with respect to a longitudinal direction of the control sleeve 8th axially extending control sleeve ribs 12 arranged, which oblique control sleeve rib end faces 14 which have a front side 13 the control sleeve 8th assigned. Between each two adjacent control sleeve ribs 12 are control sleeve grooves 15 formed, which with respect to the longitudinal direction of the control sleeve 8th have alternately different control keyway depths t1, t2. The control sleeve grooves 15 are designed such that in each case one the entire control sleeve 8th continuous control groove 15 with the depth t1, wherein the depth t1, for example, the axial length of the control sleeve 8th corresponds, in alternation with a Steuerhülsennut 15 which the control sleeve 8th axially passes only to a depth t2, is arranged. The torsion sleeve ribs 16 and the actuator ribs 19 are preferably in operative engagement with the control sleeve grooves 15 and are guided by them in an axial direction. A number of the control sleeve grooves 15 corresponds, for example, at least a double number of Verdrehhülsenrippen 16 ,

The operation of the switching valve 1 with the ballpoint pen mechanism 2 The nature of Securit ^TM mechanics is explained below. The 1 to 3 put the ballpoint pen mechanism 2 in the first detent position or the changeover valve 1 in the first switching position. In the first switching position is the valve bore 26 breaking fluid line 30 over the fluid groove 28 of the control piston 6 opened and the second fluid line 31 is through the control piston 6 blocked. In the first detent position of the ballpoint pen mechanism are the Verdrehhülsenrippen-end faces 17 at least punctiform in contact with faces 49 those control sleeve grooves 15 which the control sleeve 8th only through to the control sleeve groove depth t2. The torsion sleeve 9 is in the axial direction over the control sleeve 8th above.

For transferring the ballpoint pen mechanism 2 from the first detent position into a second detent position or for transferring the reversing valve 1 from the first in the second switching position is on the end face 47 of the actuating means 3 an actuating pulse I applied. For this purpose, a force is applied for a short time, which is applied against one of the spring device 10 caused spring force acts. This actuation pulse can, for example, via an oil pressure pulse to the actuating means 3 be applied. By the actuating pulse I, the actuating means 3 with the torsion sleeve 9 and the control piston 6 against the spring force of the spring device 10 into the valve bore 26 shifted into it. In this case, the actuating means ribs 19 and the torsion sleeve ribs 16 in the control sleeve grooves 15 axially guided. The torsion sleeve 9 will be like in 4 illustrated axially displaced so far that the Verdrehhülsenrippen 16 out of engagement with the corresponding Steuerhülsennuten 15 reach. The torsion sleeve 9 is then by means of the actuating means 3 over the control sleeve grooves 15 pushed out. The torsion sleeve 9 For example, is completely out of the control sleeve axially 8th pushed out. The torsion sleeve ribs 16 and the actuator ribs 19 are circumferentially offset from each other on the rotating sleeve 9 or the actuating means 3 arranged that as long as the ribs 16 and 19 in the guide sleeve grooves 15 are guided, a sliding of the oblique Verdrehhülsenrippen-end faces 17 on tooth flanks of the toothed ring surface 20 from the in 2 shown intermediate position in the in 4 illustrated stable end position due to the axial guidance by means of the control sleeve 8th is suppressed. In the in 2 shown position are the Verdrehhülsenrippen-end faces 17 in an unstable intermediate position on the tooth flanks of the toothed ring surface, so to speak 20 , Are the torsion sleeve ribs 16 no longer in engagement with the control sleeve grooves 15 slide the Verdrehhülsenrippen front surfaces 17 on the tooth flanks of the toothed ring surface 20 , whereby the torsion sleeve rib end faces 17 in the 4 take shown stable end position. This leads the torsion sleeve 9 with respect to the control sleeve 8th a slight first rotational movement through. At a termination of the actuating pulse I, the torque sleeve moves 9 due to the spring force of the spring device 10 against the actuating direction of the actuating means 3 back. Because the torsion sleeve 9 due to the sliding of the torsion sleeve rib end faces 17 on the tooth flanks of the toothed ring surface 20 of the actuating means 3 has performed a rotational movement, come the Verdrehhülsenrippen 16 no longer with the corresponding Steuerhülsennuten 15 with the depth t2 in engagement, but the Verdrehhülsenrippen-end faces 17 come with the control sleeve rib end faces 14 in contact. As a result, the Verdrehhülsenrippen-end surfaces slide 17 on the control sleeve rib end faces 14 off and the torsion sleeve 9 performs another second slight rotational movement, wherein the Verdrehhülsenrippen 16 in control sleeve grooves 15 be introduced with the depth t1, which is the control sleeve 8th go through on their entire axial length. This will be the first cylinder section 43 the torsion sleeve 9 preferably completely in the control sleeve 8th added. Due to the spring force of the spring device 10 becomes the control piston 6 with his face 42 against the face 13 the control sleeve 8th pressed. The ballpoint pen mechanism 2 is now in the in 5 illustrated second detent position, which the second switching position of the changeover valve 1 equivalent. In the second switching position of the switching valve 1 is the fluid channel 30 blocked and through the fluid channel 31 a fluid can flow. By re-applying the actuating pulse I, the rotating sleeve rotates 9 continue and the switching valve 1 is transferred back to its first switching position.

The 6 and 7 to which reference will now be made simultaneously to show an alternative but equally preferred embodiment of the switching valve 1 with the ballpoint pen mechanism 2 , Functionally corresponds to the embodiment of the switching valve 1 according to the 6 and 7 the previously explained embodiment of the switching valve 1 , The embodiment of the switching valve 1 according to the 6 and 7 differs from the embodiment of the switching valve 1 according to the 1 to 5 initially through the formation of the valve bore 26 , The valve bore 26 is as a stepped through hole 26 formed, wherein the spring means 10 against one in a radial groove 61 mounted circlip 62 is tense. The spring device 10 clamps the control piston 6 that the fluid groove 28 and another of the fluid groove 28 axially spaced fluid groove 29 and the ballpoint pen mechanism 2 against a paragraph 64 the valve bore 26 , The fluid line 30 is the fluid groove 28 and the fluid line 31 is the fluid groove 29 assigned. In the valve block 27 is a control line 63 provided, which is the supply of a fluid to the actuating means 3 for applying the same with the actuating pulse I is used. The 6 shows the first switching position of the switching valve 1 in which the fluid line 31 through the control piston 6 is blocked and the fluid line 30 as by the arrows 4 . 5 shown, is traversed by a fluid. The 7 shows the second switching position of the switching valve 1 in which the fluid line 30 through the control piston 6 is blocked and the fluid line 31 as by the arrows 4 . 5 shown, is traversed by a fluid.

The 8th and 9 show a further alternative but also preferred embodiment of a switching valve 1 with a ballpoint pen mechanism 2 , In this exemplary embodiment, the ballpoint pen mechanism is 2 designed as so-called ball mechanics. In the valve bore 26 are the spring device 10 , the control piston 6 and the ballpoint pen mechanism 2 arranged. In contact with the face 42 of the control piston 6 is the actuating means 3 , The actuating means 3 is at least partially from the control sleeve 8th surrounded and stored in this displaceable. The control sleeve 8th is for example an integral part of the valve bore 26 , As in 8th shown, the control sleeve 8th in the valve bore 26 also by means of two retaining rings 65 . 66 in the axial direction of the valve bore 26 be secured against slipping. In the control sleeve 8th is preferably circumferentially a radial groove 24 provided for at least partially receiving a ball 23 , in particular a steel ball 23 serves. On a peripheral surface of the actuating means 3 is a groove 25 , in particular a heart-shaped groove 25 provided, which also for at least partially receiving the ball 23 serves. The actuating means 3 is located above the ball 23 in operative engagement with the radial groove 24 the control sleeve 8th , In the in 8th illustrated first detent position of the ballpoint pen mechanism 2 , which is the first switching position of the switching valve 1 matches, the ball becomes 23 in an upper detent point of the heart-shaped groove 25 held. There she is by the spring force of the spring device 10 kept in position. The fluid line 31 is blocked, the fluid line 30 can be traversed by a fluid, as by means of the arrows 4 . 5 indicated.

When the actuating pulse I acts on the end face 47 of the actuating means 3 this is axially in the valve hole 26 shifted and the ball 23 slides along the heart-shaped groove 25 preferably clockwise from the in 8th shown first detent position in the in 9 shown second detent position of the ballpoint pen mechanism 2 , the second switching position of the switching valve 1 equivalent. At the same time, the ball moves in the radial groove 24 the control sleeve 8th , In the second detent position, the ball 23 again through the spring device 10 kept in position. The fluid line 30 is in the second switching position of the switching valve 1 blocked and the fluid line 31 is flowed through. Upon a renewed application of the actuating pulse I, the ball slides 23 continue clockwise back to the first detent position of the ballpoint pen mechanism 2 ,

The 10 and 11 illustrate an exemplary use case for a changeover valve 1 according to one of the exemplary embodiments of 1 to 9 , The 10 and 11 show a connecting rod assembly 33 for an internal combustion engine having an adjustable compression ratio. The connecting rod arrangement 33 has a connecting rod 56 and one in a connecting rod eye 34 the connecting rod 56 arranged preferably hydraulically adjustable eccentric 36 on. Alternatively or additionally, the eccentric 36 also in a crank eye 35 be arranged. The eccentric device 36 has an eccentric to a midpoint 37 of the connecting rod eye 34 arranged piston pin bore with a center point 38 on, which receives a piston pin. The eccentric device 36 is for adjusting an effective connecting rod length l _eff . The connecting rod length l _eff is the distance between a center point 32 of the stroke bearing eye 35 to the center 38 defines the piston pin bore.

The rotation of the adjustable eccentric 36 is initiated by the action of mass and load forces of the internal combustion engine, which at a power stroke of the internal combustion engine to the eccentric 36 Act. During a power stroke, the directions of action of the change to the eccentric 35 acting forces continuously. The rotational movement is acted upon by engine oil in the connecting rod assembly 33 integrated pistons 50 . 51 supports, or prevent the piston resetting the eccentric 36 due to varying force action directions of the forces acting on the eccentric forces. The pistons 50 . 51 are by means of eccentric rods 67 . 68 on both sides with an eccentric body 69 the eccentric device 36 operatively connected. The pistons 50 . 51 are over oil pipes 52 . 53 from the eye bearing eye 35 from acted upon with engine oil. check valves 54 . 55 prevent a backflow of the engine oil from the piston volumes of the piston 50 . 51 back into the hydraulic lines 52 . 53 or in an engine compartment of the internal combustion engine.

Preferably in the region of the lifting eye 35 is the changeover valve 1 with the ballpoint pen mechanism 2 intended. The changeover valve 1 is preferably designed as a preassembled module, which can be used arbitrarily at different positions and for different engines. The connecting rod 56 So put the valve block 27 the changeover valve 1 dar. The valve bore 26 extends, for example, starting from the Bublagerauge 35 as a stepped blind hole in the connecting rod 56 into it. The actuating means 3 is subjected to the same oil pressure, with the oil lines 52 . 53 be charged. To slipping out of the actuating means 3 from the valve bore 26 To prevent, for example, is a circlip 57 in a corresponding groove of the valve bore 26 intended. The fluid line 30 connects the pressure chamber of the piston 50 and the fluid line 31 connects the pressure chamber of the piston 51 with the engine interior. The entry of the fluid lines 30 . 31 in the engine compartment is in the 10 and 11 not shown, it takes place for example by a respective vent hole perpendicular to the plane of the drawing on the control piston 6 out. The connection in each case one of the fluid lines 30 . 31 towards the engine interior is by means of the switching valve 1 either blockable or releasable. Manufacturing technology, the fluid lines 30 . 31 for example, by from an outside of the connecting rod 56 the piston chambers of the pistons 50 . 51 and the valve bore 26 running through holes, the motor interior facing the ends, for example by means of closure balls 70 . 71 be sealed oil-tight.

The 10 shows the ballpoint pen mechanism 2 in the second detent position or the changeover valve 1 in the second switching position. The piston 51 is over the fluid line 31 fluidly connected to the engine compartment of the internal combustion engine. The piston 51 So it is by means of the switching valve 1 depressurized. Through the hydraulic line 53 supplied oil is through the fluid line 31 supplied to the engine compartment. The pressure relief of the fluid line 30 of the piston 50 is through the control piston 6 the changeover valve 1 blocked. That is, the piston 50 is via the hydraulic line 52 engine oil pressure applied, whereas the piston 51 is depressurized.

During a brief increase in the engine oil pressure, for example via a controllable oil supply pump of the internal combustion engine or via a hydraulic accumulator, the actuating means 3 the changeover valve 1 acted upon by a corresponding actuation pulse I. The changeover valve 1 is characterized by the second in the in 11 transferred shown first switching position. In the first switching position of the switching valve 1 is the fluid line 31 between the piston 51 and the engine compartment through the spool 6 locked, causing the piston 51 over the oil line 53 is charged with engine oil pressure. The piston 50 is over the fluid line 30 passing through the switching valve 1 is unlocked, connected to the engine compartment, that is, the piston 50 is in the first switching position of the switching valve 1 depressurized. The piston 51 So it is continuously filled with engine oil, whereas from the piston 50 the engine oil through the fluid line 30 and the switching valve 1 flows into the engine compartment. The adjustable eccentric device 36 As a result, it is supported by the pressurized piston due to the mass and load forces of the internal combustion engine acting on it 51 Turn clockwise to the right as indicated by the arrow 72 is indicated. By turning the eccentric 36 increases the effective connecting rod length l _eff , thereby changing the compression ratio of the internal combustion engine. By re-applying the actuating pulse I to the actuating means 3 the changeover valve is transferred from the first to the second switching state, whereby the eccentric 36 against the arrow 72 moved to the left, reducing the effective connecting rod length l _eff again.

The 12 exemplifies the course of the engine oil pressure for acting on the actuating means 3 the changeover valve 1 with the actuating pulse I. The pressure p is plotted on the y-axis of the diagram and the time t on the x-axis. The changeover valve 1 is initially, for example, in its first switching position. The switching positions of the changeover valve 1 be by means of the curve 74 represented, wherein the portion of the curve shown in dashed lines 74 the first and the solid portion symbolizes the second switching position. The engine oil pressure curve is by means of the curve 73 shown. The engine oil pressure initially runs at a normal level, and then for a short time to a first pressure plateau 58 to be raised. Here, the switching of the changeover valve takes place 1 from the first to the second switching position. Increasing the engine oil pressure to the pressure of the pressure plateau 58 is only required until the ballpoint pen mechanism 2 is latched from the first to the second detent position and from the second to the first detent position. After locking the ballpoint pen mechanism 2 The engine oil pressure can be lowered back to the original level. By re-raising the engine oil pressure to a second pressure plateau 75 is a renewed actuation of the switching valve 1 possible, wherein this is switched back from the second to the first switching state.

The changeover valve 1 is thus controllable without a complex external actuation. The control of the switching from the first to the second switching position or vice versa by applying an actuating pulse I, for example by briefly raising the engine oil pressure of an internal combustion engine. Therefore, the switching valve 1 easily integrated into existing engine oil systems. LIST OF REFERENCE NUMBERS 1 switching valve 2 ballpoint pen mechanism 3 Actuator / plunger 4 arrow 5 arrow 6 spool 8th control sleeve 9 Verdrehhülse 10 spring means 11 inner wall 12 Control sleeve ribs 13 front 14 End faces of the control sleeve ribs 15 Steuerhülsennuten 16 Verdrehhülsenrippen 17 End faces of the torsion sleeve ribs 19 Actuator ribs 20 Toothed ring surface 23 Bullet 24 radial groove 25 Groove / heart-shaped groove 26 valve bore 27 manifold 28 fluid groove 29 fluid groove 30 fluid line 31 fluid line 32 Center of the stroke bearing eye 33 connecting rod 34 Pleuellagerauge 35 Hublagerauge 36 eccentric 37 Center of the connecting rod eye 38 Center of the piston pin bore 39 central axis 40 face 41 face 42 face 43 First cylinder section 44 face 45 Second cylinder section 46 face 47 face 48 paragraph 49 face 50 piston 51 piston 52 Hydraulic line / oil pipe 53 Hydraulic line / oil pipe 54 check valve 55 check valve 56 connecting rod 57 circlip 58 pressure plateau 61 radial groove 62 circlip 63 control line 64 paragraph 65 circlip 66 circlip 67 eccentric 68 eccentric 69 eccentric 70 ball Size 71 ball Size 72 arrow 73 Engine oil pressure profile 74 Switching position curve 75 pressure plateau I actuating pulse l _eff Effective connecting rod length t Time p print t1 Depth of the control sleeve grooves t2 Depth of the control sleeve grooves

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 102005055199 [0004]

Claims (15)

Changeover valve ( 1 ), in particular for controlling a hydraulic fluid flow, with a ballpoint pen mechanism ( 2 ), which by applying an actuating pulse (I) to an actuating means ( 3 ) of the ballpoint pen mechanism ( 2 ) alternately latched in a first or in a second detent position and in such a way with the switching valve ( 1 ) is coupled, that the first or the second detent position of a respective first or second switching position of a control piston ( 6 ) of the changeover valve ( 1 ) corresponds. Changeover valve according to claim 1, characterized in that for switching the changeover valve ( 1 ) from the first switching position ( 4 ) in the second switching position ( 5 ) by applying the actuating pulse (I) on the actuating means ( 3 ) of the ballpoint pen mechanism ( 2 ) of the control piston ( 6 ) of the changeover valve ( 1 ) is displaceable in a direction opposite to a direction of the actuating pulse (I) by a predetermined distance. Changeover valve according to claim 2, characterized in that for switching the changeover valve ( 1 ) from the second switching position ( 5 ) in the first switching position ( 4 ) by applying the actuating pulse (I) on the actuating means ( 3 ) of the ballpoint pen mechanism ( 2 ) of the control piston ( 6 ) of the switching valve is displaceable in the direction of the actuating pulse (I) by the predetermined distance. Changeover valve according to one of the preceding claims, characterized in that the ballpoint pen mechanism ( 2 ) is designed in the manner of a Securit ^™ mechanism, in particular with: a control sleeve ( 8th ) for the axial guidance of the actuating means ( 3 ) and a rotary sleeve ( 9 ); and a spring device ( 10 ), which the control piston ( 6 ), the torsion sleeve ( 9 ) and the actuating means ( 3 ) against the actuating pulse (I) axially prestressed spring, wherein the torsion sleeve ( 9 ) with the control sleeve ( 8th ) and the actuating means ( 3 ) is operatively connected in such a way that in the application of the actuating pulse (I) to the actuating means ( 3 ) this with respect to the control sleeve ( 8th ) together with the torsion sleeve ( 9 ) is axially displaceable such that the torsion ( 9 ) alternately from the first to the second detent position can be brought. Changeover valve according to claim 4, characterized in that a control sleeve ( 8th ), which on an inner wall ( 11 ) arranged with respect to a longitudinal direction of the control sleeve ( 8th ) axially extending control sleeve ribs ( 12 ), an end face ( 13 ) of the control sleeve ( 8th ) associated oblique control sleeve rib end faces ( 14 ) and between each two adjacent control sleeve ribs ( 12 ) arranged control sleeve grooves ( 15 ), which with respect to the longitudinal direction of the control sleeve ( 8th ) have different control keyway depths alternately; one at least in sections in the control sleeve ( 8th ) arranged torsion sleeve ( 9 ) leading to the control sleeve grooves ( 15 ) complementary torsion sleeve ribs ( 16 ) and the oblique control sleeve rib end faces ( 14 ) facing oblique Verdrehhülsenrippen-end surfaces ( 17 ) having; the control piston ( 6 ) which is in operative contact with an end face ( 44 ) of the torsion sleeve ( 9 ) stands; the actuating means ( 3 ), which by means of actuating ribs ( 19 ) in the control sleeve grooves ( 15 ) and a toothed annular surface ( 20 ) which in operative contact with the Verdrehhülsenrippen-Stirnflächen ( 17 ) stands; and a spring device ( 10 ), which the control piston ( 6 ), the torsion sleeve ( 9 ) and the actuating means ( 3 ) spring-biased against the actuating pulse (I). Change-over valve according to claim 5, characterized in that upon application of the actuating pulse (I) to the actuating means ( 3 ) this with the torque tube ( 9 ) in the control sleeve ( 8th ) against a spring force of the spring device ( 10 ) is displaceable such that the Verdrehhülsenrippen ( 16 ) out of engagement with the associated control sleeve grooves ( 15 ) with a first control sleeve groove depth, wherein the toothed annular surface ( 20 ) and the torsion sleeve rib end faces ( 17 ) are in operative contact in such a way that the torsion sleeve ( 9 ) performs a first rotational movement, wherein the control sleeve rib end faces ( 14 ) and the torsion sleeve rib end faces ( 17 ) slide on each other in such a way that the torsion sleeve ( 9 ) performs a second rotational movement, wherein the Verdrehhülsenrippen ( 16 ) in control sleeve grooves ( 15 ) engage with a second Steuerhülsennuten depth, wherein the Verdrehhülse ( 8th ) engages in one of the detent positions, and wherein the control piston ( 6 ) due to the operative connection with the rotary sleeve ( 9 ) can be brought into one of the switch positions. Changeover valve according to claim 5 or 6, characterized in that a number of the torsion sleeve ribs ( 16 ) half of a number of the control sleeve grooves ( 15 ) corresponds. Switching valve according to one of claims 1 to 3, characterized in that the ballpoint pen mechanism ( 2 ) is designed in the manner of a ball mechanism, in particular with: a control sleeve ( 8th ) for the axial guidance of the actuating means ( 3 ); a ball ( 23 ), which displaceably in a radial groove ( 24 ) of the control sleeve ( 8th ) is arranged; and a spring device ( 10 ), which the control piston ( 6 ) and the actuating means ( 3 ) against the actuating pulse (I) is axially spring biased, wherein the ball ( 23 ) with one in the actuating means ( 3 ) groove ( 25 ) is operatively connected in such a way that in the application of the actuating pulse (I) to the actuating means ( 3 ) this with respect to the control sleeve ( 8th ) is axially displaceable such that the actuating means ( 3 ) due to the operative connection with the ball ( 23 ) alternately from the first to the second detent position can be brought. Change-over valve according to claim 8, characterized in that the groove ( 25 ) as a heart-shaped groove ( 25 ) is trained. Switching valve according to one of claims 5 to 9, characterized in that the control sleeve ( 8th ) as a valve bore ( 26 ) is formed, in particular as a valve bore ( 26 ) in a valve block ( 27 ) with respective fluid grooves ( 28 . 29 ) of the control piston ( 6 ) associated with the valve bore ( 26 ) passing through fluid lines ( 30 . 31 ). Switching valve according to one of the preceding claims, characterized in that the actuating pulse (I) can be applied by a fluid pressure. Switching valve according to one of claims 5 to 11, characterized in that the spring device ( 10 ) is designed such that an actuation of the switching valve ( 1 ) occurs only at an actuation pulse (I) above a predetermined threshold. An internal combustion engine having an adjustable compression ratio, comprising: a switching valve ( 1 ) according to any one of the preceding claims; and a connecting rod assembly ( 33 ) with one in a connecting rod eye ( 34 ) and / or a bung eye ( 35 ) arranged hydraulically adjustable eccentric ( 36 ) for adjusting an effective connecting rod length (l _eff ), wherein an adjustment of the eccentric ( 36 ) by means of the switching valve ( 1 ) is controllable. Internal combustion engine according to claim 13, characterized in that the switching valve ( 1 ) in the connecting rod assembly ( 33 ), in particular in a region of the Hubagerauges ( 35 ) is integrated. Internal combustion engine according to claim 13 or 14, characterized in that the actuating pulse (I) can be applied by an engine oil pressure, wherein the internal combustion engine having means, such as a controllable oil pump or a pressure accumulator for briefly increasing the engine oil pressure.

Images