EP2870327B1 - Vane type phasing device with hydraulic control valve - Google Patents

Description

The invention relates according to claim 1 a Schwenkmotorversteller with a hydraulic valve.

• ein Druckmittelanschluss P und
• zwei axial diesem unmittelbar folgende Arbeitsanschlüsse A und B ab. Der Kolben weist einen Druckkammer-Zulaufkanal und einen getrennt von diesem angeordneten Druckkammer-Ablaufkanal auf. Der Kolben soll in einer am Rande erwähnten Ausgestaltungsform auch aus Kunststoff oder in einem pulvermetallurgischen Spritzgiessverfahren hergestellt werden können. Dabei ist als Beispiel das Metal-Injection-Molding Verfahren aufgeführt.

From the DE 10 2005 041 393 A1 a hydraulic valve for a Schwenkmotorversteller is already known. The hydraulic valve in accordance with the invention comprises a piston which is longitudinally displaceable within a bore. Go from the inner wall of the valve

• a pressure medium connection P and
• two axially this immediately following working connections A and B from. The piston has a pressure chamber inlet channel and a pressure chamber outlet channel arranged separately therefrom. The piston should also be made of plastic or in a powder metallurgical injection molding in an embodiment mentioned at the edge. As an example, the metal injection molding process is listed.

From the WO / 2011/015418 A1 is another Schwenkmotorversteller known with a hydraulic valve

The DE 196 37 174 A1 shows a hydraulic valve for a Schwenkmotorversteller in which a piston is arranged longitudinally displaceable within a bore with a longitudinal axis. From the inner wall of the bore go from two working ports A, B and a pressure medium connection P. The pressure medium connection P is arranged axially between the two working ports A, B.

From the DE 198 53 670 B4 Also, a hydraulic valve for a Schwenkmotorversteller is known. From the inner wall of the bore go two working ports A, B and a tank drain T from. The tank outlet T is arranged axially between the two working ports A, B. A front side of the hydraulic valve arranged pressure medium port P leads to the bore or the hollow piston from the inside pressure.

From the DE 10 2004 038 252 A1 Another hydraulic valve for a Schwenkmotorversteller is known. From the inner wall of the hole go axially successively a pressure medium connection P, a tank outlet T and two working connections A, B from.

The object of the invention is to provide a Schwenkmotorversteller with a hydraulic valve, the pressure medium connection P, the two working ports A, B are axially adjacent to a common side.

This object is achieved with the features of claim 1.

According to one advantage of the invention, the pressure medium connection P is immediately followed by the first working connection A (B). This first work connection A is followed by the second work connection B (A) directly or indirectly. "Indirect" means that there may still be a tank outlet T between the two working connections A, B. As a result of the directly or indirectly adjacent arrangement of the two working ports A, B, the Schwenkmotorversteller can be made axially correspondingly narrow at a, for example, centrally arranged for Schwenkmotorversteller hydraulic valve. The name of the two working ports A and B is arbitrary.

According to a further advantage of the invention, the pressure medium connection P is arranged axially after or in front of the two working connections A, B. Thus, this pressure medium connection P can be connected outside the Schwenkmotorverstellers to channels in the hydraulic valve, which can promote the supply pressure from a fluid feed pump to the working ports A and B. Consequently, holes in the Schwenkmotorversteller, which supply the supply pressure from the fluid feed pump to the pressure medium connection P within the Schwenkmotorverstellers, not necessary. Such holes, in particular by the rotor of the Schwenkmotorverstellers increase the processing effort and weaken the rotor. In a particularly advantageous manner, therefore, the hydraulic fluid is passed through the hollow piston of the valve.

• eine Mantelfläche mit einem großen Außendurchmesser im axial Bereiche des einen Arbeitsanschlusses und
• eine Mantelfläche mit einen kleinen Außendurchmesser im Bereich des anderen Arbeitsanschlusses

auf. Von den beiden Mantelflächen gehen jeweils eine Zulaufkante und eine Ablaufkante ab. Die beiden Zulaufkanten weisen voneinander hinfort. Die Ablaufkanten weisen aufeinander zu, so dass ein in einen Hohlraum des Hohlkolbens eingeleiteter Versorgungsdruck einerseits an einer projizierten Kreisfläche anliegt. Diese Kreisfläche wird vom kleinen Außendurchmesser gebildet, so dass eine Kraft in einer Axialrichtung wirksam ist. Hingegen liegt der Versorgungsdruck andererseits an einer projizierten Ringfläche an. Diese Ringfläche bildet sich aus dem großen Außendurchmesser abzüglich des ersten Außendurchmessers.The hydraulic valve has a stepped bore with the outgoing from this working ports A, B on. Within the bore of the pressure balanced hollow piston is axially displaceable. The hollow piston is displaceable sealingly displaceable with a first outer diameter within a bore portion. The hollow piston has adjacent to this first outer diameter

• a lateral surface with a large outer diameter in the axial regions of a working port and
• a lateral surface with a small outer diameter in the area of the other working connection

on. From the two lateral surfaces in each case a feed edge and a discharge edge go. The two inlet edges point away from each other. The discharge edges point towards one another, so that a supply pressure introduced into a hollow space of the hollow piston rests on the one hand against a projected circular surface. This circular area is formed by the small outer diameter, so that a force in an axial direction is effective. On the other hand, the supply pressure is applied to a projected annular surface. This annular surface is formed from the large outer diameter minus the first outer diameter.

The fact that the circular area is equal to the annular surface, the hollow piston is pressure balanced.

$$\mathrm{D}\mathrm{2}=\mathrm{5}\times \mathrm{K}$$

$$\mathrm{D}\mathrm{3}=\mathrm{3}\times \mathrm{K}$$

K ist dabei eine beliebige Konstante. Der Außendurchmesser D1 ist der kleine Außendurchmesser. Der Außendurchmesser D2 ist der große Außendurchmesser. Der Außendurchmesser D3 ist der erste Außendurchmesser. Die besagte Ringfläche bildet sich damit aus der Kreisflächendifferenz an den beiden Außendurchmessern D2, D3.In order to achieve an exact pressure balance these surfaces are in a concrete relationship to each other. About the circular surface formula results for the three associated outer diameter D1, D2, D3 of the piston: $$\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="imgf0001.png"\; state="\{\{state\}\}">D</figure-callout>}\mathrm{1}=\mathrm{4}\times \mathrm{<figure-callout\; id="2"\; label="K\; D"\; filenames="imgf0001.png"\; state="\{\{state\}\}">K\; </figure-callout>}$$

$$\mathrm{D}$$$$\mathrm{}\mathrm{2}=\mathrm{5}\times \mathrm{<figure-callout\; id="3"\; label="K\; D"\; filenames="imgf0001.png"\; state="\{\{state\}\}">K\; </figure-callout>}$$

$$\mathrm{D}$$$$\mathrm{}\mathrm{3}=\mathrm{3}\times \mathrm{K}$$

K is an arbitrary constant. The outer diameter D1 is the small outer diameter. The outer diameter D2 is the large outer diameter. The outer diameter D3 is the first outer diameter. The said ring surface thus forms from the circular area difference at the two outer diameters D2, D3.

In addition to the two working ports A, B, one or two bypass ports A1, B1 can also be provided. Thus, a method according to DE 10 2006 012 733 A1 realizes which means of check valves to the tank drain flowing hydraulic fluid provides the Schwenkmotorversteller for pivoting movements.

• einem Zylinderkopf,
• einem Zylinderkopfdeckel,
• einer Zwischenplatte bzw. Zwischenbrille zwischen dem Zylinderkopf und dem Schwenkmotorversteller oder
• einem vor dem Schwenkmotorversteller angeordneten Deckel

befestigt. Die Verwendung bei einer dezentralen Anordnung ist von besonderem Vorteil, da dezentrale Hydraulikventile üblicherweise ein fest an das Hydraulikventil gekoppeltes elektromagnetisches Stellglied aufweisen. Ein solches elektromagnetisches Stellglied weist einen druckausgeglichenen Magnetanker auf. Zum Druckausgleich weist der Magnetanker eine Ausnehmung auf, die den Bewegungsraum vor dem Magnetanker mit dem Bewegungsraum hinter dem Magnetanker verbindet. Der Magnetanker bewegt sich in einem Ankerinnenraum, der an dem Tankabfluss des Hydraulikventils angeschlossen ist. Da von diesem Tankabfluss kein maßgeblicher Druck kommt, sind die Bewegungsräume frei von Druck und das Stellglied wird nicht vom Hydraulikventil weggedrückt. Demgegenüber würde ein Hydraulikventil mit einem Versorgungsanschluss an beiden axialen Enden - z.B. in der Reihenfolge P-B-T-A-P - die Bewegungsräume mit dem Versorgungsdruck beaufschlagen, so dass das Stellglied und das Hydraulikventil voneinander hinfort gedrückt würden. Damit vereinigt die erfindungsgemäße Ausführungsform als dezentrales Hydraulikventils die Vorteile:

• axial kurzer Bauraum des Hydraulikventils und
• kräftefreie Anbindung des Stellglieds.

The hydraulic valve does not have to be arranged as a central hydraulic valve radially inside the Schwenkmotorverstellers. The arrangement of the pressure medium connection P axially next to the working ports A, B instead of between the working ports A, B also brings advantages in an external or decentralized arrangement of the hydraulic valve. In such an external arrangement, the hydraulic valve is, for example, in

• a cylinder head,
• a cylinder head cover,
• an intermediate plate or intermediate glasses between the cylinder head and the Schwenkmotorversteller or
• a lid disposed in front of the Schwenkmotorversteller

attached. The use in a decentralized arrangement is of particular advantage, since decentralized hydraulic valves usually have a fixedly coupled to the hydraulic valve electromagnetic actuator. Such an electromagnetic actuator has a pressure balanced magnet armature. For pressure equalization, the armature has a recess which connects the movement space in front of the magnet armature with the movement space behind the magnet armature. The armature moves in an armature interior, which is connected to the tank drain of the hydraulic valve. Since there is no significant pressure from this tank drain, the movement spaces are free of pressure and the actuator is not pushed away from the hydraulic valve. In contrast, a hydraulic valve with a supply connection at both axial ends - for example in the order PBTAP - the movement spaces with the Apply supply pressure so that the actuator and the hydraulic valve would be pushed away from each other. Thus, the embodiment according to the invention as a decentralized hydraulic valve combines the advantages:

• axially short space of the hydraulic valve and
• force-free connection of the actuator.

The hollow piston is guided axially in the stepped bore. This bore can be incorporated in a particularly advantageous manner in the socket of a cartridge valve. However, the bore may also be arranged in a housing. In a particularly advantageous embodiment, the bore is incorporated directly into a central screw, which screws the rotor of the Schwenkmotorverstellers with the camshaft.

Further advantages of the invention will become apparent from the other claims, the description and the drawings.

The invention is explained in more detail below with reference to three exemplary embodiments.

• Fig. 1 in einer geschnittenen Darstellung einen Schwenkmotorversteller,
• Fig. 2 in einer geschnittenen Darstellung ein elektromagnetisches Stellglied eines Hydraulikventils, welches Anwendung in einem Schwenkmotorversteller findet und
• Fig. 3 in einer geschnittenen Darstellung ein Hydraulikventil, welches Anwendung bei einem Schwenkmotorversteller findet.

Showing:

• Fig. 1 in a sectional representation of a Schwenkmotorversteller,
• Fig. 2 in a sectional view of an electromagnetic actuator of a hydraulic valve, which finds application in a Schwenkmotorversteller and
• Fig. 3 in a sectional view of a hydraulic valve, which is used in a Schwenkmotorversteller.

With a Schwenkmotorversteller 14 according to Fig. 1 During operation of an internal combustion engine, the angular position on the camshaft 18 with respect to a Drive wheel 2 steplessly changed. By turning the camshaft 18, the opening and closing times of the gas exchange valves are shifted so that the engine brings its optimum performance at the respective speed. The Schwenkmotorversteller 14 has a cylindrical stator 1 which is rotatably connected to the drive wheel 2. In the exemplary embodiment, the drive wheel 2 is a sprocket over which a chain, not shown, is guided. The drive wheel 2 may also be a toothed belt wheel, via which a drive belt is guided as a drive element. About this drive element and the drive wheel 2, the stator 1 is drivingly connected to the crankshaft.

The stator 1 comprises a cylindrical stator base body 3, on the inside of which protrude webs 4 at equal intervals radially inwardly. Between adjacent webs 4 gaps 5 are formed, in which, via an in Fig. 2 shown in more detail centrally arranged hydraulic valve 12 controlled, pressure medium is introduced. Between adjacent webs 4 protrude wings 6, which project radially outward from a cylindrical rotor hub 7 of a rotor 8. These wings 6 divide the spaces 5 between the webs 4 each in two pressure chambers 9 and 10. The one pressure chamber 9 is associated with the adjustment in the direction of "early", whereas the other pressure chamber is associated with the adjustment in the "late" direction.

The webs 4 lie with their end faces sealingly against the outer circumferential surface of the rotor hub 7. The wings 6 in turn lie with their end faces sealingly against the cylindrical inner wall of the stator main body 3.

The rotor 8 is rotatably connected to the camshaft 18. In order to change the angular position between the camshaft 18 and the drive wheel 2, the rotor 8 is rotated relative to the stator 1. For this purpose, depending on the desired direction of rotation, the pressure medium in the pressure chambers 9 or 10 is pressurized, while the respective other pressure chambers 10 or 9 are relieved to the tank T. In order to pivot the rotor 8 counterclockwise relative to the stator 1 into the illustrated position, the hydraulic valve 12 forms an annular first annular rotor channel 19 in the rotor hub 7 is pressurized. From this first rotor channel 19 then further channels 11 lead into the pressure chambers 10. This first rotor channel 19 is associated with the first working port A. On the other hand, in order to pivot the rotor 8 clockwise, the hydraulic valve 12 pressurizes a second annular rotor channel 20 in the rotor hub 7, opening into the channels 13. This second rotor channel 20 is associated with the second working port B. These two rotor channels 19, 20 are axially spaced relative to a central axis 22 to each other, so that these in the plane of Fig. 1 lie hidden behind each other.

The Schwenkmotorverstellers 14 is placed on the designed as a hollow tube 16 built camshaft 18th For this purpose, the rotor 8 is placed on the camshaft 18. The hollow tube 16 has bores 23, 24, which connect the two working ports A, B associated rotor channels 19, 20 hydraulically with transverse bores 25, 26 in a bushing 27 of the hydraulic valve 12.

Thus, the Schwenkmotorversteller 14 by means of in Fig. 2 pivotable hydraulic valve 12 visible.

The central bore 28 within the bushing 27 has two different inner diameters 29, 30, which are transferred via a conical bore portion 31 into each other. The first transverse bore 25 of the bush 27 is derived from the larger inner diameter 29 and is thus assigned to the first working port A. The second transverse bore 26 of the bush 27 is derived from the smaller inner diameter 30 and is thus associated with the second working port B. Within the sleeve 27, a hollow piston 32 is displaceable. For this purpose, the hollow piston 32 has a contact surface 33 terminating this end face for an electromagnetic actuator 34. A plunger 35 of the electromagnetic actuator 34 is located centrally on this contact surface 33 at. At the other end face is a helical compression spring 36 on the hollow piston 32, which is supported on a support member of the bushing 27. The helical compression spring 36 rests against an end face 81 of the hollow piston 32. Thus, the Hollow piston 32 from the electromagnetic actuator 34 against a spring force of the helical compression spring 36 axially relative to the sleeve 27 slidably. The hollow piston 32 has an inlet channel 37 and an outlet channel 38. The inlet channel 37 is a cavity 80 within the hollow piston 32 and leads via the central bore 28 in the region of the small inner diameter 30 to an axially inserted into the socket 27 pressure medium connection P. However, the drain channel 38 leads to the tank drain T. The demarcation of the inlet channel 37 from Outflow channel 38 via a wall 40 within the hollow piston 32, which extends substantially obliquely. This oblique extension divides four control edges 41, 42, 43, 44. These control edges 41, 42, 43, 44 are arranged radially from the hollow piston 32 hinfort extending annular webs 45, 46. The two annular webs 45, 46 are axially spaced from each other. The closer to the actuator 34 annular web 45 has a lateral surface 47 with a large outer diameter D2 and is guided in the central bore 28 in the region of the larger inner diameter 29. The actuator 34 further standing annular web 46 has a lateral surface 48 with a small outer diameter D1 and is guided in the central bore 28 in the region of the small inner diameter 30. The two control edges 42, 43 define the mutually facing sides of the annular webs 45, 46. The two other control edges 41, 44 limit the sides facing away from each other of the annular webs 45, 46th

The inlet channel 37 leads, however, to the two mutually remote control edges 41, 44. Thus, the two mutually facing control edges 42, 43 are trailing edges, whereas the control edges facing away 41st , 44 forming inlet edges.

In the in Fig. 2 illustrated locking middle position of the hydraulic valve 12, the two mutually facing control edges 42, 43 a relatively large overlap 50, 51 with the socket 27 on. By contrast, in this locking center position of the hydraulic valve 12, the two control edges 41, 44 remote from each other have no overlap with the bushing 27. Thus, according to the principle of Trace edge control ensures that the rotor 8 is braced relative to the stator 1 in a certain angular position. The principle of the edge control is in the DE 198 23 619 A1 explained in more detail.

• die Mantelfläche 47 mit dem großen Außendurchmesser D2 im axialen Bereich des einen Arbeitsanschlusses A und
• die Mantelfläche 48 mit einem kleineren Außendurchmesser im axialen Bereich des anderen Arbeitsanschlusses B.

A first outer diameter D3 of the hollow piston 32 is slidably tolerated in a bore portion 71 tolerated. This bore portion 71 is formed by a sleeve 64 which is fixedly connected to the sleeve 27. For this purpose, the sleeve 64 is pressed into the socket 27. The first outer diameter D3 of the hollow piston 32 essentially corresponds to a first inner diameter 70 of the sleeve 64. The first outer diameter D3 is followed in the direction pointing axially from the actuator 34 to the pressure medium connection P.

• the lateral surface 47 with the large outer diameter D2 in the axial region of the one working port A and
• the lateral surface 48 with a smaller outer diameter in the axial region of the other working connection B.

The hollow piston 32 is pressure-balanced in a particularly advantageous manner, so that position control of the Schwenkmotorverstellers 14 can be made of high quality. For this purpose, the forces acting on the hollow piston 32 axial forces cancel. That is, the left-acting force F1 in the drawing is equal to the right-acting force F2 regardless of the supply pressure at the pressure medium port P.

On the one hand, a supply pressure introduced from the pressure medium connection P into the inlet channel 37 of the hollow piston 32 lies on the entire surface of a projected circular surface 60. This circular surface 60 is formed by the smaller outer diameter D1 of the hollow piston 32. The circular surface 60 is projected from an end face 81 and the obliquely extending wall 40 onto the plane perpendicular to the central axis 22. Thus, the force acting on the actuator 34 F1. The opposite force F2 acts via the supply pressure at an annular surface 61 which forms from the circular surface 83 at the large outer diameter D2 minus a circular area 99 at the first outer diameter D3. As in the bottom Half of the drawing Fig. 2 can be seen, formed from this difference, the annular surface 61 as projected onto the plane perpendicular to the central axis 22 surface.

The smaller inner diameter 30 of the bushing 27 corresponds essentially to the small outer diameter D1 on the lateral surface 48. Thus, the small outer diameter D1 essentially defines the circular surface 60, which multiplied by the pressure at the pressure medium connection P in the one axial direction - in the drawing to the left - Actual force F1 pretends. The force F2 acting in the opposite direction is determined by an annular surface 61 which forms on the end face 63 of the sleeve 64 pressed into the bushing 27. This end face 63 lies opposite an end face 62 of the annular web 45.

The inlet channel 37 thus establishes the hydraulic connection between the circular surface 60 and the annular surface 61. The circular surface 60 and the annular surface 61 have the same size for pressure equalization. For a freedom of forces is achieved, which facilitates the control of the position of the actuator, in particular in the illustrated middle position. From this middle position or blocking middle position is regulated. Short-term small movements from the locking center position and back into this pivoting the rotor 8 in a clockwise or counterclockwise direction.

• der Druckmittelanschluss P,
• der eine Arbeitsanschluss B,
• der andere Arbeitsanschluss A und schließlich
• der Tankablauf T.

In Fig. 2 the connection order or port order PBAT is shown. Consequently follow each other:

• the pressure medium connection P,
• the one working connection B,
• the other work connection A and finally
• the tank drain T.

The supply of the supply connection P takes place axially.

In the Fig. 2 are still two other alternative ways of connection shown in dashed lines. Thus, the outflow to the tank instead of the tank drain T can be designed as a tank drain T1. In this case, this tank drain T1 is arranged axially between the two working ports A, B. In that case, the drain channel 38 to the tank outlet T also be closed according to the dashed line 87.

Also, it is alternatively possible to move the axial connections radially by a recess in the sleeve or in the hollow piston 32 is provided. This is illustrated by means of the supply connection P1 or the tank discharge T3.

In an alternative embodiment, the shoulder is not realized with the sleeve 64. Instead, another construction may be provided to enable mountability. For example, the sleeve 27 may be designed as a two-part screwed component, which has a one-piece paragraph instead of the sleeve 64. The gland then ensures the mountability of the

Instead of the socket can also be provided a bore within a housing.

In an alternative embodiment, the pressure medium connection P is not introduced axially into the bushing 27. Instead, the pressure medium connection P is introduced radially. For this purpose, for example, a transverse bore or recess may be provided in the wall of the bush 27. This transverse bore is then in the axial region of the helical compression spring 36th

The hydraulic valve can be designed according to the embodiment as a central hydraulic valve, which is also referred to as the central valve. But it can also be designed as a decentralized hydraulic valve. The hydraulic valve can also be designed as a cartridge hydraulic valve.

Fig. 3 shows for a decentralized hydraulic valve 112 with only partially shown hydraulic part 113, the electromagnetic actuator 134. This actuator 134 is internally pressure balanced. Consequently, a channel 120 leads from the tank outlet T to an annular space 136 within the actuator 134 in which the armature magnet 135 is arranged axially displaceable. The armature magnet 135 has a recess 137, as a result of which the armature magnet 135 is pressure balanced. Since no significant pressure from the tank drain T, the movement spaces of the armature magnet 135 are free of pressure and the actuator 134 is not pushed by the hydraulic part 113 hinfort.

On the other hand, a hydraulic part of a hydraulic valve would have a supply port P at both axial ends - e.g. in order P-B-T-A-P - pressurize the movement spaces with the supply pressure so that the actuator and the hydraulic valve would be pushed away from each other.

The camshaft may for example be a built camshaft.

The tank drains do not have to be arranged on the front side. So it is also possible to run the tank drains as radial holes in the piston and / or in the socket.

The hydraulic valve can be designed as a central valve within the rotor hub or within a central recess of the camshaft. In this case, the camshaft may be a built camshaft, in which the cams are placed on a pipe.

An electromagnetic actuator for a central valve must not be designed according to Fig. 2 , In particular, it is possible to prevent problems due to the rotational movement of the contact surface 33 relative to the plunger 35 in that the plunger 35 abuts rounded only selectively on the contact surface 33. It is also possible to let the plunger 35 end with a roller bearing ball, which bears against the contact surface 33. Such an electromagnetic actuator with a roller bearing ball for a central valve, for example, the DE 10 2010 060 180 A1 ,

Alternatively, it is also possible to carry out the hydraulic valve as a remote valve or as a decentralized hydraulic valve.

• nur dem Schwenkmotorversteller oder
• dem Schwenkmotorversteller und weiteren Hydraulikaggregaten

zugeordnet sein. In diesem Fall kann die Fluid-Förderpumpe beispielsweise als Flügelzellenpumpe ausgeführt sein. Alternativ sind Zahnradpumpen, Radialkolbenpumpen und Mondsichelpumpen möglich.The pressure for the adjustment of the Schwenkmotorverstellers can come from a fluid feed pump. This fluid feed pump may be, in particular, the oil pump for supplying lubricant to the internal combustion engine. However, if a relatively high pressure is to be applied for a high adjustment speed of the swivel motor adjuster, the fluid feed pump can

• only the Schwenkmotorversteller or
• the Schwenkmotorversteller and other hydraulic units

be assigned. In this case, the fluid feed pump may be designed, for example, as a vane pump. Alternatively, gear pumps, radial piston pumps and crescent pumps are possible.

It goes without saying that the designation of the two working connections with the letters A or B is arbitrary and interchangeable.

The piston can be made of metal or plastic. The plastic is produced by injection molding. When using a plastic and a fiber reinforced plastic is advantageous, as this already in the unpublished DE 10 2007 026 831 is shown.

To make the piston, a tool with sliders can be used.

The described embodiments are only exemplary embodiments. A combination of the described features for different embodiments is also possible. Further, in particular not described features of the device parts belonging to the invention are to be taken from the geometries of the device parts shown in the drawings.

Claims (11)

1. Oscillating motor adjuster (14) with a hydraulic valve (12) which has a stepped bore (28) with working connections (A, B) emerging therefrom, wherein a pressure-equalized hollow piston (32) is axially displaceable within the bore (28) and is displaceable with a first outside diameter (D3) within a bore section (71) in a sealing manner with tolerance, wherein the hollow piston (32) has, adjacently, following said first outside diameter (D3)

   - a lateral surface (47) with a large outside diameter (D2) and

   - a lateral surface (48) with a small outside diameter (D1) in the region of a working connection (B),

   wherein a supply pressure introduced into a cavity (80) of the hollow piston (32) is applied firstly to a projected circular surface (60), which is formed by the small outside diameter (D1), such that a force (F1) is effective in an axial direction, whereas the supply pressure is applied secondly to a projected annular surface (61) which is formed from the large outside diameter (D2) minus the first outside diameter (D3).
2. Oscillating motor adjuster (14) with a hydraulic valve (12) according to patent Claim 1, characterized in that the hollow piston (32) has the lateral surface (47) with the large outside diameter (D2) in the axial region of the one working connection (A), wherein an inlet edge (41 or 44) and an outlet edge (42 or 43) emerge in each case from the two lateral surfaces (47, 48), wherein the two inlet edges (41, 44) face away from each other and the outlet edges (42, 43) face each other.
3. Oscillating motor adjuster (14) with a hydraulic valve (12) according to patent Claim 1 or 2, characterized in that the supply pressure is extensively applied to the projected circular surface (60).
4. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of the preceding patent claims, characterized in that the circular surface (60) is identical to the annular surface (61).
5. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of the preceding patent claims, characterized in that the two working connections (B, A) follow the pressure medium connection (P) which is followed by the tank outlet (T).
6. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of patent Claims 1 to 4, characterized in that the pressure medium connection (P) is followed by the one working connection (B) which is followed by a tank outlet (T1) which is followed by the other working connection (A).
7. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of the preceding patent claims, characterized in that a sleeve (64) is provided on the bore section (71) in order to produce an inside diameter (70) for the first outside diameter (D3), said sleeve being inserted into the bore (28) in a manner fixed in terms of movement, and therefore the hollow piston (32) is insertable into the bore (28) temporally before the sleeve (64) is fitted.
8. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of the preceding patent claims, characterized in that the delimitation of an inlet duct (37) from an outlet duct (38) within the hollow piston (32) takes place within the hollow piston (32) via a wall (40) which extends substantially obliquely, wherein said oblique extent divides up four control edges (41, 42, 43, 44) which are arranged on annular webs (45, 46) extending radially away from the hollow piston (32), wherein the annular web (45) which is closer to the actuator (34) has a lateral surface (47) with a large outside diameter (67), wherein said annular web (45) is guided in the central bore (28) in the region of a large inside diameter (29), wherein the annular web (46) further away from the actuator (34) has a lateral surface (48) with a small outside diameter (D1) and is guided in the central bore (28) in the region of the small inside diameter (30).
9. Oscillating motor adjuster (14) with a hydraulic valve (12) according to patent Claim 5 or 6, characterized in that the hydraulic valve (12) is designed as a central valve within a rotor hub (7), wherein the supply pressure is supplied to the hollow piston (32) axially by an assembled cam shaft designed as a hollow tube (16).
10. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of patent Claims 1 to 8, characterized in that the hydraulic valve (112) is designed as a decentral hydraulic valve (112), the electromagnetic actuator (134) of which has a magnetic armature (135) with a recess (137) for internal pressure equalization.
11. Oscillating motor adjuster (14) with a hydraulic valve (12) according to one of the preceding patent claims, characterized in that the small outside diameter is four times a constant (K), wherein the large outside diameter is five times the constant (K), wherein the first outside diameter is three times the constant (K).

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