DE102011000522A1 - Swivel motor adjuster for combustion engine, has sleeve arranged inside valve housing and displaced against spring force of spring relative to inner part that is rigidly supported at valve housing - Google Patents

Abstract

The adjuster (59) has two hydraulic valves i.e. central valves, coaxial to each other. A sleeve is arranged inside a valve housing. Inner parts are arranged inside the sleeve. A supply terminal is axially attached with two power ports to pivot the motor adjuster. Pivoting hydraulic fluid is loaded from one of the power ports to the other power port. The sleeve is displaced against spring force of a spring i.e. cup spring, relative to the inner part. The inner part is rigidly supported at the valve housing. The inner part is secured by an anti-twist plate.

Description

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

• – ein Ventilgehäuse,
• – eine innerhalb von diesem angeordnete Hülse und
• – ein innerhalb von diesem angeordnetes Innenteil

auf. Axial schließen sich dem Versorgungsanschluss zwei Arbeitsanschlüsse zum Verschwenken des Schwenkmotorverstellers an. Zum Verschwenken ist Hydraulikfluid von dem einen zu entlastenden Arbeitsanschluss an dem zu belastenden Arbeitsanschluss vorbei führbar. Dabei sind die Hülse und das Innenteil fest miteinander verbunden. Die Trennung in Hülse und Innenteil ist fertigungsbedingt. In weitere Ausführungsbeispielen in dieser DE 10 2005 041 393 A1 ist die Trennung in Hülse und Innenteil aufgehoben und das Bauteil als komplexes MIM-Bauteil einteilig gefertigt.From the DE 10 2005 041 393 A1 is already such a Schwenkmotorversteller known. In this case, the hydraulic valve is coaxial with each other

• A valve housing,
• - An arranged inside of this sleeve and
• - An inside of this arranged inside part

on. Axial close to the supply connection to two working connections for pivoting the Schwenkmotorverstellers. For pivoting hydraulic fluid from the one to be relieved work port on the work connection to be charged passable past. The sleeve and the inner part are firmly connected. The separation in sleeve and inner part is due to production. In further embodiments in this DE 10 2005 041 393 A1 the separation in the sleeve and inner part is canceled and the component is manufactured in one piece as a complex MIM component.

Also the DE 10 2005 052 481 A1 shows a central valve for a Schwenkmotorversteller. In this central valve also follow the two working ports A, B the oil supply port P, which in turn follows a single tank runoff T. For distributing the oil from the oil supply port P to the respective working port A or B, a displaceable by means of an actuator hollow piston is provided, which is supported on a helical compression spring.

Furthermore, from the DE 103 22 394 A1 a Schwenkmotorversteller known within which a hydraulic valve is provided.

The object of the invention is to provide a hydraulic valve - in particular central valve - which enables a connection sequence P-A-B in a compact design.

This object is achieved with the features of claim 1.

According to the invention, the sleeve is displaceable relative to the inner part against a spring force of a spring. The inner part, however, is axially rigidly supported on the valve housing.

The hydraulic valve according to the invention finds particular application as a central valve radially within a camshaft or within a rotor. However, it is also possible to arrange the hydraulic valve outside the rotor.

In a particularly advantageous manner, the metal injection molding method (MIM) find application. However, the complex geometry can also be created alternatively or additionally with holes and / or cutouts.

Claim 2 shows a particularly advantageous embodiment of the invention, wherein it is ensured by means of a rotation, that the inner part is in spite of not rotationally symmetrical configuration in a defined angular position to the sleeve. In this way, a supply channel coming from the supply connection and a tank discharge channel leading to the tank connection can be assigned to different openings in the sleeve.

Claim 3 shows an advantageous arrangement of the tank connection.

Claim 6 shows a possibility to compensate production-related Koaxialitätsfehler.

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

The invention is explained in more detail with reference to several embodiments.

Show

1 a Schwenkmotorversteller in a sectional plane perpendicular to the central axis,

2 a hydraulic valve inserted in the Schwenkmotorversteller in a longitudinal section along the central axis,

3 a section along line III-III of the hydraulic valve according to 2 .

4 a section along line IV-IV of the hydraulic valve according to 2 .

5 a section along line VV of the hydraulic valve according to 2 .

6 a section along line VI-VI of the hydraulic valve according to 2 .

7 the hydraulic valve off 2 partly cut out in a perspective view,

8th the hydraulic valve off 2 in a locked middle position,

9 the hydraulic valve off 2 in the completely disengaged state,

10 a detail from 7 in the area of a rotation and

11 the hydraulic valve in a second embodiment.

With a Schwenkmotorversteller 59 according to 1 is changed during operation of an internal combustion engine, the angular position of the camshaft. By turning the camshaft, the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine brings its optimal performance at the respective speed. The Schwenkmotorversteller allows a continuous adjustment of the camshaft relative to the crankshaft. The Schwenkmotorversteller has a cylindrical stator 1 on, the rotation with a drive wheel 2 connected is. In the embodiment, the drive wheel 2 a sprocket over which a chain, not shown, is guided. The drive wheel 2 but may also be a toothed belt, over which a drive belt is guided as a drive element. About this drive element and the drive wheel 2 is the stator 1 Driven with the crankshaft.

The stator 1 comprises a cylindrical stator base body 3 , on the inner side radially inwardly at equal intervals webs 4 protrude. Between neighboring bridges 4 become spaces 5 formed, into, over, a in 2 to 10 closer illustrated hydraulic valve 12 controlled, pressure medium is introduced. Between neighboring bridges 4 protrude wings 6 radially outward from a cylindrical rotor hub 7 a rotor 8th protrude. These wings 6 divide the spaces between 5 between the bridges 4 each in two pressure chambers 9 and 10 ,

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

The rotor 8th is rotatably connected to the camshaft, not shown. To the angular position of the camshaft relative to the drive wheel 2 to change, the rotor becomes 8th relative to the stator 1 turned. For this purpose, depending on the desired direction of rotation, the pressure medium in the pressure chambers 9 or 10 pressurized while each other's pressure chambers 10 or 9 be relieved to the tank. To the rotor 8th opposite the stator 1 to pivot counterclockwise in the position shown are from the hydraulic valve 12 radial bores 11 in the rotor hub 7 put under pressure. To the rotor 8th however, to pivot clockwise, are from the hydraulic valve 12 radial bores 14 in the rotor hub 7 put under pressure. These radial holes 14 lie with respect to a central axis 13 behind the first-mentioned radial holes 11 ,

2 shows the designed as a central valve hydraulic valve 12 , This hydraulic valve 12 can be operated by means of an electromagnetic actuator, not shown. For this purpose, this actuator has a plunger 27 on. The electromagnetic actuator is located in this 2 in the de-energized state.

The hydraulic valve 12 is in the drawing not shown mounted state in the rotor hub 7 used. In further alternative embodiments, not shown in the drawing, it is also possible to use the hydraulic valve 12 into the camshaft or a separate camshaft end piece and / or screw.

The radial bores 11 the rotor hub 7 thereby lead into an annular groove 15 of the hydraulic valve 12 , which forms a first working port A. This first working port A follows with respect to the central axis 13 axially a second working connection B. In an annular groove 16 This second working port B lead the radial bores 14 the rotor hub 7 ,

These two ring grooves 15 . 16 are in a bush-shaped valve housing 17 of the hydraulic valve 12 screwed. The supply port A is adjacent to a supply port P, which is also an annular groove 18 having. This supply connection P, in turn, follows the tank outlet T, which likewise has an annular groove 19 having.

Coaxial with and inside the valve body 17 is a sleeve 20 arranged. Inside this sleeve 20 is an interior part 21 arranged, which axially on the valve housing 17 is supported. This is the inner part 21 with its front end 22 on a reason 23 a blind hole 24 of the valve housing 17 at. Here is the inner part 21 permanently under the bias of a helical compression spring 25 which has a disk 26 on an axial securing ring 28 is supported. This axial securing ring 28 is in an annular groove of the valve body 17 used. This is the inner part 21 with de-energized actuator on the valve housing 17 supported.

The disc 26 is immobile by means of press fit with the sleeve 20 connected. The sleeve 20 is between the middle part as an inner part 21 and the housing 17 guided axially displaceable. The sleeve 20 has five axially mutually adjacent annular grooves 29 to 33 on.

The foremost - and thus first - annular groove 29 is assigned to the tank connection T. This is Hydraulic fluid from this annular groove 29 through T-holes 34 in the valve housing 17 can be discharged to the tank connection T. In this ring groove 34 is the hydraulic fluid from a tank drainage channel 39 conductive, located axially in the inner part 21 extends. This extends the tank drainage channel 39 offset parallel to the central axis 13 , The tank drainage channel 39 is open to the outside, leaving its outer wall from the sleeve 20 is formed. Outlets from this tank drainage channel 39 be from axially spaced tank openings 40 to 42 educated. It represents the frontmost tank opening 40 the drain to the foremost annular groove 29 ago. The middle tank opening 41 establishes the inflow from the first working port A. The rearmost tank opening 42 puts in an in 9 shown state the inflow from the second working port B ago. In the state according to 2 Thus, hydraulic fluid is discharged from the first working port A to the tank port T.

The tank connection T following - and thus second - annular groove 30 is assigned to the supply terminal P. This is hydraulic fluid from P-holes 35 in the valve housing 17 through the second annular groove 30 in a supply channel 38 introduced. From this supply channel 38 For example, the hydraulic fluid can be directed to either the first working port A or the second working port B. In the 2 In this case, the line is shown on the second working port B. In this case, the supply channel extends 38 axially in the inner part 21 parallel to the tank drainage channel 39 , This also extends the supply channel 38 offset parallel to the central axis 13 , The supply channel 38 opens on the tank drainage channel 39 opposite side, so that the outer wall of the sleeve 20 is formed. Outlets from this tank drainage channel 39 are of two axially spaced supply openings 43 . 44 educated. It represents the front supply opening 43 the inflow from the annular groove 30 which comes from the supply port P. The rear supply opening 44 makes the drain to the second working port B ago. in the state according to 9 represents the rear supply opening 44 the outflow to the first working port A ago.

Thus, hydraulic fluid from the supply port P to the one working port A and B can be performed, while the other working port B or A is relieved to the tank port T.

3 to 6 show cuts across the central axis 13 of the hydraulic valve 12 ,

The cut according to 3 passes through the center axis of the T-holes 34 , It can be seen that the tank drainage channel 39 axially to the tank port T runs, whereas the supply channel 38 not to the tank connection T is enough.

The cut according to 4 passes through the center axis of the P holes 35 , It can be seen that both the tank discharge channel 39 as well as the supply channel P in the region of the supply terminal P run side by side.

The cut according to 6 passes through the center axis of the A holes 36 , It can be seen that even in this area the tank drainage channel 39 and the supply channel P run side by side.

The cut according to 5 passes through the center axis of the B holes 37 , It can be seen that the tank drainage channel 39 extends axially to the second supply port B, whereas the supply channel 38 not to the tank connection T is enough.

7 shows the hydraulic valve 12 partially cut out in a perspective view. It is also the disc 26 it can be seen at which of the plunger, which is not shown in the drawing 27 is applied.

10 shows the sleeve 20 and the inner part 21 in the area around this disc 26 in a detail. Here is the inner part 21 opposite the sleeve 20 by means of an anti-twist device 45 secured. It can be seen that the sleeve 20 opposite the inner part 21 is secured against rotation. On the other hand, that is out of the sleeve 20 and the inner part 21 formed assembly rotatable relative to the valve housing 17 , For producing the anti-twist device 45 is the inner part 21 perpendicular to the central axis 13 with a cutout 46 provided so that two extensions 47 . 48 of the inner part 21 stay standing. Between these extensions 47 . 48 is the disc 26 used, which is thus against rotation in the circumferential direction of the extensions 47 . 48 supported. To record this disc 26 is the sleeve 20 at the rear end with an inside turn 49 provided, in which the disc 26 is pressed. Thus, the disc 26 rotatably in the sleeve 20 added.

8th shows in a representation analog 2 the hydraulic valve 12 , where the sleeve 20 located in a locking middle position. In this locking middle position is the sleeve 20 from the tappet, not shown 27 moved by this is partially disengaged. As a result, the rear annular groove 32 limiting ribs 50 . 51 brought in such a coincidence with the A-holes and B-holes, that the flow resistance of the inlet through Zuflussspalte to the two working ports A, B is smaller, than the drainage resistance through Abflusstspalte. This will be the wings 6 of the rotor 8th opposite the stator 1 clamped so that the Schwenkmotorversteller 59 is held in a defined angular position.

9 shows the hydraulic valve 12 when the plunger, not shown in the drawing 27 is completely disengaged. In this case, the first working port A is charged by the supply port P, whereas the second working port B is relieved against the tank port T.

11 shows an alternative embodiment of a hydraulic valve 52 , which can also be designed as a central valve. In contrast to the previous Ausführungsbelspiel the tank port T is axial. The hydraulic valve 52 is installed in a hollow camshaft, which is designed as a built camshaft. In this case, the hydraulic fluid coming from the tank connection T is discharged inside the hollow camshaft. In contrast to the first embodiment is a helical compression spring 53 at the front end of the sleeve 54 clamped. Here is the sleeve 54 elastic over the helical compression spring 53 and a spring plate 55 on an inner part 56 supported. Because of the spring plate 55 firmly on the inner part 56 is pressed, form the spring plate 55 and the inner part 56 an easy-to-assemble unit that latches against a ring bar 57 in a valve housing 58 can be pushed. This assembly is then fitted with an axial securing ring 60 secured, in an inner ring groove 61 of the valve housing 58 is used.

A supply channel 64 is shown in contrast to the previous embodiment above. This supply channel is constructive 64 the supply channel 39 of the previous embodiment is relatively similar. However, in contrast to the previous embodiment, a tank drainage channel 62 in the inner part 56 not openly executed. Instead, there is a radially aligned drainage hole 63 and the axially aligned tank drain T by means of an eccentrically arranged bore 67 connected with each other.

In the illustrated unshielded position of the sleeve 54 the second working port B is supplied from the supply port P with hydraulic pressure. From the first working port A, however, the hydraulic pressure via the tank discharge channel 62 discharged to tank connection T.

Will the sleeve 54 by means of an electromagnetic actuator relative to the inner part 56 against the spring force of the helical compression spring 53 shifted, then an overlap is reduced 65 until it is gone. Then a channel opens between the sleeve 54 and the inner part 56 , This channel leads from a tank opening 66 over the hole 67 to the drainage recess 63 , This allows the hydraulic fluid from B holes 68 over this channel to the tank opening 66 be relieved.

As a result of this described in the last paragraph axial displacement of the sleeve 54 Another channel is opened, so that one in the 11 apparent overlap 69 no longer exists. Because this overlap in the position according to 11 has blocked the inflow from the supply port P to the first working port A, is in shifted sleeve 54 the access to the first work port A free. Consequently, the first working port A is loaded with hydraulic pressure and in return the second working port B is relieved.

Analogously to the first embodiment, there are also in the hydraulic valve according to 11 a locking middle position in which the inner part 56 and the sleeve 54 are overlapping in such a way that the flow resistance of the inflow through Zuflussspalte to the two working ports A, B is smaller than the outflow resistance through Abflussungspalte.

For producing an anti-twist device 70 are also at the inner part 56 the actuator facing extensions 71 . 72 provided that a cutout 73 limit. In this cutout 73 becomes a slice 74 inserted during energization of the actuator, so that this disc along the extensions 71 . 71 pushes. In doing so, the disc can 74 be loosely inserted, as they - depending on the valve position - of the helical compression spring 53 either against the axial securing ring 60 or the ram of the actuator is tensioned. The disc is guided 74 in the raceway inside the sleeve 54 ,

In particular, the inner part according to the second embodiment may also be designed as an MIM component because of the complex geometry. In this case, instead of drilling 67 Also a channel can be made from a slider of the tool.

The listed in the first embodiment and the two working ports A, B associated supply port 44 can also be split, leaving two breakthroughs in the sleeve 20 are provided.

The rotation of both embodiments can be realized in different constructions. In particular, an extension may be sufficient instead of the two extensions. Likewise, more than two extensions are possible. It is also possible to carry out the extension as a central mandrel, on which the helical compression spring is guided. The extension may, however, rotationally fixed in a receptacle - for example, a slot - engage the disc.

At the hydraulic valve 52 According to the second embodiment, the tank drain can also on the other side - ie in the range of Actuator - be arranged. This is especially true when a chain drive to be lubricated instead of a dry toothed belt drives the camshaft.

The hydraulic valve according to both embodiments may be provided on the one hand with a thread and on the other hand with a screw head, so that forms a central screw as a central valve.

The valve housing according to both embodiments may also be a tubular portion of a built camshaft. In this case, an external thread can also be provided at the outside end of the valve housing or the camshaft. On this external thread then a nut is screwed, which braces the rotor of the Schwenkmotornockenwellenverstellers against a shoulder on the camshaft.

Instead of the helical compression spring can be provided as a spring, for example, a plate spring package.

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.

LIST OF REFERENCE NUMBERS

1

stator

2

drive wheel

3

stator base

4

Stege

5

interspaces

6

wing

7

rotor hub

8th

rotor

9

pressure chamber

10

pressure chamber

11

radial bores

12

hydraulic valve

13

central axis

14

radial bores

15

ring groove

16

ring groove

17

valve housing

18

ring groove

19

ring groove

20

shell

21

inner part

22

front

23

reason

24

blind

25

Helical compression spring

26

disc

27

tappet

28

axial securing

29

ring groove

30

ring groove

31

ring groove

32

ring groove

33

ring groove

34

T-bores

35

P-bores

36

A drilling

37

B-bores

38

supply channel

39

Tank drainage channel

40

tank opening

41

tank opening

42

tank opening

43

Treatment opening

44

Treatment opening

45

twist

46

countersink

47

extension

48

extension

49

recess

50

rib

51

rib

52

hydraulic valve

53

Helical compression spring

54

shell

55

spring plate

56

inner part

57

ring land

58

valve housing

59

Schwenkmotorversteller

60

axial securing

61

inner annular

62

Tank drainage channel

63

Abflussausnehmung

64

supply channel

65

coverage

66

tank opening

67

drilling

68

B-bores

69

coverage

70

twist

71

extension

72

extension

73

countersink

74

disc

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 102005041393 A1 [0002, 0002]
• DE 102005052481 A1 [0003]
• DE 10322394 A1 [0004]

Claims (10)

Schwenkmotorversteller ( 59 ), in which a hydraulic valve ( 12 . 52 ) coaxial with each other - a valve housing ( 17 . 58 ), - a sleeve arranged inside it ( 20 . 54 ) and - an inside part ( 21 . 56 ), wherein axially a supply connection (P) two working connections (A, B) for pivoting the Schwenkmotorverstellers ( 59 ), wherein for pivoting hydraulic fluid from the one to be relieved working port (B or A) on the work to be loaded port (A or B) is passable, characterized in that the sleeve ( 20 . 54 ) opposite the inner part ( 21 . 56 ) against a spring force of a spring ( 25 . 53 ) is displaceable, wherein the inner part ( 21 . 56 ) axially rigidly on the valve housing ( 17 . 58 ) is supported. Schwenkmotorversteller according to any one of the preceding claims, characterized in that the inner part ( 21 . 56 ) opposite the sleeve ( 20 . 54 ) by means of an anti-twist device ( 45 . 70 ) is secured. Schwenkmotorversteller according to claim 1 or 2, characterized in that axially outside the supply port (P) and the working ports (A, B), a tank port (T) is provided, to the hydraulic fluid from each to be relieved working port (A or B) is feasible , Schwenkmotorversteller according to claim 1, characterized in that the inner part ( 21 ) two radially outwardly open channels ( 38 . 39 ), which is of the angularly installed sleeve ( 20 ) are concealed in such a way that from the channel associated with the discharge ( 39 ) - one of the first working port (A) associated tank opening ( 41 ) in the sleeve ( 20 ) and - a second working port (B) associated tank opening ( 42 ) in the sleeve ( 20 ), whereas from the channel associated with the load ( 38 ) - a supply port (P) associated with supply port ( 43 ) in the sleeve ( 20 ) and - one of the two working ports (A, B) associated tank opening ( 44 ) in the sleeve ( 20 ) is provided. Schwenkmotorversteller according to claim 4, characterized in that of the discharge associated channel ( 39 ) a tank port (T) associated sleeve opening ( 40 ) goes off. Schwenkmotorversteller according to any one of the preceding claims, characterized in that the inner part ( 21 . 56 ) radial clearance relative to the valve housing ( 17 . 58 ), so that the inner part ( 21 . 56 ) opposite the sleeve ( 20 . 54 centered). Schwenkmotorversteller according to claim 2, characterized in that the rotation ( 45 . 70 ) at least one extension ( 47 . 48 ) which rotates with play in a receptacle of a sleeve insert ( 26 . 74 ) intervenes. Schwenkmotorversteller according to claim 7, characterized in that the spring ( 25 ) from the extension ( 47 . 48 ) to be led. Schwenkmotorversteller according to one of the claims 1 to 7, characterized in that the spring ( 53 ) on the one hand axially to a support region of the inner part ( 56 ) and on the other hand axially on the sleeve ( 54 ) is supported, so that the spring ( 53 ), the inner part ( 56 ) and the sleeve ( 54 ) form a preassemblable unit. Schwenkmotorversteller according to one of the claims 1 to 3 or 6 to 8, characterized in that the inner part ( 56 ) has an axial tank drain (T), which via an eccentric channel (T) ( 67 ) to a drainage recess ( 63 ), which discharges the hydraulic fluid from the working port (A or B) to be relieved.

Images