Hydraulic valve for a cam phaser

Abstract

A hydraulic valve for a cam phaser, the hydraulic valve comprising: a bushing including a piston that is movable in a bore along a longitudinal direction; a supply connection for feeding a hydraulic fluid; a first operating connection and a second operation connection; and a first tank drain connection and a second tank drain connection configured to drain the hydraulic fluid, wherein a first check valve is associated with the first operating connection and a second check valve is associated with the second operating connection, and the first operating connection and the second operating connection are connectable through at least one of the first check valve and the second check valve alternatively with each other or with the supply connection or with the first tank drain connection or with the second tank drain connection by moving the piston, wherein the hydraulic valve includes five switching positions,

Claims

1. A hydraulic valve for a cam phaser, the hydraulic valve comprising: a bushing including a piston that is movable in a bore along a longitudinal direction; a supply connection for feeding a hydraulic fluid; a first operating connection and a second operating connection; and a first tank drain connection and a second tank drain connection configured to drain the hydraulic fluid, wherein a first check valve is associated with the first operating connection and a second check valve is associated with the second operating connection, and the first operating connection and the second operating connection are connectable through at least one of the first check valve and the second check valve alternatively with each other or with the supply connection or with the first tank drain connection or with the second tank drain connection by moving the piston, wherein the hydraulic valve includes five switching positions, wherein the second operating connection is connected with the supply connection and the first operating connection is connected with the first tank drain connection in a first switching position of the piston and a fluid path from the first operating connection to the second operating connection is openable by the first check valve that is associated with the first operating connection under a pressure that exceeds a threshold value, wherein the second operating connection is connected with the supply connection and a connection between the first operating connection and the first tank drain connection is interrupted in a second switching position of the piston and a fluid path from the first operating connection to the second operating connection is openable by the first check valve that is associated with the first operating connection under a pressure that exceeds the threshold value, wherein a connection between the first operating connection, the second operating connection and the supply connection and the first tank drain connection and the second tank drain connection is interrupted in a third switching position of the piston which is positioned in a center position, wherein the first operating connection is connected with the supply connection and a connection between the second operating connection and the second tank drain connection is interrupted in a fourth switching position of the piston and a fluid path from the second operating connection to the first operating connection is openable by the second check valve that is associated with the second operating connection under a pressure that exceeds the threshold value, wherein the first operating connection is connected with the supply connection and the second operating connection is connected with the second tank drain connection in a fifth switching position of the piston and a fluid path from the second operating connection to the first operating connection is openable by the second check valve that is associated with the second operating connection under a pressure that exceeds the threshold value, wherein the connection between the first operating connection and the first tank drain connection in the first switching position is throttled by a first throttling cross section of a first annular tubular channel formed by a first outer circumferential surface of the piston and a first inner circumferential surface of the bore wherein the first throttling cross section is flowed through in the longitudinal direction, and wherein the connection between the second operating connection and the second tank drain connection in the fifth switching position is throttled by a second throttling cross section of a second annular tubular channel formed by a second outer circumferential surface of the piston and a second inner circumferential surface of the bore wherein the second throttling cross section is flowed through in the longitudinal direction.

2. The hydraulic valve according to claim 1, wherein the first operating connection is associated with the first check valve on an outside of the piston, and wherein the second operating connection is associated with the second check valve on the outside of the piston.

3. A cam phaser with the hydraulic valve according to claim 1, wherein the hydraulic valve is configured as a central valve.

4. A hydraulic valve for a cam phaser, the hydraulic valve comprising: a bushing including a piston that is movable in a bore along a longitudinal direction; a supply connection for feeding a hydraulic fluid; a first operating connection and a second operating connection; and a first tank drain connection and a second tank drain connection configured to drain the hydraulic fluid, wherein a first check valve is associated with the first operating connection and a second check valve is associated with the second operating connection, and the first operating connection and the second operating connection are connectable through at least one of the first check valve and the second check valve alternatively with each other or with the supply connection or with the first tank drain connection or with the second tank drain connection by moving the piston, wherein the hydraulic valve includes five switching positions, wherein the second operating connection is connected with the supply connection and the first operating connection is connected with the first tank drain connection in a first switching position of the piston and a fluid path from the first operating connection to the second operating connection is openable by the first check valve that is associated with the first operating connection under a pressure that exceeds a threshold value, wherein the second operating connection is connected with the supply connection and a connection between the first operating connection and the first tank drain connection is interrupted in a second switching position of the piston and a fluid path from the first operating connection to the second operating connection is openable by the first check valve that is associated with the first operating connection under a pressure that exceeds the threshold value, wherein a connection between the first operating connection, the second operating connection and the supply connection and the first tank drain connection and the second tank drain connection is interrupted in a third switching position of the piston which is positioned in a center position, wherein the first operating connection is connected with the supply connection and a connection between the second aerating connection and the second tank drain connection is interrupted in a fourth switching position of the piston and a fluid path from the second operating connection to the first operating connection is openable by the second check valve that is associated with the second operating connection under a pressure that exceeds the threshold value, wherein the first operating connection is connected with the supply connection and the second operating connection is connected with the second tank drain connection in a fifth switching position of the piston and a fluid path from the second operating connection to the first operating connection is openable by the second check valve that is associated with the second operating connection under a pressure that exceeds the threshold value, wherein the connection between the first operating connection and the first tank drain connection in the first switching position is throttled by a first throttling cross section of a first annular tubular channel formed by a first outer circumferential surface of the piston and a first inner circumferential surface of the bore wherein the first throttling cross section is flowed through in the longitudinal direction, and wherein the connection between the second operating connection and the second tank drain connection in the fifth switching position is throttled by a second throttling cross section of a second annular tubular channel formed by a second outer circumferential surface of the piston and a second inner circumferential surface of the bore wherein the second throttling cross section is flowed through in the longitudinal direction wherein the first check valve is arranged at a first piston attachment that envelops the piston and that is connected with the piston in a rigid manner, and wherein the second check valve is arranged at a second piston attachment that envelops the piston and that is connected with the piston in a rigid manner.

5. The hydraulic valve according to claim 4, wherein the first check valve is provided as a disc shaped closing element that is preloaded against the first piston attachment by a common compression spring, and wherein the second check valve is provided as a disc shaped closing element that is preloaded against the second piston attachment by the common compression spring.

6. The hydraulic valve according to claim 4, wherein the first piston attachment includes two first annular bars which respectively include two first control edges that respectively cooperate with two first recesses in the bushing, and wherein the second piston attachment includes two second annular bars which respectively include two second control edges that respectively cooperate with the two second recesses in the bushing.

7. The hydraulic valve according to claim 6, wherein the first control edges of the two first annular bars cooperate with the first operating connection configured as a radial recess in the bushing and with a first groove shaped recess in a portion of the bore hole, wherein the second control edges of the two second annular bars cooperate with the second operating connection configured as a radial recesses in the bushing and with a second groove shaped recess in the portion of the bore hole, wherein the first groove shaped recess is arranged in the axial direction between the first operating connection and the first tank drain connection, and wherein the second groove shaped recess is arranged in the axial direction between the second operating connection and the second tank drain connection.

8. The hydraulic valve according to claim 7, wherein a first distance between an outside diameter of an outer first annular bar of the two first annular bars and a groove base of the first groove-shaped recess is smaller in the first and the fifth switching position than a second distance between groove side surfaces of the first groove-shaped recess and a face of the outer first annular bar, and wherein the first distance between an outside diameter of an outer second annular bar of the two second annular bars and a groove base of the second groove-shaped recess is smaller in the first and the fifth switching position than the second distance between groove side surfaces of the second groove-shaped recess and a face of the outer second annular bar.

9. The hydraulic valve according to claim 8, wherein a ratio of the first distance to the second distance is greater than 1.4 to 1.

10. A hydraulic valve for a cam phaser, the hydraulic valve comprising: a bushing including a piston that is movable in a bore along a longitudinal direction between a first end position and a second end position; a supply connection for feeding a hydraulic fluid; a first operating connection and a second operating connection; and a first tank drain connection and a second tank drain connection configured to drain the hydraulic fluid, wherein the first operating connection and the second operating connection are flow connectable with each other by positioning the piston, wherein the piston includes a second outer annular bar that is arranged at a second axially exterior end of the piston and configured to completely close the second tank drain connection in the first end position, wherein the piston includes a first outer annular bar that is arranged at a first axially exterior end of the piston and configured to completely close the first tank drain connection in the second end position, and wherein a connection between the first operating connection and the first tank drain connection in the first end position is throttled by a first throttling cross section of a first annular tubular channel formed by a first outer circumferential surface of the piston and a first inner circumferential surface of the bore wherein the first throttling cross section is flowed through in the longitudinal direction and a connection between the second operating connection and the second tank drain connection in the second end position is throttled by a second throttling cross section of a second annular tubular channel formed by a second outer circumferential surface of the piston and a second inner circumferential surface of the bore wherein the second throttling cross section is flowed through in the longitudinal direction.

11. The hydraulic valve according to claim 10, wherein the bushing includes a first groove shaped recess and a second groove shaped recess in a portion of the bore, wherein the first groove shaped recess is associated with the first outer annular bar, and wherein the second groove shaped recess is associated with the second outer annular bar.

12. The hydraulic valve according to claim 11, wherein the first groove shaped recesses is arranged in the longitudinal direction between the first operating connection and the first tank drain connection, and wherein the second groove shaped recesses is arranged in the longitudinal direction between the second operating connection and the second tank drain connection.

13. The hydraulic valve according to claim 11, wherein a first distance between an outside diameter of the first outer annular bar of the two first annular bars and a groove base of the first groove-shaped recess is smaller in the first and the fifth switching position than a second distance between groove side surfaces of the first groove-shaped recess and a face of the outer first annular bar, and wherein the first distance between an outside diameter of an outer second annular bar of the two second annular bars and a groove base of the second groove-shaped recess is smaller in the first and the fifth switching position than the second distance between groove side surfaces of the second groove-shaped recess and a face of the outer second annular bar.

14. The hydraulic valve according to claim 10, wherein the piston includes a first inner annular bar and a second inner annular bar between the first outer annular bar and the second outer annular bar, and wherein the first inner annular bar is associated with the first operating connection and the second inner annular bar is associated with the second operating connection.

15. The hydraulic valve according to claim 14, wherein the piston is movable into a second position where the first tank drain connection is closed by the first outer annular bar and the second tank drain connection is closed by the second outer annular bar and the first operating connection is closed by the first inner annular bar and the second operating connection is closed by the second inner annular bar.

16. The hydraulic valve according to claim 10, wherein the piston is movable into a first position where first tank drain connection is closed by the first outer annular bar and the second tank drain connections is closed by the second outer annular bar, and wherein the second operating connection is in fluid communication with the supply connection and the first operating connection is in fluid communication with the second operating connection.

17. The hydraulic valve according to claim 10, wherein the piston is movable into a third position where the first tank drain connection is closed by the first outer annular bar and second tank drain connection is closed by the second outer annular bar, and the first operating connection is fluid flow connectable with the supply connection and the first operating connection is fluid flow connectable with the second operating connection.

18. The hydraulic valve according to claim 10 in the first end position, wherein the second tank drain connection of the second operating connection is completely closed by the second outer annular bar, wherein the first tank drain connection of the first operating connection is throttled without control edges by an annular gap between a first outer annular bar and a first groove shaped recess and the first operating connection is fluid flow connected with the second operating connection, and wherein the second operating connection is fluid flow connected with the supply connection.

19. The hydraulic valve according to claim 18 in the second end position, wherein the first tank drain connection of the first operating connection is completely closed by the first outer annular bar, wherein the second tank drain connection of the second operating connection is throttled without control edges by an annular gap between the second outer annular bar and the second groove shaped recess, wherein the first operating connection is fluid flow connected with the second operating connection, and wherein the first operating connection is fluid flow connected with the supply connection.

20. The hydraulic valve according to claim 18, wherein the piston is transferred between the first end position and the second end position in a continuously variable manner.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further advantages can be derived from the subsequent drawing description. The drawing figures illustrate an embodiment of the invention. The drawing figures, the description and the claims include several features in combination. A person skilled in the art will also view the features individually and will combine them into other useful combinations, wherein

(2) FIG. 1 illustrates a hydraulic valve configured to adjust a cam phaser according to an embodiment of the invention in a first switching position illustrated in a longitudinal sectional view;

(3) FIG. 2 illustrates the hydraulic valve according to FIG. 1 in a perspective view;

(4) FIG. 3 illustrates a switching diagram of the hydraulic valve according to FIG. 1;

(5) FIG. 4 illustrates a piston assembly of the hydraulic valve according to FIG. 1 in a perspective view;

(6) FIG. 5 illustrates a piston assembly according to FIG. 4 in a longitudinal sectional view;

(7) FIG. 6 illustrates the bushing of the hydraulic valve according to FIG. 1 in a longitudinal sectional view;

(8) FIG. 7 illustrates the characteristic diagram of the hydraulic valve according to FIG. 1; and

(9) FIG. 8 illustrates a blown-up detail of the hydraulic valve according to FIG. 1 in the first switching position in a longitudinal sectional view.

DETAILED DESCRIPTION OF THE INVENTION

(10) The subsequent description relates to valves as well as to hydraulic valves.

(11) In the drawing figures identical or like components are provided with identical reference numerals. The drawing figures merely show embodiments and do not limit the sprit and scope of the invention.

(12) FIG. 1 illustrates a hydraulic valve 1 for adjusting a non-illustrated cam phaser according to an embodiment of the invention in a first switching position 10 in a longitudinal sectional view. The hydraulic valve 1 includes a bushing 2 with a piston 4 that is movably arranged in a longitudinal direction L in a bore 3. The piston 4 is supported by a compression coil spring 5 at the bushing 2 or supported at a disc 6 that is arranged by a ring 7 in the bushing 2.

(13) The bushing 2 includes a supply connection P for feeding a hydraulic fluid and a first operating connection A and a second operating connection B that are respectively provided as a radial recess or plural radial recesses in the bushing in the sequence A-P-B. The supply connection P is protected against contamination by a screen 8 that is externally arranged at the bushing 2. Furthermore a band check valve 9 is arranged on an interior side of the bushing in a portion of the supply connection in order to prevent a flow back of hydraulic fluid in a direction towards the pump.

(14) The hydraulic valve 1 includes a first and a second tank drain connection T1, T2 for draining the hydraulic fluid wherein both connections are respectively configured axially. The tank drain connections T1 and T2 can be alternatively connected with each other by a center bore hole in the piston 4, so that the entire tank drain connection can be provided through a single tank drain connection T. The described tank drain connections T1 and T2 are interpreted in this case as a tank drain that is associated with the respective operating connection A or B, wherein both are run out of the valve by the only tank drain connection T.

(15) The first operating connection A and the second operating connection B are respectively associated with a check valve 15, 16 wherein the first operating connection A and the second operating connection B are alternatively connectable with each other and/or with the supply connection P and/or with one of the tank drain connections T1, T2 through at least one of the check valves 15, 16 by moving the piston 4.

(16) According to the invention the hydraulic valve 1 includes five switching positions 10-14, wherein the second operating connection B is connected through the bore hole 3 and an annular cavity 17 configured therein about the piston 4 with the supply connection P in the first switching position 10 of the piston 4 illustrated in FIG. 1 and the first operating connection A is connected through the bore hole 3 and another fluid path between a first piston attachment 18 and an interior of the bushing with the first tank drain connection T1 as will be described in more detail infra.

(17) A second outer annular bar 27 closes a second tank drain opening 22 completely on an opposite side of the piston 4. The first switching position can also be interpreted as a first end position of the piston 4.

(18) When a pressure applied to the first operating connection A exceeds a predetermined threshold value an additional fluid path is openable from the first operating connection A to the second operating connection B through the check valve 15 that is associated with the first operating connection A and the hydraulic fluid is passed through with fast phaser characteristics to the second operating connection B.

(19) In a second switching position 11 of the piston 4 the second operating connection B is connected with the supply connection P and a connection between the first operating connection A and the first tank drain connection T1 is interrupted by the piston attachment 18, in particular by a first outer annular bar 25, wherein the fluid path from the first operating connection A to the second operating connection B is openable by the check valve 15 that is associated with the first operating connection in this position. By the same token the tank drain connection T2 is closed by the annular bar 27 which is arranged at the piston attachment 19. In this position the hydraulic valve 1 has pure fast phaser characteristics. This second switching position can also be interpreted as a first position of the piston 4 within the control range of the fast phaser characteristics.

(20) In a third switching position 12 the piston 4 is positioned in a center position in which a connection between the operating connections A, B and the supply connection P and the tank drain connections T1, T2 is completely interrupted. This third switching position can also be interpreted as a second position of the piston 4 within the control range of the fast phaser characteristics.

(21) In a fourth switching positon 13 of the piston 4 the first operating connection A is connected with the supply connection P and a connection between the second operating connection B and the second tank drain connection T2 is interrupted by a second piston attachment 19, in particular by the second outer annular bar 27. A fluid path from the second operating connection B to the first operating connection A is operable by the check valve 16 that is associated with the second operating connection B through a pressure that exceeds a threshold value. By the same token the tank drain connection T1 is closed by the first outer annular bar 25 that is arranged at the piston attachment 18. This fourth switching position can also be interpreted as a third position of the piston 4 within the control range of the fast phaser characteristics.

(22) In a fifth switching positon the piston 4 is arranged in a second end position where the first operating connection A is connected by the bore hole 3 and an annular cavity 17 configured therein about the piston 4 with the supply connection P and the second operating connection B is connected through the bore hole 3 and a fluid path between the second piston attachment 19 and an inside of the bushing with the second tank drain connection T2 as will be described in more detail infra. On an opposite side of the piston 4 the first outer annular bar 25 completely closes the second tank drain connection T1. The fifth switching position can also be interpreted as a second end positon of the piston 4.

(23) When a pressure applied to a second operating connection B exceeds a particular threshold value, a fluid path from the second operating connection B to the first operating connection A is openable through the check valve 16 that is associated with the operating connection B.

(24) As evident in particular from FIG. 5 a respective check valve 15, 16 on the outside of the piston 4 is respectively associated with the first operating connection A and the second operating connection B. The check valves are respectively arranged at the piston attachments 18, 19 which envelop the piston 4 and which are connected in a rigid manner with the piston 4 e.g. by a press fit or by welding. This facilitates a compact configuration of the hydraulic valve and a simple and economical configuration of the piston assembly 20.

(25) The check valves 15, 16 are respectively provided as disc shaped closing elements which are preloaded by a common compression spring 21 against the piston attachments 18, 19 and thus close openings 22, 23 through which hydraulic fluid is conductible through the check valves 15, 16 starting with the pressure threshold value described supra. Thus, a preassembled piston assembly 20 can be advantageously provided which can be installed in the bushing 2 in a simple manner.

(26) Axial protrusions 46, 47 of the check valves 15, 16 facilitate a secure axial movement on the piston 4.

(27) The piston attachments 18, 19 respectively include two inner annular bars 24, 26 and the two outer annular bars 25, 27 which respectively include two control edges 28, 29, 30, 31, 32, 33, 34, 35 which cooperate with recesses in the bushing 2. Through the control edges 28-35 the volume flow of the hydraulic fluid can be controlled in an improved manner so that a significant increase of the adjustment speed, in particular in the upper engine speed range and improved force properties can be obtained.

(28) Thus, the control edges 28-35 of the inner and outer annular bars 24-27 cooperate with the operating connections A, B as radial recesses 38, 39 in the bushing 2 and with two groove shaped recesses 36, 37 in the portion of the bore hole 3, wherein the groove shaped recesses 36, 37 are arranged in the axial direction respectively between the operating connection A or B and the associated tank drain connection T1 or T2. The groove shaped recesses 36, 37 facilitate a position dependent opening and closing of the tank drain connections T1, T2 in cooperation with the control edges 28-30 and 33-35 in that a fluid path between the first operating connection A and the second operating connection B or to the first or second tank drain connection T1 or T2 is opened in the switching positions 10 and 14 between the outer annular bars 25 or 27 of the piston attachments 18 or 19 and an inside of the bushing, Thus, the first outer annular bar 25 of the first piston attachment 18 is in the portion of the groove shaped recess 36 in the first switching position 10 illustrated in FIG. 1 and a fluid flow between the first outer annular bar 25 and an inner side of the bushing is possible towards the tank drain connection T1. The second outer annular bar 27 of the second piston attachment 19, however, is outside of the groove-shaped recess 37, so that no fluid flow in a direction towards the tank drain connection T2 is possible through the closed control edges 34, 35.

(29) As evident from FIG. 8 which illustrates a blown-up detail of the hydraulic valve 1 in the first switching position 10 or in the first end position a distance A1 between an outer diameter 50 of the annular bar 25 and a groove base 51 of the groove-shaped recess 36 is smaller in the first end position than a distance A2 between groove-side surfaces 52, 53 of the groove-shaped recess 36 and faces 54, 55 of the annular bar 25. In order to provide a defined control of the tank drain in the direction towards T1, it is provided that the distance A1 is configured smaller than the distance A2 so that a ratio of A2 to A1 is greater than 1.4 to 1. This provides throttling without control edges or without an aperture for a fluid flow towards the tank drain connection T1 wherein the throttling is only constant in the end positions. Without control edges means that the throttling of the tank drain is facilitated almost exclusively by an annular surface between the annular bar 25 or 27 in the fifth switching position or the second end position and the groove-shaped recess 36 or 37 in the fifth switching position. The throttling is thus provided by the described annular gap and not by control edges provided at the bushing 2 and the outer annular bars 25, 27.

(30) In order to assure the hydraulic fixing of the cam phaser in the center position and the control quality of the hydraulic valve 1, the described configuration of the piston 4 and the bushing 2 outside of the end positions 10, 14 provides a rather high level of tank throttling. In the end positions, however, the respective pressure chambers can be emptied quickly.

(31) Thus, the described ratio between A2 and A1 facilitates reduced throttling of the fluid flow in a direction towards T1 in the illustrated first end position, wherein the reduced throttling can be used to empty the pressure chamber of the cam phaser that is associated with the operating connection A more quickly. This applies accordingly in the second end position 14 for the second outer annular bar 27 and the groove-shaped recess 37.

(32) The second outer outer annular bar 27 of the second piston attachment 19, however, is outside of the groove-shaped recess so that no fluid flow towards the tank drain connection T is possible through the closed control edges 34, 35.

(33) In the second and in the fourth switching position 11 and 13 of the hydraulic valve 1 the outer annular bars 25 and 27 are arranged outside of the groove-shaped recesses 36 and 37 so that no fluid flow is possible in a direction towards the tank drain connections T1 or T2 through the closed control edges 34, 35, 28, 29.

(34) FIG. 7 illustrates a characteristic volume flow diagram of the hydraulic valve 1 plotted over valve travel. The volume flow/valve travel characteristic diagram shows the resulting volume flow as a function of a position of the piston 4 (5 switching positions 10-14).

(35) The lines 40 and 40′ show the volume flow from A-B and the lines 41 and 41′ show the volume flow from P-B during the first and the second switching position 10 and 11.

(36) Approximately after half the total travel the center position 12 is reached where a connection between the operating connections A, and B and the supply connection P and the tank drain connections T1, T2 is completely interrupted.

(37) The lines 42 and 42′ show the volume flow from P to A and the lines 43 and 43′ show the volume flow from B to A in the fourth and the fifth switching position 13 and 14.

(38) It is evident from the lines 44 and 44′ that the connection from A to T1 is only open in the first switching position 10. The connection from B to T2 is only open in the fifth switching position 14 as illustrated by the lines 45 and 45′.