Control valve for cam phaser and method for mounting the control valve

Abstract

A control valve for a cam phaser of an internal combustion engine, the control valve including a cylindrical housing, including a first operating connection, a second operating connection, a supply connection, and a tank drain connection configured to drain a hydraulic fluid; a control piston device, including a control piston, a supply tube, a first check valve and a second check valve enabling cam torque recirculation, wherein the control piston device is arranged in the housing and axially movable by an actuator, wherein the first check valve is configured with a first disc portion and a second disc portion and the second check valve is configured with a third disc portion and a fourth disc portion and the first check valves and the second check valve are arranged offset from each other by a compression coil spring.

Claims

1. A control valve for a cam phaser of an internal combustion engine, the control valve comprising: a cylindrical housing, including a first operating connection, a second operating connection, a supply connection, and a tank drain connection configured to drain a hydraulic fluid; a control piston device, including a control piston, a supply tube, a first check valve and a second check valve enabling cam torque recirculation, wherein the control piston device is arranged in the cylindrical housing and axially movable by an actuator, wherein the first check valve is configured with a first disc portion and a second disc portion and the second check valve is configured with a third disc portion and a fourth disc portion and the first check valve and the second check valve are arranged offset from each other by a compression coil spring so that a control chamber is formed between the first disc portion and the third disc portion, wherein the second disc portion and the fourth disc portion are arranged axially movable on the supply tube, wherein the supply tube is configured with stop elements that limit an axial movement of the first check valve and the second check valve in a direction towards the control chamber, wherein the supply tube is configured so that the second disc portion and the fourth disc portion are slidable onto the supply tube in an axial direction, wherein the compression coil spring is arranged between the first disc portion and the third disc portion and ends of the compression coil spring are guided by axial disc projections of the first disc portion and the third disc portion, and wherein the axial disc projections protrude into an inside of the compression coil spring and are configured to limit a radial movement of the compression coil spring by contacting the inside of the compression coil spring.

2. The control valve according to claim 1, wherein the first check valve and the second check valve are made from a synthetic material or from aluminum.

3. The control valve according to claim 1, wherein the stop elements are configured as larger diameter portions of the supply tube.

4. The control valve according to claim 1, wherein the first disc portion and the third disc portion are applied with respective outer edges in a sealing manner to a reduced diameter of the control piston and to a check valve flow cup, and wherein the check valve flow cup is arranged in the control piston.

5. The control valve according to claim 1, wherein the supply tube includes at least one inlet opening to the control chamber, wherein the at least one inlet opening is arranged so that the hydraulic fluid is fed to the control chamber centrally and symmetrically between the first check valve and the second check valve.

6. The control valve according to claim 5, wherein the supply tube is configured with a hollow cylinder which includes the at least one inlet opening to the control chamber and a connection opening that connects with the supply connection.

7. The control valve according to claim 1, wherein the control piston device is movable into a first control position, a second control position and a third control position, wherein the first operating connection is closed by the first disc portion of the first check valve for the hydraulic fluid flowing from the control chamber in the first control position, wherein the hydraulic fluid flowing from the first operating connection into the control chamber and to the second operating connection is enabled by a check function of the first check valve, wherein the first operating connection and the second operating connection are closed in the second control position, and wherein the second operating connection is closed by the third disc portion of the second check valve for a fluid from the control chamber in the third control position, and wherein a flow of fluid from the second operating connection into the control chamber and to the first operating connection is enabled by a check function of the second check valve.

8. The control valve according to claim 1, wherein the first check valve and the second check valve are axially arranged in the control piston and include opposite opening directions.

9. The control valve according to claim 1, wherein the control valve is configured with a supply connection non-return valve and a flow disc, and wherein the flow disc includes a circular opening along a center axis and the non-return valve includes openings in an outer section.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Additional advantages of the invention can be derived from the description and the drawing figures. The invention is subsequently described in more detail based on embodiments with reference to drawing figures, wherein:

(2) FIG. 1 illustrates a longitudinal sectional view of a first embodiment of a control valve according to the invention;

(3) FIG. 2 illustrates an enlarged section of the longitudinal sectional view of the control piston device of the control valve according to FIG. 1;

(4) FIG. 3 illustrates an perspective view of the control valve according to FIG. 1;

(5) FIG. 4 illustrates an perspective view of the control piston device according to FIG. 2;

(6) FIG. 5 illustrates an perspective view of the non-return valve and the flow disc of the control valve according to FIG. 1;

(7) FIG. 6 illustrates the non-return valve according to FIG. 5;

(8) FIG. 7 illustrates the flow disc according to FIG. 5;

(9) FIG. 8 illustrates a longitudinal sectional view of the control valve according to FIG. 1 with the control piston device in a first position;

(10) FIG. 9 illustrates a longitudinal sectional view of the control valve according to FIG. 1 with the control piston device in a second position;

(11) FIG. 10 illustrates a central longitudinal sectional view of the control valve according to FIG. 1 with the control piston device in a third position;

(12) FIG. 11 illustrates a symbol view of the control valve according to FIG. 1;

(13) FIG. 12 a longitudinal sectional view of a second embodiment of a control valve according to the invention.

DETAILED DESCRIPTION OF THE INVENTION

(14) A control valve that is illustrated in FIGS. 1-12 is used to adjust a path of a fluid flow and resulting therefrom a phase orientation of a cam phaser or of its rotor.

(15) FIG. 1 illustrates a first embodiment of a control valve 1 with a cylindrical housing 2 that is configured herein as a central bolt. The housing 2 includes a head side 3 and an insertion side 4, wherein a hexagonal head 5 is arranged at the head side 3 and an external thread 6 is arranged at the insertion side 4. Furthermore the housing 2 includes numerous openings that are provided as first operating connections A, second operating connections B, supply connection P and tank drain connections T. Thus, the opening at the insertion side 4 is a supply connection P. The openings that are arranged at or in the housing 2 in a radially circumferential manner in a respective hole series 7, 8, 9. Starting from the insertion side 4 the openings in the first hole row 7 are tank drain connections T with openings 63, in the second hole row 8 the openings 64 are first operating connections A and in the third hole row 9 the openings 65 are second operating connections B. A calibration cap 10 protrudes from the opening at the insertion side 4 wherein a supply filter 11 is arranged in the calibration cap 10 and retained in the calibration cap 10 by a safety ring 12.

(16) The control valve 1 controls a cam phaser and attaches it at the cam shaft. The attachment is performed by threading the housing 2 that is configured as a central bolt and by the hexagonal head 5 arranged at the housing 2 and by the external thread 6. The controlling is performed by the connections A, B, P and T. Thus, a fluid is introduced into the control valve 1 by the supply connection P. The operating connections A and B and fluid, flowing out either through the operating connections A or the operating connections B, facilitates respectively controlling one respective operating connection of the two operating connections or phase arrangements of the cam phaser. The tank drain connection T is only used for draining superfluous fluid.

(17) The control valve 1 also includes a flow disc 13, a supply connection non-return valve 14, a non-return valve spring 15, a calibration spring 16 and last not least a control piston device 17 according to the invention.

(18) The supply connection non-return valve 14 is held against the flow disc 13 by the non-return valve spring 15. The non-return valve 14 opens when the force of the supply pressure acting on the disc 13 is greater than the spring force and the force of the pressure acting on the non-return valve 14. FIGS. 5-7 illustrate that the flow disc 13 includes a circular opening 41 along a center axis of the flow disc 13, whereas non-return valve 14 includes openings 42 in an outer section, so that opening 41 of the flow disc 13 and the openings 42 of the non-return valve 14 do not overlap in a closed state. This configuration allows an improved response of the non-return valve 14 and improved flow from P due to one larger opening 41 along the center axis. Pressure loss can be reduced further.

(19) The control piston device 17 includes a control piston 18, a first check valve 20, a second check valve 21, a supply tube 22 and a check valve flow cup 19.

(20) The control piston 18 includes a mounting opening 23 on the head side 3 and a supply spout portion 24 with a supply opening 25 on the insertion side 4. Additionally the control piston 18 like the housing 2 in FIG. 1 also has three hole rows with openings, wherein the hole rows are configured as a fourth hole row 26, a fifth hole row 27 and a sixth hole row 28. Starting from the insertion side 4 the openings in the first hole row 26 are first operating pass through openings 29 (also called A1), in the fifth hole row 27 central pass through openings 30 and in the sixth hole row 28 second operating pass through openings 31 (also called B1).

(21) The check valves 20, 21, which enable cam torque recirculation and which are best shown in FIG. 2 showing an enlarged control piston device 17 of the control valve 1 of FIG. 1, are configured with a first disc portion 32, 33, a second disc portion 37, 38 and a spring 34 that is thus configured as a compression coil spring. Thus, the first disc portion 32 and the second disc portion 37 forms the first check valve 20 and the first disc portion 33 and the second disc portion 38 forms the second check valve 21. Thus, a respective outer edge 35, 36 of the first disc portion 32, 33 is arranged at the first discs portions 32, 33, which can be configured in the non-illustrated embodiment with additional radial seals or seal elements at the outer edges 35, 36. As can be seen from FIG. 2 the outer edges 35, 36 are biased against a reduced diameter 47 of the control piston 18 and the check valve flow cup 19, which is fixedly arranged in the control piston 18 at the head side 3.

(22) Inlet openings 44 are arranged at the hollow supply tube 22 in a radially circumferential manner. Additionally the supply tube 22 terminates on the insertion side 4 with a connection opening 45.

(23) Additionally a control chamber 46 is visible that is formed during the assembly and arranged within the control piston 18 between the check valves 20, 21 and which is penetrated by the compression coil spring 34. Thus, the control chamber 46 is connected in a fluid conducting manner by the central pass through openings 30 with a portion outside of the control piston 18 and connected by the inlet openings 44 with the supply tube 22 in a fluid conducting manner. Thus the supply tube 22 is applied with its connection opening 45 from an inside or from the head side 3 in a form locking manner to the supply spout portion 24 of the control valve 1.

(24) The second disc portions 37, 38 are axially movable on the supply tube 22, wherein the supply tube 22 is configured with stop elements 50, 51 to limit an axially movement of the check valves 20, 21 in the direction of the control chamber 46. Thus the control valve 1 according to the invention is configured very short or compact in the axial direction which saves space in the joint arrangement with the cam phaser and provides space for new functional components as required. It can advantageously be ensured that the supply connection P remains open during a cam torque recirculation function (CTR).

(25) Furthermore the stop elements 50, 51 are advantageously configured as one or two larger diameter portions of the supply tube 22. Thus, the CTR function with a best reaction is ensured easily and cost-effective.

(26) The compression coil spring 34 is arranged between the first disc portions 32, 33 and ends of the spring 34 are guided by axial disc projections 39, 40, which connect the first disc portions 32, 33 with the second disc portions 37, 38 of the check valves 20, 21. This optimized design prevents the check valves 20, 21 and the spring 34 from tipping or wedging and prevents the check valves 20, 21 from wearing out.

(27) FIG. 3 and FIG. 4 illustrate perspective views of the control valve 1 and the control piston device 17.

(28) FIG. 8 illustrates a longitudinal sectional view of the control valve of FIG. 1 with the control piston device 17 in a first position 52. The position 52 is indicated by two arrows at the head side 3 of the control valve 1 that point towards each other with their arrow tips. Since the position 52 is a starting position no movement has occurred yet or the movement of the control piston device 17 in the housing 2 is 0 mm. The arrow tips are therefore illustrated contacting each other. Due to the position 52 three fluid flows 53, 54, 55 are possible in the control valve wherein the fluid flows are respectively indicated by dashed lines. The dashed lines are respectively configured with an arrow at one end in order to indicate the flow direction of the fluid flows 53, 54, 55. In particular a first fluid flow 53 runs from the supply connection P to the second operating connection B, a second fluid flow 54 runs from the first operating connection A to the second operating connection B, and a third fluid flow 55 runs from the first operating connection A to the radially arranged tank drain connection T. The reference numerals A, B, P and T are illustrated in FIG. 2 for the purpose of clarity only at ends of dashed lines representing the fluid flows 53, 54, 55 and/or at a respective corresponding opening at the housing 2. The mode of illustration used in FIG. 2 also applies for the subsequent FIGS. 3 and 4. Subsequently the exact paths of the fluid flows 53, 55 are described.

(29) The first fluid flow 53 runs from the supply connection P through the calibration cap 10 to the supply spout portion 24 of the control piston 18 and its supply opening 25. From the supply spout portion 24 the first fluid flow 53 runs through the connection opening 45 of the supply tube 22 into its hollow cylinder and subsequently through the inlet opening 44 into the control chamber 46. From the control chamber 46 the first fluid flow 53 runs through the central pass through openings 30 to the second operating connection B.

(30) The second fluid flow 54 runs from the first operating connection A through the first operating pass through openings 29 and the first check valve 20 into the control chamber 46. From the control chamber 46 the second fluid flow 54 runs together with the first fluid flow 53 through the central pass through openings 30 to the second operating connection B.

(31) The third fluid flow 55 that is a simple drain flow runs only from the first operating connection A in the housing 2 and the first operating pass through openings 29 out of the control piston 18 to the radially arranged tank drain connection T.

(32) In the illustrated first position 52 of the control piston device 17 the first operating connection A is closed by the first check valve 20 for a fluid that is fed from the control chamber 46. An exit of the fluid from the first operating connection A to the control chamber 46 and the second operating connection B by a check valve function of the first check valve 20, however is possible.

(33) FIG. 9 illustrates a longitudinal sectional view of the control valve of FIG. 1 with the control piston device 17 in a second position 56. In the second position 56 the control piston device 17 is arranged inserted a little further, thus in particular by 1.5 mm in a direction towards the insertion side 4 into the housing 2. Thus, there are no fluid conducting connections between the connections A, B, P and T. The two operating connections A, B are closed due to the axial position of the control piston 18. Thus no possible fluid flows are illustrated.

(34) FIG. 10 illustrates a central longitudinal sectional view of the control valve of FIG. 1 with the control piston device 17 in a third position 57. In the third position 57 the control piston device 17 is inserted a little bit further, in particular by an additional 1.5 mm or overall by 3 mm in a direction of the insertion side 4 into the housing 2. Due to the position 57, three fluid flows 58, 59, 60 are possible in the control valve which are designated herein as fourth fluid flow 58, fifth fluid flow 59 and sixth fluid flow 60. In particular the fourth fluid flow 58 runs in FIG. 7 from the supply connection P to the first operating connection A, the fifth fluid flow 59 runs from the second operating connection B to the first operating connection A and the sixth fluid flow 60 runs from the second operating connection B to the tank drain connection T arranged at the head side 3. Subsequently exact paths of the fluid flows 58, 59, 60 are described.

(35) The fourth fluid flow 58 runs from the supply connection P initially to the control chamber 46 like the first fluid flow 53 of FIG. 2. However, the fourth fluid flow 58 runs from the control chamber 46 through the central pass through openings 30 to the first operating connection A.

(36) The fifth fluid flow 59 runs from the second operating connection B through the second operating pass through openings 31 and through openings 61 of the check valve flow cup 19 and from there through the second check valve 21 into the control chamber 46. From the control chamber 46 the fifth fluid flow 59 runs together with the fourth fluid flow 58 through the central pass through openings 30 to the first operating connection A.

(37) The sixth fluid flow 60 is a simple drain flow and runs only from the second operating connection B and through the openings 31, 61 out of the control piston 18 to the tank drain connection T at the head side 3.

(38) In the illustrated third position of the control piston device 17 the second operating connection B is closed by the second check valve 21 for a fluid that is fed by the control chamber 46. However, an exit of fluid from the second operating connection B to the control chamber 46 and the first operating connection A is possible due to a check function of the second check valve 21.

(39) FIG. 11 illustrates a symbol view of the control valve 1 and the three control positions 52, 56, 57. The control valve 1 can be set in any position between 52 and 57. The various valve positions control the flow by changing the amount the holes are uncovered. Modifying the flow controls the speed of the relative position of the camshaft to the crankshaft as desired.

(40) FIG. 12 illustrates a second embodiment of a control valve 1 with a cylindrical housing 2 that is configured herein as a central bolt. It only differs from the first embodiment in the design of the check valve cup 19, in which an additional valve stem or bolt 62 is fixed. Furthermore the calibration cap 10 does not protrude from the opening at the insertion side 4.