阅读说明：本技术 具有由外部执行器定位且包括凹槽的阀芯的用于控制凸轮相位器的油控制阀 (Oil control valve for controlling a cam phaser with a spool positioned by an external actuator and including a groove ) 是由 丹尼尔·斯坦霍普 于 2018-09-18 设计创作，主要内容包括：一种用于内燃机的凸轮相位器的油控制阀，其中阀芯由外部致动器定位。该阀包括阀芯组件，该阀芯组件包括能够在中心开口中轴向地移动的阀芯，并且在阀芯中存在至少一个凹槽。当打开时，该凹槽显著地增加了通过液压阀的流体流量。通过控制凹槽的尺寸和位置，可以控制流体流量的量。通过控制阀芯中的孔的尺寸，可以进一步控制流体流量。与不存在至少一个凹槽的情况相比，可归因于凹槽的流体流量的增加可为至少50％、100％或甚至200％。(An oil control valve for a cam phaser of an internal combustion engine in which a spool is positioned by an external actuator. The valve includes a spool assembly including a spool axially movable in a central opening and there is at least one groove in the spool. When open, the groove significantly increases the fluid flow through the hydraulic valve. By controlling the size and location of the grooves, the amount of fluid flow can be controlled. By controlling the size of the orifice in the valve spool, fluid flow can be further controlled. The increase in fluid flow attributable to the grooves may be at least 50%, 100%, or even 200% as compared to the absence of the at least one groove.)

1. A hydraulic valve for a cam phaser, comprising:

a valve cartridge assembly including a valve cartridge axially movable in a central opening of a valve housing; and

at least one groove on the outside of the valve core,

wherein the valve core assembly has at least a first position, a second position corresponding to the retaining position, and a third position,

wherein when the valve core assembly is in the first position or the third position, fluid flows through the hydraulic valve, and

wherein the at least one groove substantially increases fluid flow through the hydraulic valve when the at least one groove is opened in the first position or the third position or both the first position and the third position.

2. The hydraulic valve of claim 1, wherein the spool assembly includes an integrally disposed check valve tube and check valve disc.

3. The hydraulic valve of claim 1, wherein the hydraulic valve is pressure balanced.

4. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve when the at least one groove is open only in the first position.

5. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve when the at least one groove is open only in the third position.

6. The hydraulic valve of claim 1, wherein the at least one groove substantially increases a fluid flow rate through the hydraulic valve when the at least one groove is opened in the first and third positions.

7. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve whenever a spool strokes into the first position.

8. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve whenever the spool strokes into the third position.

9. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve after a spool stroke travels a predetermined distance in the first position.

10. The hydraulic valve of claim 1, wherein the at least one groove substantially increases fluid flow through the hydraulic valve after a spool stroke travels a predetermined distance in the third position.

11. The hydraulic valve of claim 1, wherein the at least one groove is uniform.

12. The hydraulic valve of claim 1, wherein the at least one groove has a smaller groove portion and a larger groove portion.

13. The hydraulic valve of claim 1, wherein the at least one groove increases fluid flow by at least 50% as compared to an absence of the at least one groove.

14. The hydraulic valve of claim 1, wherein the at least one groove increases fluid flow by at least 100% as compared to an absence of the at least one groove.

15. The hydraulic valve of claim 1, wherein the at least one groove increases fluid flow by at least 200% as compared to an absence of the at least one groove.

16. The hydraulic valve of claim 1, wherein the spool includes a plurality of bores each having the same size, the plurality of bores merging into the at least one groove.

17. The hydraulic valve of claim 1, wherein the spool includes at least two differently sized bores that merge into the at least one groove.

18. A hydraulic valve for a cam phaser, comprising:

a valve cartridge assembly including a valve cartridge axially movable in a central opening of a valve housing; and

first and second check valves axially disposed in the spool, the first and second check valves preventing hydraulic fluid flowing through the spool assembly from inadvertently flowing out of the interior space of the spool assembly in first and second flows through the first and second openings of the spool associated with the first and second operating connections, respectively;

wherein the valve core assembly has at least a first position, a second position and a third position,

wherein when the spool assembly is in the first position, the hydraulic fluid flows from the first operating joint to the second operating joint,

wherein when the valve spool assembly is in the second position, the hydraulic fluid does not flow between the first and second operating joints,

wherein when the spool assembly is in the third position, the hydraulic fluid flows from the second operating joint to the first operating joint,

wherein the first and second operating joints open and close according to the position of the spool, an

Wherein the check valve is axially movable on the supply tube of the cartridge assembly and has an opposite opening direction.

19. The hydraulic valve of claim 18, wherein the first check valve abuts against a recess of the spool and the second check valve abuts against a check valve disc.

20. The hydraulic valve of claim 19, wherein the check valve disc is fixed to an end of the supply tube.

21. The hydraulic valve of claim 19, wherein the check valve disc and the supply tube are integrally provided.

22. The hydraulic valve as set forth in claim 18,

wherein the valve element comprises a plurality of bores which merge into at least one groove on the outside of the valve element, and

wherein the at least one groove substantially increases fluid flow through the hydraulic valve when the at least one groove is opened in the first position or the third position or both the first position and the third position.

23. The hydraulic valve of claim 22, wherein the spool includes a plurality of bores each having the same size.

24. The hydraulic valve of claim 22, wherein the spool includes a plurality of apertures having at least two different sizes.

25. The hydraulic valve of claim 22, wherein the at least one groove is offset from the bore.

Technical Field

The present invention relates to an oil control valve for a cam phaser for an internal combustion engine in which a spool is positioned by an external actuator and the spool has a groove.

Background

Hydraulic valves for cam phasers of internal combustion engines are well known in the art. The hydraulic valve includes a piston that is axially movable in a housing of the hydraulic valve and that controls the hydraulic load of the cam phaser. There are many different configurations of desired hydraulic valves and a new original design is typically required for each new desired hydraulic valve. Accordingly, there is a need in the art to reduce the need for the original design when designing new hydraulic valves.

Disclosure of Invention

It is an object of the present invention to provide a hydraulic valve for a cam phaser including a spool assembly including a spool axially movable in a central opening of a valve housing and at least one groove on an outside of the spool. The valve core assembly has at least a first position, a second position corresponding to the retained position, and a third position, and fluid flows through the hydraulic valve when the valve core assembly is in the first position or the third position. Additional positions therebetween are possible. The at least one groove substantially increases a fluid flow rate through the hydraulic valve when the at least one groove is opened in the first position or the third position or both the first position and the third position. The valve core assembly may include a check valve tube and a check valve disc provided in one piece. The hydraulic valve may be pressure balanced. The at least one recess may substantially increase the fluid flow through the hydraulic valve when the at least one recess is open in only the first position or only the third position, but not both positions. The at least one groove may substantially increase fluid flow through the hydraulic valve once the spool stroke enters the first and/or third positions, or may do so after the spool stroke travels a predetermined distance in the first and/or third positions. The at least one groove may be uniform or may have a smaller groove portion and a larger groove portion. The at least one groove increases fluid flow by at least 50%, 100%, or even 200% as compared to the absence of the at least one groove. The valve core may include a plurality of holes of the same size, or may include a plurality of holes having at least two different sizes.

It is another object of the present invention to provide a hydraulic valve for a cam phaser including a spool assembly including a spool axially movable in a central opening of a valve housing. The spool assembly has first and second check valves axially disposed within the spool that prevent hydraulic fluid flowing through the spool assembly from inadvertently flowing out of the interior space of the spool assembly in first and second flows through the first and second openings of the spool associated with the first and second operating joints, respectively. The spool assembly has at least a first position, a second position, and a third position. When the spool assembly is in the first position, hydraulic fluid can flow from the first operating joint to the second operating joint, when the spool assembly is in the second position, hydraulic fluid does not flow between the first operating joint and the second operating joint, and when the spool assembly is in the third position, hydraulic fluid can flow from the second operating joint to the first operating joint. The operating joint and the second operating joint open and close according to the position of the spool. The check valve is axially movable on the supply tube of the cartridge assembly and has an opposite opening direction. The first check valve may abut against the recess of the spool and the second check valve may abut against the check valve disc. The check valve disc may be secured to the end of the supply tube. The check valve disc and the supply pipe may be provided in one piece. The spool may include a plurality of apertures incorporated into at least one groove on an outside of the spool, wherein the at least one groove substantially increases fluid flow through the hydraulic valve when the at least one groove is opened in the first position or the third position or both the first and third positions. The valve core may include a plurality of holes each having the same size. The valve core may include a plurality of apertures having at least two different sizes. The at least one recess may be offset from the aperture.

Drawings

Further advantages, features and details of the invention can be taken from the following description of an advantageous embodiment and the drawings. The features and combinations of features set forth in the foregoing description, as well as the features and combinations of features set forth and illustrated in the accompanying drawings individually, may be used not only in the combination set forth individually, but in other combinations or alone without departing from the spirit and scope of the invention. The same reference numerals are used to denote identical or functionally equivalent elements. For purposes of clarity, possible elements have not been designated with reference numbers in all of the figures, but have not lost their association, wherein:

FIG. 1 illustrates an exemplary embodiment of an oil control valve assembly of the present invention;

FIG. 2 illustrates an assembled view of another exemplary embodiment of an oil control valve for a cam phaser of an internal combustion engine of the present invention;

FIG. 3 illustrates an exemplary embodiment of a prior art valve cartridge wherein openings in the valve cartridge meter oil flow;

FIG. 4 illustrates a second exemplary embodiment of a prior art valve cartridge, wherein an opening in the valve cartridge meters oil flow;

FIG. 5 illustrates a first exemplary embodiment of a valve spool, wherein an opening in the valve spool meters oil flow;

FIG. 6 shows a second exemplary embodiment of a valve cartridge similar to the valve cartridge of FIG. 5, but with openings of different sizes;

FIG. 7 illustrates another embodiment of the oil control valve assembly of the present invention having 0mm travel (home position);

FIG. 8 shows the oil control valve according to FIG. 7 with 1.5mm travel (neutral or hold position);

fig. 9 shows the oil control valve according to fig. 7 with 3mm travel (end position);

FIG. 10 shows a graph of flow rate versus spool travel for a spool having a hole but no groove, such as the spool of FIG. 3;

FIG. 11 shows a graph of flow rate versus spool travel for a spool having a bore and a groove starting with the bore diameter, such as the spool of FIG. 4;

FIG. 12 shows a graph of flow rate versus spool travel for a spool having a bore and a groove starting 0.8mm behind the bore opening, such as the spool of FIG. 5;

FIG. 13 shows a graph of flow rate versus spool travel for a spool having fewer orifices and a groove that begins 0.5mm behind the orifice opening, such as the spool of FIG. 6;

FIG. 14 shows a flow aperture in a housing;

FIG. 15 shows a small flow area;

FIG. 16 illustrates an increased flow area corresponding to a location where a groove is exposed to increase flow;

FIG. 17 shows a flow hole in the valve core;

FIG. 18 shows the aperture edge at the port edge;

FIG. 19 illustrates the increased flow area; and

fig. 20 illustrates an example valve core assembly having a groove offset from the bore.

Detailed Description

The present invention relates to an oil control valve for a cam phaser for an internal combustion engine in which a spool is positioned by an external actuator and has a groove. In the prior art, metering of the flow from the supply channel to the control channel is achieved by opening a port on the drilled channel hole. When the spool moves and the port begins to open, only a small area of the bore is uncovered to allow oil to flow. This is important in cam phaser oil control valves where the intermediate position is used to hold the phaser position and a small flow is required on either side of the hold position (either advance or retard) to compensate for leakage. When fast phaser movement is desired, the additional spool travel exposes a larger area and increases the flow. However, unlike the prior art, the present invention uses drilled access holes to meter the flow near the holding location and further places the notch into a run that allows for increased flow for fast phaser movement. Advantageously, the oil control valve is pressure balanced. Advantageously, the oil control valve may include a check valve tube and a check valve disc provided in one piece.

FIG. 1 illustrates an exemplary embodiment of an oil control valve 100 of the present invention. The oil control valve 100 includes a center valve housing 10, a spring 12, a calibration cap 14, a spring 16, a check valve 18, a flow disc 20, a supply filter 22, a snap ring 24, a spool assembly 26, a spool 30, a first check valve 32, a second check valve 33, a supply tube 34, and a check valve disc 40, and a spring 38. The plate check valves 32, 33 are arranged axially in the valve cartridge 30 and are axially movable on the supply pipe 34 and have opposite opening directions. They abut against the recesses of the valve spool 30 and the check-valve disc 40. The supply pipe 34 extends through the inner space 21 of the spool 30, and the right end of the supply pipe 34 is positioned in the recess of the spool 30. Check-valve disc 40 is secured to the left end of supply tube 34, which includes a radial supply opening 41 into between check valves 32, 33. The valve housing 10 has a stepped bore with working (operating) connections a, B projecting therefrom, wherein the pressure-balanced hollow piston 30 is axially displaceable within the bore and is sealingly movable with tolerance within the bore portion by a first outer diameter D3. The hollow piston 30 has, next to said first outer diameter D3, a side surface with a large outer diameter D2 and a side surface with a small outer diameter Dl. The supply pressure introduced into the cavity of the hollow piston 30 is first applied to the protruding circular surface formed by the small outer diameter Dl, so that the force F1 is effective in the axial direction. The supply pressure is secondly applied to the protruding annular surface formed by the large outer diameter D2 minus the first outer diameter D3, so that the force F2 acts in the opposite axial direction. The hollow piston 30 is pressure balanced in that the circular surface is at least almost identical to the annular surface. Pressure balanced, also referred to as pressure compensated, hollow piston 30 is further discussed in U.S. patent 9739182, which is incorporated herein by reference in its entirety.

The first and second check valves 32, 33 prevent hydraulic fluid flowing through the spool assembly from inadvertently exiting the interior space 21 of the spool assembly in a first flow through the first opening 42 of the spool 30 and a second flow through the second opening 43 of the spool 30 associated with the first and second operating joints a, B, respectively. The openings 42, 43 may be drilled holes.

The valve 100 includes at least a first position (start position), a second position (intermediate or hold position), and a third position (end position) as shown in fig. 1. In the starting position, the second operating connection B is connected to the fluid supply P through the supply pipe 34, the radial supply and third openings 41, 44 of the spool 30 and the second check valve 33, resulting in a cam torque recirculation of oil from a to B. To hydraulically supply the cam phasers, a plurality of taps A, B, P, T1 (located in the center of the housing 10), T2 (located on the left end) are provided. In the neutral position shown, spool lands 45, 46 block a and B to maintain the cam phaser position. In the intermediate position there is no recirculation or exhaust. In the end position, the first operative connection a is connected to the fluid supply P via the supply pipe 34, the radial supply and third openings 41, 44 of the spool 30 and the first plate check valve 32, resulting in a cam torque recirculation of oil from B to a. Fig. 2 shows an assembled view of another embodiment of an oil control valve 100 for a cam phaser for an internal combustion engine. The oil control valve includes a center valve housing 10, a spring 12, a calibration cap 14, a spring 16, a check valve 18, a flow disc 20, a feed filter 22, a snap ring 24, a cartridge assembly 26, a cartridge 30, a check valve 32, a check valve 33, a supply tube 34, and a flow disc 35, a catch 36, and a spring 38. The valve cartridge assembly 26 or the valve cartridge 30, or both, include one or more grooves 50 on the outside of the valve cartridge 30. The plate check valves 32, 33 are arranged axially in the valve spool 30 and have opposite opening directions. They may alternatively rest against a groove in the valve spool 30, the flow disc 35 or a separate check valve disc (not shown). The first and second openings 42, 43 of the spool 30 merge into the grooves 50, which allows for increased fluid flow when one of the grooves 50 is open in the first or first position of the valve 100.

Fig. 3 shows an exemplary embodiment of a prior art valve spool 30 in which openings 42, 43 in the valve spool meter the oil flow.

Fig. 4 shows a second exemplary embodiment of a prior art valve spool 30 in which orifices (also referred to as openings) 42, 43 in the spool meter the oil flow. The spool 30 of fig. 4 has improved oil flow compared to that provided by the spool 30 of fig. 3, but the improved oil flow is at the expense of control at the hold position.

Fig. 5 shows a first exemplary embodiment of the spool 30, wherein the openings 42, 43 in the spool 30 meter the oil flow. The valve spool of fig. 5 includes a groove 50 that allows increased oil flow when the valve spool 30 travels sufficiently to open the groove 50 and allow additional oil flow. The valve spool 30 provides good control of retention similar to the valve spool 30 of fig. 3 and provides a high flow rate similar to the valve spool 30 of fig. 4 once the valve spool travels sufficiently to open the groove 50. As can be seen, the groove 50 is offset from the openings (drilled holes) 42, 43. These grooves 50 allow for increased oil flow rate and may also be referred to as high flow grooves 50. By selecting the size of the groove 50, the rate of flow increase per millimeter of travel of the spool 30 can be controlled. The larger the size of the groove 50, the greater the increase in flow rate per millimeter of travel of the spool 30. These high flow rate grooves 50 are different from other grooves that have been incorporated into the valve spool. For example, a groove for contaminant removal would not provide the additional oil flow provided by the groove 50 of the present invention.

Fig. 6 shows a second exemplary embodiment of the valve cartridge 30 similar to the valve cartridge 30 of fig. 5, but with the openings 42, 43 having different sizes.

The relationship of flow to travel around the hold position can be set by controlling the size and number of apertures 42, 43 at the edges. Thus, the oil flow provided by the spool 30 of fig. 5 around the hold position is less than the oil flow provided by the spool 30 of fig. 6 because some of the openings of fig. 6 are smaller than those of fig. 5.

Fig. 7 shows an oil control valve 100 very similar to the valve 100 according to fig. 1. In contrast to fig. 1, supply tube 34 and check-valve disc 40 are provided in one piece. This simplifies manufacturing and reduces the number of parts. In the starting position with 0mm travel, the second operating joint B is connected to the fluid supply P via the supply pipe 34, the radial supply opening 41 and the third opening 44 of the spool 30, and the second check valve 33, resulting in cam torque recirculation of oil from a to B. The first operating connection a is additionally connected to a tank connection T1. To hydraulically supply the cam phasers, a plurality of taps A, B, P, T1 (located in the center of the housing 10), T2 (located at the left end) are provided.

Fig. 8 shows the oil control valve 100 with 1.5mm travel (neutral or hold position). In the neutral position, spool lands 45, 46 block a and B to maintain the cam phaser position. In the intermediate position there is no recirculation or exhaust.

Fig. 9 shows the oil control valve 100 with 3mm travel (end position). In the end position, the first plate check valve 32 causes cam torque recirculation of oil from B to a. The second operating connection B is additionally connected to a tank connection T2.

The openings 42, 43 of the spool 30 may merge into the grooves 50, which allows an increased fluid flow when one of the grooves 50 is open in the first or first position of the valve 100 according to the embodiment shown in fig. 5 or 6.

FIG. 10 is a graph of flow rate versus spool travel for a spool 30 having orifices 42, 43 but no grooves, such as the spool 30 of FIG. 3.

FIG. 11 is a graph of flow rate versus spool travel for a spool 30 having orifices 42, 43 and a groove 50 beginning with an orifice diameter, such as the spool 30 of FIG. 4. The grooves 50 greatly increase the flow rate. Note that the rate of increase in flow rate of the spool movement is greatly increased.

FIG. 12 is a graph of flow rate versus spool travel for a spool 30, such as the spool 30 of FIG. 5, having orifices 42, 43 and a groove that begins 0.8mm behind the orifice opening.

Here, the flow rate substantially matches that of fig. 10, which does not include the groove 50, until 0.8mm from the hole, the groove opens and the flow increases.

Fig. 13 is a graph of flow rate versus spool travel for a spool 30, such as the spool 30 of fig. 6, having fewer orifices and a groove 50 that begins 0.5mm behind the orifice opening.

Here, since there are fewer holes than in fig. 10, the flow rate decreases. Once the spool moves 0.5mm from the orifice, the groove 50 opens and the flow increases.

The flow rates from the orifice openings 42, 43 and the flow rate from the groove 50 can be considered to be the total flow rate. The increase in flow per millimeter of spool travel (where the groove 50 is open) is typically a significant fraction of the total flow increase for a given spool travel where the groove is open. In other words, the flow rate increase in the case where the groove 50 is opened is significantly increased as compared to the case where the groove 50 is not opened. Advantageously, the flow increase from the groove 50 is at least 50% of the flow increase provided by the orifice openings 42, 43, with even more for some embodiments. For example, the groove 50 may provide at least 100%, or at least 200%, or even more, as compared to the increase in flow from the aperture 302.

Fig. 14 shows the flow openings 47 in the housing 48.

Fig. 15 shows a small flow area. In the prior art device and the present invention, a small flow area occurs without the grooves 50 being exposed to increase flow.

Fig. 16 shows the increased flow area, which corresponds to the location where the groove 50 is exposed to increase flow.

Fig. 17 shows the flow hole 43 in the spool 30.

Fig. 18 shows the hole edge of the hole 43 at the port edge of the second operating joint B.

Fig. 19 shows the increased flow area of the holes 43.

Fig. 20 illustrates an example valve core assembly 26 similar to the valve 100 according to fig. 7. In contrast to fig. 7, the openings 42, 43 of the spool 30 may merge into the grooves 50, which allows for an increased fluid flow when one of the grooves 50 is open in the first or first position of the valve 100. According to the groove 50 shown in fig. 5, the groove 50 is offset from the openings 42, 43. The flow rate is reduced when only the edges of the openings 42, 43 are open. As the spool 30 moves and exposes the groove 50, the flow rate increases. The flow around the center provides good control to maintain a fixed phaser position. Uncovering the recess 50 increases the flow when it is desired to move the phaser quickly from one position to another. Supply tube 34 and check-valve disc 40 are provided as one piece. This simplifies manufacturing, reduces leakage, and improves the life of the oil control valve 100.

Although several embodiments of the present invention and their advantages have been described in detail, it should be understood that changes, substitutions, variations, alterations, adaptations, variations, substitutions and alterations can be made therein without departing from the teachings of the invention, the spirit and scope of which is set forth in the following claims.