Patent Application
20140190435
The invention relates to a mechanism intermediate a crankshaft and a poppet-type intake or exhaust valve of an internal combustion engine for operating at least one such valve, wherein the mechanism varies the time period relative to the operating cycle of the engine, and more particularly, wherein the mechanism operably engages with a concentric camshaft to vary an angular position of one camshaft and an associated cam relative to another camshaft and associated cam.
The performance of an internal combustion engine can be improved by the use of dual camshafts, one to operate the intake valves of the various cylinders of the engine and the other to operate the exhaust valves. Typically, one of such camshafts is driven by the crankshaft of the engine, through a sprocket and chain drive or a belt drive, and the other of such camshafts is driven by the first, through a second sprocket and chain drive or a second belt drive. Alternatively, both of the camshafts can be driven by a single crankshaft powered chain drive or belt drive. A crankshaft can take power from the pistons to drive at least one transmission and at least one camshaft. Engine performance in an engine with dual camshafts can be further improved, in terms of idle quality, fuel economy, reduced emissions or increased torque, by changing the positional relationship of one of the camshafts, usually the camshaft which operates the intake valves of the engine, relative to the other camshaft and relative to the crankshaft, to thereby vary the timing of the engine in terms of the operation of intake valves relative to its exhaust valves or in terms of the operation of its valves relative to the position of the crankshaft.
As is conventional in the art, there can be one or more camshafts per engine. A camshaft can be driven by a belt, or a chain, or one or more gears, or another camshaft. One or more lobes can exist on a camshaft to push on one or more valves. A multiple camshaft engine typically has one camshaft for exhaust valves, one camshaft for intake valves. A “V” type engine usually has two camshafts (one for each bank) or four camshafts (intake and exhaust for each bank).
Variable cam timing (VCT) devices are generally known in the art, such as U.S. Pat. No. 7,841,311; U.S. Pat. No. 7,789,054; U.S. Pat. No. 7,270,096; U.S. Pat. No. 6,725,817; U.S. Pat. No. 6,244,230; and U.S. Published Application No. 2010/0050967. Known patents and publications disclose hydraulic couplings for single phaser assemblies in which an annular space is provided between a drive member concentrically surrounding a single driven member. The annular space is divided into segment-shaped or arcuate variable volume working chambers by one or more vanes extending radially inward from an inner surface of the drive member and one or more vanes extending radially outward from an outer surface of the single driven member. As hydraulic fluid is admitted into and expelled from the various chambers, the vanes rotate relative to one another and thereby vary the relative angular position of the drive member and the single driven member. Hydraulic couplings that use radial vanes to apply a tangentially acting force will be referred to herein as vane-type hydraulic couplings. Each of these prior known patents and publications appears to be suitable for its intended purpose. However, dual variable cam timing (VCT) devices with variable volume working chambers that are positioned axially spaced with respect to one another require additional axial space for the dual VCT assembly, while those dual VCT devices with variable volume working chambers that are positioned circumferentially spaced with respect to one another potentially suffer from reduced angular actuation distance of the associated rotor and vane, and can potentially suffer from reduced actuation force as a result of limited number of vanes, limited vane surface area, and limited actuation fluid chamber size. Therefore, it would be desirable to provide a configuration that requires less axial space for a dual VCT assembly. It would also be desirable to provide increased angular actuation distances for a dual VCT assembly. Further, it would be desirable to provide increased actuation force capabilities for a dual VCT assembly.
A dual variable cam timing phaser can be driven by power transferred from an engine crankshaft and delivered to a concentric camshaft having a radially inner shaft and a radially outer shaft for manipulating two sets of cams. The phaser can include a drive stator connectible for rotation with an engine crankshaft and two concentric driven rotors, each rotor connectible for rotation with a respective one shaft of the concentric camshaft supporting the corresponding two sets of cams. The drive stator and the driven rotors are all mounted for rotation about a common axis. The driven rotors are coupled for rotation with the drive stator by a plurality of radially stacked, (as opposed to axially stacked or circumferentially stacked), vane-type hydraulic couplings to enable the phase of the driven rotors to be adjusted independently of one another relative to the drive stator. It should be recognized that this configuration requires less axial space for a dual VCT assembly. Furthermore, this configuration can provide increased angular actuation distances for a dual VCT assembly. This configuration can also provide increased actuation force capabilities for a dual VCT assembly.
A dual variable cam timing phaser for an internal combustion engine having a concentric camshaft with a radially inner shaft and a radially outer shaft can include a stator having an axis of rotation. An outer rotor can be rotatable relative to the axis of rotation of the stator independently of the stator. A radially outer located vane-type hydraulic coupling can include a combination of an outer vane and cavity associated with the outer rotor to define first and second outer variable volume working chambers. An inner rotor can be rotatable relative to the axis of rotation of the stator independently of both the stator and the outer rotor. The inner rotor can be located radially inwardly within an innermost periphery of the outer rotor. A radially inner located vane-type hydraulic coupling can include a combination of an inner vane and cavity associated with the inner rotor to define first and second inner variable volume working chambers. A plurality of fluid passages can connect the first and second, outer and inner working chambers with respect to a source of pressurized fluid for facilitating angular phase orientation of the outer and inner rotors independently with respect to each other and independently with respect to the stator.
Other applications of the present invention will become apparent to those skilled in the art when the following description of the best mode contemplated for practicing the invention is read in conjunction with the accompanying drawings.
The description herein makes reference to the accompanying drawings wherein like reference numerals refer to like parts throughout the several views, and wherein:
Referring now to
The plurality of radially stacked, vane-type hydraulic couplings can include a radially outer located vane-type hydraulic coupling 40 and a radially inner located vane-type hydraulic coupling 50. The radially outer located vane-type hydraulic coupling 40 can include at least one radially outer located vane 22 and at least one corresponding radially outer located cavity 20a associated with the radially outer located rotor 20 to be divided by the at least one radially outer located vane 22 into a first outer variable volume working chamber 20b and a second outer variable volume working chamber 20c. The radially inner located vane-type hydraulic coupling 50 can include at least one radially inner located vane 32 and at least one corresponding radially inner located cavity 30a adjacent the radially inner located rotor 30 to be divided by the at least one radially inner located vane 32 into a first inner variable volume working chamber 30b and a second inner variable volume working chamber 30c.
The radially outer located vane-type hydraulic coupling 40 can include a combination of an outer vane 22 and cavity 20a associated with the outer rotor 20 to define first and second outer variable volume working chambers 20b, 20c. The combination of the outer vane 22 and cavity 20a can be defined by the stator 14 having a wall portion 14a with a radially outer surface 14b defining the outer vane 22, and the outer rotor 20 surrounding the radially outer surface 14b of the stator 14 to define the outer cavity 20a. The radially inner located vane-type hydraulic coupling 50 can include a combination of an inner vane 32 and cavity 30a associated with the inner rotor 30 to define first and second inner variable volume working chambers 30b, 30c. The combination of the inner vane 32 and cavity 30a can be defined by the stator 14 having a wall 14a with a radially inner surface 14c defining the inner cavity 30a, and the inner rotor 30 having an outer surface 30d defining the inner vane 32.
As best seen in
In operation, a dual variable cam timing phaser 10 provides radially outer annular spaces or cavities 20a and radially inner annular spaces or cavities 30a with respect to the drive stator 14 and the concentrically located driven outer and inner rotors 20, 30. The annular spaces or cavities 20a, 30a are divided into segment-shaped or arcuate variable volume working chambers 20b, 20c, 30b, 30c by outer and inner vanes 22, 32 extending radially from a surface of the outer and inner rotors 20, 30 and one or more vanes or walls 18 extending radially from a surface of the drive stator 14. As hydraulic fluid is admitted into and expelled from the various chambers 20b, 20c, 30b, 30c, the vanes 22, 32 rotate relative to one another and thereby vary the relative angular position of the driven outer and inner rotors 20, 30 with respect to each other and with respect to the stator 14.
Referring now to
The plurality of radially stacked, vane-type hydraulic couplings can include a radially outer located vane-type hydraulic coupling 40 and a radially inner located vane-type hydraulic coupling 50. The radially outer located vane-type hydraulic coupling 40 can include at least one radially outer located vane 22 and at least one corresponding radially outer located cavity 20a associated with the radially outer located rotor 20 to be divided by the at least one radially outer located vane 22 into a first outer variable volume working chamber 20b and a second outer variable volume working chamber 20c. The radially inner located vane-type hydraulic coupling 50 can include at least one radially inner located vane 32 and at least one corresponding radially inner located cavity 30a adjacent the radially inner located rotor 30 to be divided by the at least one radially inner located vane 32 into a first inner variable volume working chamber 30b and a second inner variable volume working chamber 30c.
The radially outer located vane-type hydraulic coupling 40 can include a combination of an outer vane 22 and cavity 20a associated with the outer rotor 20 to define first and second outer variable volume working chambers 20b, 20c. The combination of the outer vane 22 and cavity 20a can be defined by the stator 14 having a radially outer wall portion 14d with an inner surface 14e defining the outer cavity 20a, and the outer rotor 20 having an outer surface 20d defining the outer vane 22. The radially inner located vane-type hydraulic coupling 50 can include a combination of an inner vane 32 and cavity 30a associated with the inner rotor 30 to define first and second inner variable volume working chambers 30b, 30c. The combination of the inner vane 32 and cavity 30a can be defined by the stator 14 having a radially inner wall portion 14f interposed radially between the outer rotor 20 and the inner rotor 30. The inner wall portion 14f can have a radially inner surface 14g defining the inner cavity 30a, and the inner rotor 30 can have an outer surface 30d defining the inner vane 32.
As best seen in
In operation, a dual variable cam timing phaser assembly provides radially outer annular spaces or cavities 20a and radially inner annular spaces or cavities 30a with respect to the drive stator 14 and the concentrically located driven outer and inner rotors 20, 30. The annular spaces or cavities 20a, 30a are divided into segment-shaped or arcuate variable volume working chambers 20b, 20c, 30b, 30c by outer and inner vanes 22, 32 extending radially from a surface of the outer and inner rotors 20, 30 and one or more vanes or walls 18 extending radially from a surface of the drive stator 14. As hydraulic fluid is admitted into and expelled from the various chambers 20b, 20c, 30b, 30c, the vanes 22, 32 rotate relative to one another and thereby vary the relative angular position of the driven outer and inner rotors 20, 30 with respect to each other and with respect to the stator 14.
Referring now to FIGS. 1 and 7-10, a pressurized fluid distribution system for a variable cam timing phaser 10 for an internal combustion engine having at least one camshaft 12 can include a stator 14 having an axis of rotation and at least one rotor 20, 30 rotatable relative to the axis of rotation of the stator 14 independently of the stator 14. At least one vane-type hydraulic coupling 40, 50 can include a combination of a vane 22, 32 and cavity 20a, 30a associated with the at least one rotor 20, 30 to define first and second variable volume working chambers 20b, 20c; 30b, 30c. The first and second variable volume working chambers 20b, 20c; 30b, 30c, when selectively communicating with a source of pressurized fluid, can facilitate angular phase orientation of the at least one rotor 20, 30 independently with respect to the stator 14. At least one fluid transfer plate 60 can include a plurality of pressurized fluid passages 62a, 62b, 62c, 62d. Each fluid passage 62a, 62b, 62c, 62d can extend from a corresponding centrally located port 64a, 64b, 64c, 64d in fluid communication with a radially extending passage portion 66a, 66b, 66c, 66d in fluid communication with an arcuately extending passage portion 68a, 68b, 68c, 68d. At least one pressurized fluid passage 62a, 62b, 62c, 62d can be located on each side 60a, 60b of the at least one fluid transfer plate 60 for communication with a corresponding one of the first and second variable volume working chambers 20b, 20c, 30b, 30c. As best seen in
As best seen in
As best seen in
As best seen in
Referring now to
Referring now to the simplified schematic of
The annular groove segments 74f, 74g can be angularly positioned to benefit from oscillating torque. Phaser control can be accomplished by moving the control valve 160 away from a central null position to one of the shifted longitudinal end positions, while the annular groove segments 74f, 74g align with the first and/or second common shared fluid passages 116, 116b and move back to the central null position to close off flow until the desired alignment repeats. The control valve 160 can move back away from the central null position to continue phaser motion when the desired alignment repeats. Alternatively, the control valve 160 can be oscillated in both directions from the central null position during one revolution of concentric camshaft 12. An alternative control strategy for shared oil feed phasers can include oscillation of the control valve 160 around a null position at the camshaft rotation frequency or at fractional multiples of camshaft rotation frequency. The engine control unit can advance or retard the timing of the control valve 160 motion to overlap more or less with the portion of the cam rotation where annular groove segments 74f, 74g allow fluid flow in or out of the connected vane-type hydraulic couplings 40, 50. In other words, the control valve 160 is not held at a null position; instead flow from the control valve to the phaser is opened or closed by varying the overlap of the control valve 160 opening of the inlet ports 162 and/or outlet ports 164, 164a and the annular groove segment 74f, 74g openings being in fluid communication with a common shared fluid passage 116a, 116b.
It should be recognized that the annular groove segments 74f, 74g and outer diameter lands 112a, 112b can be equally angularly spaced as illustrated, or can be positioned an any non-overlapping angular extent and orientation desired. When the annular groove segments 74f, 74g and lands 112a, 112b are equally angularly spaced, the first and second variable volume working chambers 20b, 20c; 30b, 30c are simultaneously in fluid communication or simultaneously isolated depending on the angular position of the fluid transfer sleeve 72 and associated cam bearing 80. When the segments 74f, 74g and lands 112a, 112b are not equally angularly spaced, the fluid communication and isolation of the first and second variable volume working chambers 20b, 20c; 30b, 30c are offset in time with respect to one another depending on the angular position of the fluid transfer sleeve 72 and associated cam bearing 80.
While only two annular groove segments 74f, 74g have been shown schematically in
A method of assembling a pressurized fluid distribution system for a variable cam timing phaser 10 of an internal combustion engine having at least one camshaft 12 is disclosed. The method can include providing a stator 14 having an axis of rotation, and assembling at least one rotor 20, 30 within the stator 14 to be rotatable relative to the axis of rotation of the stator 14 independently of the stator 14. The stator 14 and at least one rotor 20, 30 define at least one vane-type hydraulic coupling 40, 50 including a combination of a vane 22, 32 and cavity 20a, 30a associated with the at least one rotor 20, 30 to define first and second variable volume working chambers 20b, 20c; 30b, 30c. The first and second variable volume working chambers 20b, 20c; 30b, 30c, when selectively communicating with a source of pressurized fluid, facilitate angular phase orientation of the at least one rotor 20, 30 independently with respect to the stator 14. The method can further include assembling at least one fluid transfer plate 60 having a plurality of pressurized fluid passages 62a, 62b, 62c, 62d with respect to the first and second variable volume working chambers 20b, 20c; 30b. 30c. Each passage 62a, 62b, 62c, 62d can extend from a corresponding centrally located port 64a, 64b, 64c, 64c, 64d in fluid communication with a radially extending passage portion 66a, 66b, 66c, 66d in fluid communication with an arcuately extending passage portion 68a, 68b, 68c, 68d. At least one pressurized fluid passage 62a, 62b, 62c, 62d can be formed on each side 60a, 60b of the at least one fluid transfer plate 60 for communication with a corresponding one of the first and second variable volume working chambers 20b, 20c; 30b, 30c.
A sprocket ring 52 can be assembled to the stator 14 interposed between the at least one fluid passage plate 60 and the first and second variable volume working chambers 20b, 20c; 30b, 30c. The sprocket ring 52 can include fluid passages 52a, 52b, 52c, 52d formed therethrough allowing fluid communication between the plurality of fluid passages 62a, 62b, 62c, 62d of the at least one fluid transfer plate 60 and the first and second variable volume working chambers 20b, 20c; 30b, 30c. An end plate 70 can be assembled to the at least one fluid passage plate 60 sealing at least some of the pressurized fluid passages 62a, 62b, 62c, 62d on one side 60a, 60b of the at least one fluid transfer plate 60.
A fluid transfer sleeve 72 can be assembled over the at least one camshaft 12. The fluid transfer sleeve 72 can be formed with a plurality of longitudinally extending and circumferentially spaced fluid passages 74a, 74b, 74c, 74d in fluid communication with longitudinally spaced and circumferentially spaced fluid ports 76a, 76b, 76c, 76d and ports 78a, 78b, 78c, 78d. Each fluid passage 74a, 74b, 74c, 74d can be separate and independent from the other fluid passages 74a, 74b, 74c, 74d of the fluid transfer sleeve 72. Each fluid outlet port 78a, 78b, 78c, 78d can define separate and independent fluid passages from other fluid outlet ports 78a, 78b, 78c, 78d of the fluid transfer sleeve 72 for assembly into fluid communication with a corresponding pressurized fluid passage 62a, 62b, 62c, 62d allowing fluid communication with the variable volume working chambers 20b, 20c; 30b, 30c of the first and second vane-type hydraulic couplings 40, 50.
A cam bearing 80 can be assembled into engagement with the fluid transfer sleeve 72. The cam bearing 80 can be formed having a plurality of annular fluid passages 82a, 82b, 82c, 82d spaced longitudinally from one another. Each annular fluid passage 82a, 82b, 82c, 82d can be assembled into fluid communication with one corresponding fluid passage 74a, 74b, 74c, 74d of the fluid transfer sleeve 72.
A variable cam timing phaser 10 can be driven by power transferred from an engine crankshaft and delivered to at least one camshaft 12 for manipulating at least one set of cams. The phaser 10 can include a drive stator 14 connectible for rotation with an engine crankshaft. At least one driven rotor 20, 30 can be associated with the stator 14. Each rotor 20, 30 can be connected for rotation with a corresponding one of the at least one camshaft 12 supporting at least one set of cams. The drive stator 14 and the driven rotor 20, 30 can be mounted for rotation about a common axis. A plurality of vane-type hydraulic couplings 40, 50 are defined between the drive stator 14 and driven rotor 20, 30 for coupling the at least one driven rotor 20, 30 for rotation with the drive stator 14 to enable the phase of the at least one driven rotor 20, 30 to be adjusted relative to the drive stator 14. A fluid transfer plate 60 can be provided having a plurality of pressurized fluid passages 62a, 62b, 62c, 62d, if desired. Each passage 62a, 62b, 62c, 62d can extend from a corresponding centrally located port 64a, 64b, 64c, 64d in fluid communication with a radially extending passage portion 66a, 66b, 66c, 66d in fluid communication with an arcuately extending passage portion 68a, 68b, 68c, 68d. At least one pressurized fluid passage 62a, 62b, 62c, 62d can be formed on each side 60a, 60b of the at least one fluid transfer plate 60 for communication with the plurality of vane-type hydraulic couplings 40, 50.
While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiments but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as is permitted under the law.
This application is a continuation-in-part of and under §119(e) claims the benefit of U.S. patent application Ser. No. 61/528,920 filed on Aug. 30, 2011 (Attorney Docket No. DKT11086) which is incorporated by reference herein in its entirety, is a continuation-in-part of and under §119(e) claims the benefit of U.S. Provisional Pat. Appl. Ser. No. 61/547,390 filed on Oct. 14, 2011 (Attorney Docket No. DKT11138), which is incorporated by reference herein in its entirety, and is a continuation-in-part of and under §119(e) claims the benefit of U.S. patent application Ser. No. 61/667,127 filed on Jul. 2, 2012 (Attorney Docket No. DKT11196).
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/US2012/052018 | 8/23/2012 | WO | 00 | 2/10/2014 |
| Number | Date | Country | |
|---|---|---|---|
| 61528920 | Aug 2011 | US | |
| 61547390 | Oct 2011 | US | |
| 61667127 | Jul 2012 | US |
