• 专利附录
  • 专利说明
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    • 专利摘要:
    method and system for engine cylinder decompression. a system for actuating an engine valve to decompress an engine cylinder for engine starting and/or engine braking is disclosed. the system may include a first element, such as an external piston, disposed above an engine valve, that receives an internal piston extending into a diameter produced in the first element. one or more springs can predispose the internal piston to a predefined position in the first element. the internal piston may include a lower surface that directly, or through an intermediate slide pin, actuates an engine valve in response to the application of fluid pressure to the internal piston. the internal piston can be used to decompress an engine cylinder for engine starting and/or to perform engine braking.
    公开号:BR112014006435B1
    申请号:R112014006435-0
    申请日:2012-09-21
    公开日:2021-06-22
    发明作者:Brian Ruggiero；Steven N. Ernest；Neil E. Fuchs；Jin Xu；Erin Day；Joseph Paturzo Iii；Johnathan W. Prusak；Jeffrey E. Mossberg
    申请人:Jacobs Vehicle Systems, Inc.；
    IPC主号:
    专利说明:

    Cross reference to related orders
    [001] The present application refers to, and claims priority to, United States Provisional Patent Application 61/537,430 filed September 21, 2011, which is entitled "Method and System For Engine Cylinder Decompression". field of invention
    [002] The present invention relates to systems for and methods of actuation of engine valves to decompress an engine cylinder for engine starting, bleed braking and/or braking with compression release. Invention precedents
    [003] The control of exhaust gas flow through an internal combustion engine has been used in order to provide vehicle engine braking of both the compression release type and the bleed type. Both types of engine braking operate by decompressing an engine cylinder to allow exhaust gas to exit the cylinder. Controlling the exhaust gas flow can also provide benefits during engine starting. Specifically, holding an exhaust valve open during engine startup can decompress the cylinder so that the piston can move to the cylinder's top dead center (TDC) position more easily. Benefits of decompression during engine starting can include easier engine starting, lighter starting system and/or battery requirements, and avoiding or reducing the need for additional starting aids.
    [004] Generally speaking, engine braking systems can control the flow of exhaust gas from the engine cylinders to the exhaust system (ie, exhaust manifold, exhaust pipe, etc.). The flow of exhaust gas from the engine cylinders can be controlled to provide a retarding force on the engine pistons to slow the engine down. Specifically, one or more exhaust valves can be selectively actuated to provide engine braking by releasing compression, bleed and/or partial bleed.
    [005] The operation of a compression release, or retarder, type engine brake is well known. A four-stroke internal combustion engine experiences intake, compression, expansion and exhaust cycles during its operation. The intake cycle occurs in conjunction with a main intake valve event, during which the intake valves on each cylinder are opened to allow air to enter the cylinder. The exhaust cycle occurs in conjunction with a main exhaust valve event, during which the exhaust valves on each cylinder are opened to allow combustion gases to exit the cylinder. Typically, the exhaust and intake valves are closed during most of the compression and expansion cycles. During engine compression release braking, the fuel supply to the engine cylinders is stopped and, in addition to the main exhaust valve event, one or more exhaust valves can also be selectively opened during the compression stroke to convert the internal combustion engine for a force-absorbing air compressor. Specifically, as the engine piston travels upward during the compression stroke, gases trapped in the cylinder are compressed and oppose the upward movement of the piston. As the piston approaches the top dead center (TDC) position during the compression stroke, at least one exhaust valve can be opened to release compressed gases in the cylinder to the exhaust manifold, preventing energy stored in the compressed gases is returned to the piston in the subsequent expansion downward stroke. In doing so, the engine develops the retarding force to help decelerate the vehicle. An example of a prior art compression release engine brake is presented by the disclosure of Cummins, Pat. U.S. 3,220,392 (November 1965), which is incorporated herein by reference.
    [006]The operation of a bleed-type motor brake is also known. During engine bleed braking, in addition to the main exhaust valve event, one or more exhaust valves may be held slightly open for all remaining engine cycles (ie, the intake, compression, and expansion cycles for a brake by full-cycle bleed) or for a portion of the remaining engine cycles (ie, the compression and expansion cycles for a partial-cycle bleed brake). The primary difference between a partial-cycle bleed brake and a full-cycle bleed brake is that the former can allow the exhaust valve to close for most or all of the intake cycle. An example of a bleed engine brake is revealed in Yang, Pat. U.S. 6,594,996 (July 22, 2003), which is incorporated herein by reference.
    [007] The initial opening of the exhaust valves in a bleed braking operation may be before the TDC of the compression stroke and is preferably near the bottom dead center (BDC) point between the intake and compression cycles. As such, the bleed-type engine brake may require much less force to actuate the valves and generate less noise due to continuous bleed rather than the quick release of a compression release-type brake. Thus, the engine bleed brake can have significant advantages.
    [008] An engine decompression system can keep one or more exhaust valves open in an engine cylinder during engine starting. An engine decompression system of the type described here can be particularly useful in cold weather conditions, when crank battery power is less, crank time to start is longer, and the engine is more difficult to turn. Additionally, engine decompression, which can reduce battery power and starter system requirements, can result in lighter components, which allows for greater fuel efficiency. The reduction in start-up time resulting from the use of a decompression system can also have emission benefits. Accordingly, advantages such as these, but not limited to the foregoing, may be realized by using one or more of the embodiments of the invention described herein.
    [009] Additional advantages of the various embodiments of the invention are set forth, in part, in the description that follows and, in part, will be apparent to the person skilled in the art from the description and/or practice of the invention. Invention Summary
    [010] Responsive to the foregoing challenges, the applicant has developed an innovative system to activate an engine valve to decompress an engine cylinder or perform engine bleed braking comprising: a vertically movable element disposed above an engine valve, said vertically movable element having an inner piston diameter that extends horizontally into the vertically movable element; a horizontally movable inner piston disposed on the diameter of the inner piston; a first spring placed in the diameter of the inner piston, said first spring predisposing the inner piston to a predefined position in the diameter of the inner piston and a pneumatic or hydraulic fluid supply passage communicating with the diameter of the inner piston, wherein said internal piston includes a device to cause the engine valve to be actuated positioned along the lower surface of the internal piston.
    [011] It is to be understood that both the preceding general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed. Brief description of the drawings
    [012] In order to aid in the understanding of this invention, reference will now be made to the accompanying drawings, in which like reference characters refer to like elements.
    [013] Figure 1 is a sectional side view illustrating a system to provide engine braking and/or engine decompression for engine starting according to a first embodiment of the present invention.
    [014] Figure 2 is a sectional side view illustrating a system to provide engine braking and/or engine decompression for engine starting according to a second embodiment of the present invention when the system is maintaining a valve for the engine. open engine.
    [015] Figure 3 is a sectional side view illustrating the system shown in figure 2 when the system is allowing the engine valve to close.
    [016] Figure 4 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a third embodiment of the present invention.
    [017] Figure 5 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a fourth embodiment of the present invention.
    [018] Figure 6 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a fifth embodiment of the present invention.
    [019] Figure 7 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a sixth embodiment of the present invention.
    [020] Figure 8 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a seventh embodiment of the present invention.
    [021] Figure 9 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to an eighth embodiment of the present invention.
    [022] Figure 10 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a ninth embodiment of the present invention.
    [023] Figure 11 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to a tenth embodiment of the present invention.
    [024] Figure 12 is a sectional side view illustrating a system to provide engine braking and engine decompression for engine starting according to an eleventh embodiment of the present invention.
    [025] Figure 13 is a flowchart illustrating an example of a process for decompressing engine cylinders at engine shutdown according to an embodiment of the present invention.
    [026] Figure 14 is a flowchart illustrating an example of a process for starting an engine with uncompressed engine cylinders according to an embodiment of the present invention. Detailed description of embodiments of the invention
    [027] Reference will now be made in detail to a first embodiment of the present invention, whose example is illustrated as the valve actuation system of the engine 10 in Figure 1 of the accompanying drawings. Valve actuation system 10 may include a housing 100 mounted to an engine above a rocker arm, valve bridge, engine trigger valve, or other valve assembly element (not shown). Housing 100 may include a vertically extending outer piston diameter 110 and a hydraulic fluid supply passage 120 communicating with the outer piston diameter. A slack adjusting screw 130 can extend vertically through the housing 100 into the diameter of the outer piston 110. A nut 132 can be used to tighten the slack adjusting screw in place. An optional vent passage 112 may extend from the diameter of the outer piston 110 to the environment.
    [028] An outer piston 140 can be arranged in the bore of the diameter of the outer piston 110 to be vertically movable. "Vertically movable" is defined by the movement of the outer piston 140 along the geometric axis of the diameter of the outer piston 110. The outer piston 140 may include a diameter of the inner piston 142 that extends laterally or horizontally into the outer piston and is at register with the fluid supply passage 120. The outer piston 140 acts as a vertically movable element or "housing", itself for the horizontally disposed inner piston placed the diameter of the inner piston. Outer piston 140 may include a pin diameter 144 that extends vertically from the bottom of the outer piston 140 to the diameter of the inner piston 142. A vent passage 146, spaced laterally from the diameter of the pin 144, may also extend from the bottom of the outer piston 140 to inner piston diameter 142. The upper surface of outer piston 140 may contact clearance adjusting screw 130.
    [029] An inner piston 150 may be disposed horizontally on the diameter of inner piston 142. Inner piston 150 may include an annular recess 152 that extends partially (shown) or completely (not shown) around the circumference of the inner piston. The recessed surface formed by recess 152 may define one or more shoulders that frame the recess. Inner piston 150 may further include an inner diameter 154 that receives a spring from inner piston 156. Spring 156 may bias inner piston 150 to the fluid supply passage 120. Recess 152 formed in inner piston 150 may be positioned along the lateral length of the inner piston so that it is not centered above the diameter of pin 144 when the inner piston is closest to the fluid supply passage 120.
    [030] A vertically sliding pin 160 can be disposed on the diameter of the pin 144. The sliding pin 160 can have an upper portion with a chamfered upper surface and a lower portion of reduced diameter. A pin shoulder may be formed at the intersection of the reduced diameter lower portion and the upper portion of the sliding pin 160. A pin spring 162 may be placed between the sliding pin shoulder 160 and a washer through which the lower diameter portion reduced slide pin extends. The chamfered upper surface of the slide pin can be formed and sized to be received in the annular recess 152. The slide pin 160 can be positioned above a rocker arm or valve bridge which, in turn, is used to actuate the relief valve. . If positioned above a valve bridge, slide pin 160 can be positioned above the center of the valve bridge to open multiple relief valves or above one end of a floating valve bridge to open a single relief valve.
    [031] The modality shown in figure 1 can provide cylinder decompression during engine startup by holding one or more exhaust valves (not shown) open by vertically moving slide pin 160 after engine shutdown. Referring to figures 1 and 13, when the motor stops, a stop command is received during step 610, after which the motor speed is determined to verify that it is below the threshold value X in step 620. engine speed is not below threshold X, system can continue to monitor engine speed until it falls below threshold. Once the engine speed is determined to be below the X threshold, the engine speed can be compared to a recovery threshold in step 630. If the engine speed is not below the recovery threshold, the system can return to step 610, however, if the engine speed is below the recovery threshold, the fuel can be stopped for the cylinders to be decompressed in step 640. Then control valve 170 (figure 1) can be instructed to open in step 650, causing the hydraulic or pneumatic pressure to be decreased in the fluid supply passage 120. As a result, the inner piston 150 can be translated horizontally to the fluid supply passage under the influence of the inner piston spring 156. The movement horizontal of inner piston 150 means the movement of inner piston along the diameter of inner piston 142. When inner piston 150 moves to the left (as shown in fig. a 1), the slide pin 160 is forced downwards, so that it, for example, is flush with the diameter wall of the inner piston 142. The translation of the slide pin 160 downward causes it to move the swing arm or the valve bridge below it downwards, which, in turn, will prevent the closure of the exhaust valve, via direct contact or through a valve bridge, after being opened by another element of the valve assembly, such as a swinging arm. Thus, the lower surface of the inner piston 150 provides a device for causing the relief valve to be actuated using the sliding pin 160. Preferably, this downward translation may be approximately 2 mm for decompression at startup, however, the invention does not it is limited by the amount of downward translation. In step 660, the motor speed can be checked to determine if it is above zero. If the engine speed is above zero, the control valve can be kept open. If the engine speed is determined to be zero, the control valve can be instructed to close in step 670. Inner piston 150 and slide pin 160 remain in the position shown in figure 1 while the engine is off. As a result, one or more exhaust valves are opened at the time of the next attempt to start the engine.
    [032]Referring to figures 1 and 14, the engine can be started as follows. System 10 may receive a command that engine start is beginning at step 700, at which time fluid is not initially supplied to the fluid supply passage 120 because control valve 170 is closed and/or the fluid source is inactive. In turn, the fluid control valve 170 can be commanded to open in step 702 and the engine starter can be instructed to rotate the engine in step 704. In step 706, the engine speed can be checked to determine if it it is sufficient to supply the engine cylinders not decompressed. If the engine speed is not sufficient, the attempt to start the engine may continue to keep control valve 170 closed. If the engine speed is sufficient for fueling, fuel can be added to the cylinders not decompressed in step 708. When the engine speed equals or exceeds a predetermined threshold, as determined in step 710, the initiator can be disengaged in step 714 If the motor still does not start, the starting attempt can continue as per step 712. Then the motor temperature can be monitored to determine if it is above a threshold Y value in step 716. has not been exceeded, control valve 170 can be held closed during step 718. If temperature threshold Y has been exceeded, control valve 170 can be commanded to open in step 720 and fuel supplied to all engine cylinders at step 722.
    [033] After control valve 170 is opened in step 720, it may take up to close to time or after the engine is running for sufficient fluid pressure to build up in the fluid supply passage 120 to move the piston internal 150 to the diameter of the internal piston 142 against the bias of the spring of the internal piston 156. The lateral or horizontal movement of the internal piston 150 into its diameter 142 causes the annular recess 152 to register with the upper portion. of the slide pin 160. When the inner piston 150 is moved fully to the right, the upper portion of the slide pin 160 is received within the annular recess 152 and, as a result, the slide pin translates upward under the influence of the pin spring 162 In turn, the slide pin is no longer able to hold the swingarm or valve bridge down to keep the exhaust valve(s) open. Then the exhaust valves can be opened and closed under the influence of the other elements of the valve assembly.
    [034] The mode shown in figure 1 can also provide bleed-type engine braking during engine operation by holding one or more exhaust valves open by vertical movement of the slide pin 160. In order to provide engine braking , fluid supply passage 120 is connected to an optional solenoid or other type of control valve 170 that can selectively maintain or vent hydraulic or pneumatic pressure from the fluid supply passage in response to an electrical signal. When engine braking is desired during engine operation, fuel flow to the engine cylinder ceases and hydraulic pressure decreases in fluid supply passage 120 under control of control valve 170. Control valve 170 can decrease the hydraulic pressure by venting hydraulic fluid from the fluid supply passage 120. As a result, the inner piston 150 is translated to the fluid supply passage under the influence of the inner piston spring 156, the slide pin 160 is forced downwards , so that it is flush with the inner piston diameter wall 142 and the rocker arm or valve bridge below the slide pin yields opening one or more exhaust valves. Preferably, this downward translation of the exhaust valve may be approximately 0.5 mm for engine braking, however, the invention is not limited by the amount of downward translation of the exhaust valve. Inner piston 150 and sliding pin 160 can remain in the position shown in Figure 1 while hydraulic fluid pressure is applied to the diameter of inner piston 142 through fluid supply passage 120. As a result, one or more exhaust valves are maintained open to provide bleed braking.
    [035] When engine braking is no longer desired, control valve 170 can be activated to supply hydraulic pressure to fluid supply passage 120. When hydraulic pressure builds up in fluid supply passage 120, the Inner piston 150 is forced into the diameter of inner piston 142 against biasing the spring of inner piston 156. Lateral movement of inner piston 150 into its diameter 142 causes annular recess 152 to register with the upper portion of the slide pin 160. When the inner piston 150 is moved fully to the right, the upper portion of the slide pin 160 is received within the annular recess 152 and, as a result, the slide pin translates upward under the influence of the pin spring 162 In turn, the slide pin 160 no longer holds the swingarm or valve bridge down to keep the exhaust valve(s) open and bleed braking ceases.
    [036] An engine valve actuation system 20 constructed in accordance with a second embodiment of the present invention is illustrated in Figures 2 and 3. Referring to Figure 2, the system 20 may include a housing 200 mounted to an engine above one side of a valve bridge 72. The valve bridge can be used to actuate the engine valves 74 and 76 which are preferably exhaust valves and which are mounted to a cylinder head of the engine 78. valve 72 may be "floating", meaning that it can receive a downward movement at only one end to open only one engine valve 74 and/or receive a downward movement at its center to open both engine valves 74 and 76. swingarm 70 can be used to actuate both engine valves 74 and 76 providing a downward movement to the center of valve bridge 72.
    [037] The housing 200 may include a piston diameter 210 and a hydraulic fluid supply passage 220. The hydraulic fluid supply passage 220 may be connected to a low pressure fluid source such as an oil pump ( not shown) and can be provided with a continuous supply of hydraulic fluid when the engine is running. An actuator piston 240 may be slidably disposed on the diameter of the piston 210. One or more springs 250 may bias the actuator piston into the diameter of the piston 210 and away from the end cap 270 used to seal the diameter of the piston. Actuator piston 240 may include an inner chamber 260 that is formed and sized to allow the side wall of the actuator piston to receive a tubular sleeve 230 without undue leakage of hydraulic fluid from chamber 260. Sleeve 230 may be biased by a spring 232 to the closed end of the piston diameter 210. The biasing force of the one or more springs 250 may be greater than the biasing force of the spring 232 so that the system assumes the position shown in Figure 2 when hydraulic pressure is released of the inner chamber 260.
    [038] The mode shown in figures 2 and 3 can provide cylinder decompression during engine starting by keeping the exhaust valve 74 open through the horizontal movement of the actuator piston 240. Referring to figure 2, when the engine is stopped, the hydraulic pressure decreases in the fluid supply passage 220. As a result, the actuator piston 240 is translated to the fluid supply passage 220 under the influence of one or more springs 250. When the actuator piston 240 moves to the right, its lower surface engages valve bridge 72 below it and forces valve bridge downward, which in turn yields opening relief valve 74. At the same time, sleeve 230 is fully received on actuator piston 240, the which causes spring 232 to compress. In this way, the lower surface of the actuator piston 240 acts as a device to cause the relief valve 74 to be actuated. Preferably, this downward translation may be approximately 2 mm for decompression for motor starting, however, the invention is not limited by the amount of downward translation. Actuator piston 240 remains in the position shown in figure 2 while the engine is off. As a result, exhaust valve 74 is opened at the time of the next attempt to start the engine.
    [039] Referring to figure 3, when the engine is started, hydraulic fluid is not initially supplied to the 220 fluid supply passage. Sufficient hydraulic fluid forms in the fluid supply passage 220 and inside the inner chamber 260 to move the actuator piston 240 to the diameter of the piston 210 against biasing one or more springs 250. Lateral movement of the actuator piston 240 to the end cap 270 causes the lower surface of the actuator piston to disengage valve bridge 72. At the same time, biasing spring 232 holds sleeve 230 in position against end wall of inner chamber 260. Sleeve 230 may impede undue leakage of hydraulic fluid from the inner chamber. In turn, the valve bridge 72 is free to move upward under the influence of the relief valve springs (not shown) and the relief valve 74 can close. Thereafter, the exhaust valves 74 and 76 can be opened and closed under the influence of the rocker arm 70 and/or other elements of the valve assembly.
    [040] The modality shown in figures 2 and 3 can also provide bleed-type engine braking during engine operation by holding the exhaust valve 74 open through the horizontal movement of the actuator piston 240, as described above. In order to provide engine braking, fluid supply passage 220 may be connected to an optional solenoid or other type of control valve that can selectively maintain or vent hydraulic pressure from the fluid supply passage in response to a signal. electric. When engine braking is desired during engine operation, fuel flow to the engine cylinder is ceased and hydraulic pressure decreases in the fluid supply passage 220 under control of the control valve. As a result, the lower surface of the actuator piston 240 can engage the valve bridge 72 below it and force the valve bridge downward which, in turn, yields opening the exhaust valve 74 for bleed-type engine braking. When bleed braking is no longer desired, the control valve can supply hydraulic fluid to the inner chamber 260 so that the actuator piston 240 disengages valve bridge 72 and exhaust valve 74 closes as shown in figure 3.
    [041] A third embodiment of the present invention is illustrated in Figure 4, in which similar reference characters refer to similar elements. Figure 4 illustrates a portion of the outer piston 140 shown in Figure 1 with an alternative inner piston assembly. All aspects of system 30 shown in figure 4 are the same as those for system 10 shown in figure 1, except for the inner piston assembly and the extension of the diameter of inner piston 142 through outer piston 140 and housing 100. Referring to Figure 4, the inner piston 350 is predisposed to the fluid supply passage (not shown on the left) by a first inner piston spring 156 and a second inner piston spring 158. The inner piston 350 is also provided with a recessed surface including a first annular recess 352 and a second annular recess 354 of different depths. A solenoid or other type of control valve 170 can be connected to fluid supply passage 120, as shown in figure 1.
    [042] Referring to figures 1 and 4, the system 30 can provide engine bleed and cylinder decompression type engine braking. When cylinder decompression for engine starting is desired, control valve 170 can vent hydraulic pressure from fluid supply passage 120 so that inner piston first spring 156 forces inner piston 350 to the position shown. in figure 4. This in turn forces slide pin 160 down so that it can yield by opening one or more cylinder relief valves as described in conjunction with figure 1.
    [043] If neither cylinder decompression nor bleed braking is desired, control valve 170 can be controlled to supply hydraulic fluid at low pressure to the fluid supply passage 120. This causes internal piston 350 translates to the inner piston springs 156 and 158. Low pressure hydraulic fluid may be sufficient to overcome the bias of the first spring of the inner piston 156, but not sufficient to overcome the bias of the second spring of the inner piston 158. As a result, the Low pressure application of hydraulic fluid to the inner piston 350 causes it to move only enough so that the upper surface of the slide pin 160 is received in the second annular recess 354. This position places the slide pin 160 in its most suitable position. which causes the exhaust valve being actuated by the sliding pin to close.
    [044] Still referring to figures 1 and 4, if bleed braking is desired, control valve 170 can be controlled to supply hydraulic fluid at higher pressure to the fluid supply passage 120. This causes inner piston 350 translates further to inner piston springs 156 and 158. Hydraulic fluid at higher pressure may be sufficient to overcome the biases of inner piston first spring 156 and inner piston second spring 158. As a result of application of the higher pressure hydraulic fluid to the inner piston 350, it moves enough to the first and second springs 156 and 158 that the upper surface of the slide pin 160 is received in the first annular recess 352. This position places the slide pin 160 in an intermediate position, which causes the exhaust valve to be actuated by the sliding pin for bleed braking, ie to a lesser extent than for cylinder decompression.
    [045] A fourth embodiment of the present invention is illustrated in Figure 5, in which similar reference characters refer to similar elements. Figure 5 illustrates a portion of the vertically movable outer piston 140 shown in Fig. 1 with an alternative horizontally movable inner piston assembly. All aspects of system 40 shown in figure 5 are the same as those for system 10 shown in figure 1, except for the inner piston assembly and the extension of the diameter of inner piston 142 through outer piston 140 and housing 100. Referring to Figure 5, inner piston 350 is predisposed to the fluid supply passage (not shown left) by a first inner piston spring 156. Conversely, inner piston 350 is predisposed to first inner piston spring 156 by a second inner piston spring 158. The inner piston 350 is also provided with a first annular recess 352 and a second annular recess 354 of different depths. A solenoid or other type of control valve 170 can be connected to fluid supply passage 120, as shown in figure 1.
    [046] Referring to figures 1 and 5, the system 40 can provide engine bleed and cylinder decompression type engine braking. When cylinder decompression for starting the engine is desired, control valve 170 can vent hydraulic pressure from fluid supply passage 120 so that inner piston first spring 156 forces inner piston 350 into its furthest position. to the left, so that the sliding pin 160 is forced downward by the surface 356 of the inner piston. When slide pin 160 is in this position, it yields by opening one or more relief valves for cylinder decompression as described in conjunction with Figure 1.
    [047] If neither cylinder decompression nor bleed braking is desired, control valve 170 can be controlled to supply hydraulic fluid at low pressure to the fluid supply passage 120. This causes internal piston 350 translate to and slightly compress the first inner piston spring 156. The second inner piston spring 158 can aid in compressing the first inner piston spring 156. The combination of low pressure hydraulic fluid and the second inner piston spring bias can be sufficient to overcome the bias of the first spring of the inner piston 156. As a result, the application of hydraulic fluid at low pressure to the inner piston 350 causes it to move only enough so that the upper surface of the sliding pin 160 is received in the second annular recess 354, as shown in figure 5. This position places the slide pin 160 in its uppermost position, which causes the valve to e. scape being actuated by the slide pin close.
    [048] Still referring to Figures 1 and 5, if bleed braking is desired, the control valve 170 can be controlled to supply a higher pressure hydraulic fluid to the fluid supply passage 120. This causes the inner piston 350 translates further and further compresses the inner piston spring 156. The higher pressure hydraulic fluid may be sufficient to overcome the bias of the first inner piston spring 156 with the help of the second inner piston spring 158. How to As a result of applying hydraulic fluid at higher pressure to the inner piston 350, it moves enough to the first inner piston spring 156 that the upper surface of the slide pin 160 is received in the first annular recess 352. This position places the slide pin 160 in an intermediate position, which causes the exhaust valve to be actuated by the sliding pin for bleed braking, i.e. to a lesser extent than for decompression of the cylinder.
    [049] A fifth embodiment of the present invention is illustrated in Figure 6, in which similar reference characters refer to similar elements. Figure 6 illustrates a system 50 for providing engine valve actuation. System 50 may include a vertically movable outer piston 140 in which a diameter of inner piston 142 is created. The outer piston 140 can be arranged on a diameter of the outer piston created in a housing, such as housing 100 shown in Figure 1, so as to be vertically movable. The diameter of inner piston 142 can receive a horizontally disposed inner piston 420 that includes an outer surface 440, first and second notches 430 and 432, and first and second recesses 442 and 444 that form a recessed surface. A slide pin diameter 144 can be created on the outer piston 140 and a slide pin 160 can be placed on the slide pin diameter. A slide pin spring 162 can bias the slide pin for contact with the inner piston 420.
    [050] The first and second springs 450 and 452 can be compressed against the flat surfaces of the first and second notches 430 and 432 to hold the inner piston 420 in the position shown in figure 6. The inner piston 420 can be rotated in the direction clockwise and counterclockwise, that is, it can be movable, relative to the diameter of the inner piston 142 using any known mechanical, hydraulic, electromechanical, hydromechanical or similar mechanism. Rotating the inner piston 420 clockwise causes the slide pin 160 to be received in the second recess 444, which allows the motor valve (not shown) that is actuated by the slide pin to close. Rotating inner piston 420 counterclockwise causes slide pin 160 to rise onto surface 440 and open the engine valve. For example, when slide pin 160 is pushed down by surface 440, an exhaust valve or exhaust valve bridge can be lowered by the slide pin to provide cylinder relief. When the piston 420 is not rotated in one way or the other, as shown in figure 6, the slide pin 160 can be slightly lowered by the first recess 442 to open the engine valve to a lesser degree. If the engine valve is an exhaust valve, this position can place the slide pin 160 in an intermediate position, which causes the exhaust valve to be actuated by the slide pin for bleed braking.
    [051] A sixth embodiment of the present invention is illustrated by Figure 7, in which like reference characters refer to like elements. Figure 7 illustrates a system 60 for providing engine valve actuation. System 60 may include a housing 500 mounted to an engine above a rocker arm, valve bridge, or other element of the valve assembly (not shown). Housing 500 may include an outer piston diameter 510 and a first hydraulic fluid supply passage 512 communicating with the outer piston diameter. A first control valve, as shown in Figure 1, or master piston may hydraulically communicate with the first hydraulic fluid supply passage 512. A clearance adjusting screw 130 may extend through housing 100 into the diameter of the external piston 510. A nut 132 can be used to hold the backlash adjusting screw in place.
    [052] An outer piston 520 may be arranged to slide the diameter of the outer piston 510. The outer piston 520 may include a diameter of the inner piston 524 that extends vertically into the outer piston so as to be coaxial with the diameter of the outer piston 510. The diameter of inner piston 524 communicates with a second fluid supply passage 514 via passage 522. A second control valve, as shown in Figure 8, can communicate with the second hydraulic fluid supply passage. 514. Outer piston 520 can act as a vertically movable element or "housing" itself for the inner piston disposed on the diameter of inner piston 524. The second hydraulic fluid supply passage 514 can communicate with a second valve for control or master piston assembly (not shown). One or more recesses 536 may be created in the wall of outer piston 520.
    [053] An inner piston 540 may be disposed sliding the diameter of inner piston 524. Inner piston 540 may have a hollow interior 542 defined by the upper portion of the inner piston wall. The hollow interior 542 can be staggered to form a shoulder over which a first spring 526 can exert a biasing force to separate the inner piston 540 from the outer piston 520. The inner piston wall may also include one or more openings. sized to receive a ball or roller 532, each of which is sized, in turn, to be securely received in the one or more recesses 536 provided in the wall of outer piston 520, as shown in Figure 7. Inner piston 540 may include a lower portion adapted to actuate a rocker arm, valve bridge or other valve assembly element which, in turn, can actuate an engine valve.
    [054] A locking piston 530 may be slidably disposed within the hollow interior 542 of the inner piston 540. The locking piston 530 may include a central opening 534 in which to receive a second spring 544. The second spring may bias the inner piston 540 and locking piston 530 to separate. The diameter of the locking piston 530 in the lower portion may be substantially equivalent to the diameter of the hollow interior 542 of the inner piston 540. The upper portion of the locking piston 530 may have a reduced diameter. The difference between the radius of the lower portion of the locking piston 530 and the radius of the upper portion of the locking piston is at least equal to or greater than the depth of the one or more recesses 536.
    [055] The mode shown in figure 7 can provide cylinder decompression during engine starting by holding one or more exhaust valves (not shown) open by vertically moving the internal piston 540. When the engine is stopped, the hydraulic pressure is decreased in the second hydraulic fluid supply passage 514 under the control of the second control valve. As a result, the inner piston 540 is translated downwardly under the influence of the first spring 526 and the locking piston 530 is translated upwardly under the influence of the second spring 544. 530 moves upward, each of the balls or rollers 532 is pushed through its respective opening in the inner piston wall and into the one or more mating recesses 536. Insertion of the balls or rollers 532 into the one or more recesses 536 lock the inner piston 540 in the position shown in figure 7 relative to the outer piston 510. While in this position, the inner piston 540 causes the swingarm or valve bridge below it to be lowered, which in turn yields opening one or more exhaust valves. Preferably, such downward translation may be approximately 2 mm for decompression at start, however, the invention is not limited by the amount of downward translation. Inner piston 540 remains in the position shown in figure 7 while the engine is off. As a result, one or more exhaust valves are opened at the time of the next attempt to start the engine.
    [056] When the engine is started, the second control valve can be opened to supply hydraulic fluid, however, hydraulic fluid may not initially be supplied to the second fluid supply passage 514. This may take up to near time or after the engine is running that sufficient hydraulic fluid pressure builds up in the second fluid supply passage 514 to move the lock piston 530 into the hollow interior 542 of the inner piston 540 against the bias of the second spring 544. downward movement of lock piston 530 into hollow interior 542 allows balls or rollers 532 to be accommodated by the reduced diameter upper portion of lock piston and thereby move out of one or more recesses 536. As a result , the inner piston 540 can be unlocked from the outer piston 520 and the inner piston 540 can be pushed up by the exhaust valve springs through s of an intermediate swingarm or valve bridge. Thereafter, the exhaust valves can be opened and closed under the influence of other elements of the valve assembly.
    [057] The modality shown in figure 7 may also provide bleed-type engine braking during engine operation by holding one or more exhaust valves open by locking the internal piston 540 as described above under the control of the second control valve.
    [058]The mode shown in figure 7 can also be used to provide engine braking by bleed or compression release in another way. Compression release engine braking can be provided by filling the hydraulic fluid supply passage of the first hydraulic fluid at high pressure 512 from a high pressure reservoir under the control of the optional first control valve or a master piston assembly (shown as element 172 in Figure 8). High pressure fluid can be supplied cyclically to the outer piston diameter 510 when the piston in the engine cylinder underlying the system 60 is near top dead center. High pressure fluid can be released when the piston moves away from the top dead center position so that the outer piston 520 is forced down to an engine braking event by compression release. Engine valve springs (not shown) can return external piston 520 to the position shown in figure 7 after each compression release event.
    [059] Still referring to figure 7, for engine bleed braking, low pressure hydraulic fluid can be supplied to the first hydraulic fluid supply passage 512 under the control of the optional second control valve, so that outer piston 520 and inner piston 540 are forced down together for a bleed braking event. Low pressure fluid can be released when bleed braking is no longer desired and engine valve springs (not shown) can return external piston 520 to the position shown in figure 7.
    [060] A seventh embodiment of the present invention is illustrated as the engine valve actuation system 70 in Figure 8 of the accompanying drawings. Valve actuation system 70 shown in figure 8 is identical to system 10 shown in figure 1, with the following exceptions. System 70 includes a second hydraulic fluid supply passage 122 that extends from a second control valve or master piston assembly 172 to the diameter of outer piston 110.
    [061] System 70 can perform all of the engine valve actuations described above in conjunction with figure 1 and also perform engine braking by bleeding or compression release. Engine braking by bleed or compression release can be accomplished by supplying hydraulic fluid at low pressure to inner piston diameter 142 from fluid supply passage 120. This can cause inner piston 150 to move inward of inner piston diameter 142 against inner piston spring bias 156. Lateral movement of inner piston 150 into its diameter 142 causes annular recess 152 to register with the upper portion of sliding pin 160. Inner piston 150 is moved fully to the right, the upper portion of the slide pin 160 is received within the annular recess 152 and, as a result, the slide pin translates upward under the influence of the spring of the pin 162.
    [062] Still referring to figure 8, for engine braking by compression release, high pressure hydraulic fluid can be supplied to the second hydraulic fluid supply passage 122 from a high pressure container under the control of the optional second control valve or from a master piston assembly 172. Fluid at high pressure can be supplied cyclically to the diameter of the outer piston 110 when the piston in the engine cylinder underlying the slide pin 160 is near top dead center . High pressure fluid can be released when the piston moves away from the top dead center position so that the outer piston 140 and slide pin 160 are forced downward for a compression release engine braking event. Engine valve springs (not shown) can return external piston 140 to the position shown in figure 8 after each compression release event.
    [063] For bleed engine braking, low pressure hydraulic fluid can be supplied to the second hydraulic fluid supply passage 122 under the control of the optional second control valve 172, so that the external piston 140 and the slide pin 160 are forced down for a bleed braking event. Low pressure fluid can be released when bleed braking is no longer desired and engine valve springs (not shown) can return external piston 140 to the position shown in figure 8.
    [064] An eighth embodiment of the present invention is illustrated as the valve actuation system of the engine 80 in Figure 9 of the accompanying drawings. Valve actuation system 80 shown in figure 9 is identical to system 10 shown in figure 1, with the following exceptions. System 80 includes an inner piston diameter 142 and an inner piston 150 that are positioned in a housing 100 that is also a valve bridge. Additionally, rather than contacting a slide pin, internal piston 150 can act directly on the valve stem of an engine 74. System 80 can perform all of the engine valve actuations described above in conjunction with figure 1.
    [065] A ninth embodiment of the present invention is illustrated as the engine valve actuation system 90 in Figure 10 of the accompanying drawings. The valve actuation system 90 shown in figure 10 is identical to system 60 shown in figure 7, with the following exceptions. System 90 is disposed on a valve bridge that provides housing 500 for the system. Additionally, rather than using a first hydraulic fluid supply passage 512 to provide compression release braking or bleed braking, another element of the valve assembly, such as a swing arm, cam, slave piston, or other element 550 performs a mechanical braking actuation of the engine to the external piston 520. Additionally, the internal piston 540 can act directly on the valve stem of the engine 74. System 90 can perform all of the engine valve actuations described above in conjunction with the figure 7.
    [066] A tenth embodiment of the present invention is illustrated as the valve actuation system of the engine 95 in Figure 11 of the accompanying drawings. Valve actuation system 95 shown in figure 11 is identical to system 70 shown in figure 8, with the following exceptions. System 95 includes a hydraulic slack adjuster assembly 180 which includes a hydraulic slack adjusting piston 182 disposed on the lower end of slack bolt 130, and a slack spring 184 biasing slack adjusting piston 182 away from the slack bolt. 130. A small fluid opening 186 can allow hydraulic fluid to fill the interior of the slack adjuster piston 182. System 95 can perform all of the engine valve actuations described above in conjunction with figure 8.
    [067] An eleventh embodiment of the present invention is illustrated as the valve actuation system of the engine 97 in Figure 12 of the accompanying drawings. Valve actuation system 97 shown in figure 12 is identical to system 70 shown in figure 8, with the following exceptions. In system 97, passage 122 is no longer used to supply hydraulic fluid, but instead receives a sliding element 190. The sliding element may have a generally cylindrical center body, a conical or frusto-conical end 196, and a portion The passage 122 may have a double diameter to securely receive the body of the slide member and the head portion 192 of the slide member 190. A spring 194 may be disposed between a shoulder formed by the double diameter passage 122 and the head portion of the sliding element 192 so as to bias the sliding element 190 away from the outer piston 140.
    [068] In a first example, for bleed braking of the engine, hydraulic fluid at low pressure can be supplied to passage 122 under the control of the optional second control valve 172 so that the sliding element 190 engages the external piston 140 and forces the outer piston and slide pin 160 down for a bleed brake event. Fluid at low pressure can be released from passage 122 by second control valve 172 when bleed braking is no longer desired and spring 194 can cause the slider to disengage the outer piston 140 so that the outer piston retracts. -turns to its uppermost position shown in figure 12. Alternatively, hydraulic fluid can be supplied to passage 122 under the control of optional second control valve 172 to provide engine cylinder relief for engine starting rather than braking by bleeding. In all other respects, system 97 can perform all of the engine valve actuations described above in conjunction with figure 8.
    [069] It will be apparent to those skilled in the art that variations and modifications of the present invention may be made without departing from the scope or spirit of the invention. For example, a pneumatic fluid can be used instead of a hydraulic fluid in the above embodiments without departing from the intended scope of the invention. Additionally, the annular recesses described above are not shown to extend completely around the pistons in which they are provided, however, it is found that these annular recesses could extend around the entire circumference of the pistons without departing from the intended scope of this invention.
    权利要求:
    Claims (15)
    [0001]
    1. System for actuating an engine valve to decompress an engine cylinder or perform engine bleed braking, CHARACTERIZED in that it comprises: a first vertically movable element disposed above an engine valve, said first vertically movable element having an inner piston diameter that extends horizontally into the first vertically movable element; device for moving the first vertically movable element, an inner piston provided in the diameter of the horizontally extending inner piston, said inner piston having a circumference and a recessed surface, means for moving the inner piston with respect to the diameter of the inner piston; and a second vertically movable element configured to contact either the circumference of the inner piston or the recessed surface of the inner piston, wherein the circumference of the inner piston is configured so that the contact between the second vertically movable element and the circumference The inner piston seal prevents the engine valve from closing and the recessed surface of the inner piston is configured so that contact between the second vertically movable element and the recessed surface allows the opening and closing of the engine valve.
    [0002]
    2. System according to claim 1, CHARACTERIZED by the fact that the device for moving the inner piston in relation to the diameter of the inner piston comprises a device for moving the inner piston in a horizontal axial direction.
    [0003]
    3. System according to claim 1, CHARACTERIZED in that it further comprises: a first fluid supply passage extending between the device for moving the inner piston and the diameter of the inner piston, wherein the device for moving the internal piston comprises a fluid control valve.
    [0004]
    4. System according to claim 1, CHARACTERIZED by the fact that it further comprises: a housing having an outer piston diameter, wherein the first vertically movable element comprises an outer piston disposed on the diameter of the outer piston.
    [0005]
    5. System according to claim 1, CHARACTERIZED by the fact that the device for moving the first vertically movable element comprises a clearance screw.
    [0006]
    6. System according to claim 1, CHARACTERIZED by the fact that it further comprises a first spring provided in the diameter of the inner piston, said first spring predisposing the inner piston to a predefined position in the diameter of the inner piston.
    [0007]
    7. System according to claim 6, CHARACTERIZED by the fact that it further comprises: an inner diameter provided in the inner piston, wherein the first spring extends into the inner diameter.
    [0008]
    8. The system according to claim 1, CHARACTERIZED in that it further comprises: a diameter of the vertically oriented sliding pin that extends through a lower portion of the inner piston to the diameter of the inner piston, wherein the second element is vertically movable comprises a sliding pin arranged on the diameter of the sliding pin.
    [0009]
    9. System according to claim 1, CHARACTERIZED by the fact that the second vertically movable element comprises an engine valve stem.
    [0010]
    10. System according to claim 1, CHARACTERIZED by the fact that it further comprises a spring predisposing the second vertically movable element to contact with the recessed surface of the internal piston.
    [0011]
    11. System according to claim 1, CHARACTERIZED by the fact that the recessed surface of the internal piston includes first and second recesses of different depths.
    [0012]
    12. System according to claim 3, CHARACTERIZED in that it further comprises: a housing having a diameter of the outer piston, an outer piston disposed on the diameter of the outer piston, wherein the outer piston comprises the first vertically movable element and a second fluid supply passage extending between the device for moving the first vertically movable element and the diameter of the outer piston.
    [0013]
    13. System according to claim 12, CHARACTERIZED in that it further comprises a second fluid control valve, wherein the second fluid control valve comprises the device for moving the first vertically movable element.
    [0014]
    14. System according to claim 12, CHARACTERIZED by the fact that it further comprises a master piston assembly in hydraulic communication with the second fluid supply passage.
    [0015]
    15. System for actuating an engine valve to decompress an engine cylinder or perform engine bleed braking, CHARACTERIZED by the fact that it comprises: a housing mounted on an engine above one side of a valve bridge, a diameter of the piston extending horizontally into the housing, a hydraulic fluid supply passage communicating with the piston diameter, an actuator piston disposed on the piston diameter, said actuator piston having an inner chamber with an end wall, a spring predisposing the actuator piston to within the piston diameter in a direction that causes the actuator piston to engage an underlying engine valve bridge, a sleeve disposed in the inner chamber; and a spring biasing the sleeve away from the end wall of the inner chamber.
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    同族专利:
    公开号 | 公开日
    WO2013044091A1|2013-03-28|
    EP2766589B1|2019-01-16|
    US20130068195A1|2013-03-21|
    KR101542360B1|2015-08-07|
    CN103917762B|2017-05-24|
    US8863726B2|2014-10-21|
    CN103917762A|2014-07-09|
    JP5966008B2|2016-08-10|
    BR112014006435A2|2020-10-27|
    JP2014526655A|2014-10-06|
    EP2766589A1|2014-08-20|
    EP2766589A4|2016-10-19|
    BR112014006435A8|2021-03-16|
    KR20140071442A|2014-06-11|
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    法律状态:
    2020-11-10| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-12-15| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-06-01| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-06-22| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 21/09/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US201161537430P| true| 2011-09-21|2011-09-21|
    US61/537,430|2011-09-21|
    PCT/US2012/056657|WO2013044091A1|2011-09-21|2012-09-21|Method and system for engine cylinder decompression|
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