• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Abstract The invention relates to an actuator for axial displacement of an object, the actuator (l) comprises an actuator piston(7),is displaceable in the axial direction,and a hydraulic circuit (20)(21), the first end (8)(7) being arranged to be displaced in the axial direction(21),mouth in said liquid filled chamberof the The actuator is characterized in (4) comprising and an actuator piston rod wherein theactuator piston (4)comprising a liquid filledchamber of the actuator piston rodwithin said liquid filled chamber(22) and is arranged to receive the first end (8) wherein an axiallyextending recess(21)actuator piston rod (7). that the actuator piston rod (7) in the area of a first end (8) presents a cylindrical envelope surface (24), and in thatthe recess (22) presents a cylindrical inner surface (25)having matching shape, wherein the actuator comprises a (22)when the cylindrical envelope surface(25)wherein the passage presents at a(A1) thatdecrease as a function of increasing overlap between the(24) passage extending between the recessfilled chamber (21)(24) and the cylindrical inner surface overlapping configuration, and the liquid are located in braking overlap section a cross section area cylindrical envelope surface(25). and the cylindrical inner surface Publication picture: Figure 3
    公开号:SE1350398A1
    申请号:SE1350398
    申请日:2013-03-28
    公开日:2014-09-29
    发明作者:Anders Höglund
    申请人:Freevalve Ab；
    IPC主号:
    专利说明:

    The present invention relates generally to the field of devices for providing axial displacement of an object, such as actuators providing axial displacement of a valve. In particular, the present invention relates to combustion engine valve actuators. The actuator comprises an actuator piston comprising an actuator piston rod having a first end and a second end, the actuator piston vane is displaceable forwards and backwards in the axial direction between a first position and a second position, and therefor the actuator comprises a hydraulic circuit comprising a hydraulic shaft-filled actuator the first end of the rod is arranged to be displaced in the axial direction in the said liquid-filled chamber in connection with axial displacement of the actuator piston, used in an axially extending recess opening into the said liquid-filled chamber and is arranged to receive the actuating position of the actuator.
    Background of the Invention The invention is applicable to various technical fields in which an axial displacement of an object is to be provided. The invention is particularly useful in applications which have high demands on the speed and controllability of the axial displacement, and has high demands on low noise levels, such as the application to control a valve, for example an inlet valve or an outlet valve of an internal combustion engine.
    An actuator, commonly known as a pneumatic actuator, includes an actuator piston that is displaceable forward and reciprocating in the axial direction between a first position and a second position. The displacement is performed by controlling a pressure fluid, such as pressurized gas, which acts against the actuator piston, the actuator piston in turn acting against the valve, or the like, to control its position. There are Oven hydraulic actuators that work according to the same principles. 2 When the actuator piston is in its first / inactive position, the valve is in contact with its valve actuator, and when the actuator piston is in its second / active position, the valve is open, ie the bellows at a distance from said valve set.
    The axial displacement of a conventional camshaft controlled motor valve is controlled in such a way that during closing of the motor valve the closing speed is reduced just before the motor valve comes into contact with the valve seat due to the shape of the cam, however a pneumatically controlled motor valve will have accelerating or maximum closing speed. in contact with the valve seat. This causes the motor valve, valve cap and actuator piston rod to be subject to significant wear.
    In addition, the motor valve and actuator piston can bounce back, creating noise, vibration and incorrect operation of the motor.
    Thus, there is a behavior for a reduction or limitation of the closing speed just before the engine valve comes into contact with the valve seat, to reduce rebound, noise and vibration.
    Documents US 6192841, US 6412457 and US 7387095 which show prior art, show actuators for motor valves which have a controlled / decreasing closing speed at the moment of contact, however these actuators are from a technical point of view very complicated and comprise a number of movable elements to achieve the controlled / reduced closing speed.
    The second US 7,121,237 discloses an actuator arranged in accordance with the preamble of claim 1.
    OBJECT OF THE INVENTION The present invention aims to obviate the above-mentioned disadvantages and shortcomings of prior art actuators, and to provide an improved actuator. A basic object of the present invention is to provide an improved actuator of the initially defined type comprising a hydraulic brake arrangement in which the viscosity dependence of the hydraulic brake arrangement is minimized. It is another object of the present invention to provide an actuator in which the hydraulic brake arrangement is easy to manufacture. It is a further object of the present invention to provide an actuator in which the hydraulic brake arrangement only affects the return speed of the actuator piston just before the actuator piston reaches its first / inactive position, i.e. provides a short braking distance / time. It is another object of the present invention to provide an actuator which generates less noise and less vibration.
    Brief Description of the Invention According to the invention, at least the basic object is achieved by means of the initially defined actuator having the features defined in the independent claim. Preferred embodiments of the present invention are further defined in the dependent claims.
    According to the present invention there is provided an actuator of the initially defined type, which is characterized in that the actuator piston rod in the region of the first second has a cylindrical circumferential surface, and that the recess has a cylindrical inner surface, the cylindrical circumferential surface forming the inner surface and the cylindrical circumferential surface in the actuator comprises a passage extending between the recess and the liquid-filled chamber dd the cylindrical mantle surface and the cylindrical inner surface Or beldgna in overlapping configuration, used in a section of a predetermined, maximum overlap constitutes a brake overlap, the passage being named has a cross-sectional area (At) that decreases as a function of increasing overlap between the cylindrical mantle surface and the cylindrical inner surface.
    Thus, the present invention is based on the insight that by having matching cylindrical surfaces, the actuator piston rod and recess, and a defined passage between the recess and the liquid-filled chamber, where the cross-sectional circumference has been minimized relative to the cross-sectional area of the passage, .
    In a preferred embodiment of the present invention, the said cross-sectional area of the passage at the beginning of said brake overlap section decreases with decreasing derivatives, i.e. the cross-sectional area decreases with decreasing speed as a function of increasing overlap.
    In another preferred embodiment of the present invention, the said cross-sectional area of the passage at the end of said brake overlap section with increasing derivatives, i.e. the cross-sectional area decreases with increasing speed as a function of increasing overlap.
    In a further preferred embodiment of the present invention, the said cross-sectional area of the passage in said brake overlap section with constant derivatives is reduced.
    In a preferred embodiment of the present invention, the actuator piston rod has in the region of the first end a end edge with a recess which forms said passage. Preferably, said recess is formed by a groove extending from a dead surface of the first end of the actuator piston rod to the cylindrical shell surface. By only cutting a groove in the end edge of the actuator piston rod, the braking arrangement is easily manufactured by only one extra process step in connection with the manufacture of the actuator piston rod.
    According to a further preferred embodiment of the present invention, the axial length of said grooves in said cylindrical circumferential surface is greater than the maximum overlap between the cylindrical circumferential surface and the cylindrical inner surface, in order to ensure a fluid communication distance between the recess and the there is a risk that liquid will be trapped in the recess and prevent the actuator piston from fully reaching the first / inactive position.
    Preferably, the axial length of the maximum overlap is greater than 1 mm and less than 5 mm. As a result, only the last distance causes the actuator piston to reach the first position braked and the greater part of the axial displacement to be actuated.
    According to a preferred embodiment of the present invention, the hydraulic circuit has an inlet line extending into the liquid-filled chamber and an outlet line extending from said liquid-filled chamber, said outlet line having a cross-sectional area having a minimum area of at least one factor. 2 ginger maximum area has the passage cross-sectional area. Thus, the return rate of the actuator piston is further controlled to avoid a hammer effect which the first second actuator piston gear engages with the recess of the hydraulic circuit. Preferably, said minimum area has the cross-sectional area has the outlet line equal to the maximum area has the cross-sectional area has the said passage.
    Further advantages and features of the invention are apparent from other dependent claims and from the following detailed description of preferred embodiments.
    Brief Description of the Drawings A more complete understanding of the above and other features and advantages of the present invention will become apparent from the following detailed description of the preferred embodiments when taken in conjunction with the accompanying drawings, in which: Fig. 1 is a schematic cross-sectional side view; of an actuator according to the invention and an exhaust engine valve, wherein the actuator piston Or in the first / inactive position, Fig. 2 Or a schematic cross-sectional view from the side of the arrangement according to Fig. 1, wherein the actuator piston Or is in the second / active position, Fig. 3 Or a schematic cross-sectional view from the side of the arrangement according to Figures 1 and 2, the actuator piston Or in return stroke from the second / active position to the first / inactive position, Fig. 4 shows a set of schematic views of the first spirit of the actuator piston rod according to a first embodiment, Fig. 5 is a schematic cross-sectional side view of a preferred embodiment of a part of the hydraulic circuit, Fig. 6 is a schematic cross-sectional view from the side of an alternative embodiment of the recess has the hydraulic circuit, Fig. 7 is a schematic view from below of the recess taken along the line VII-VII in Fig. 6, Figs. 8-10 are different schematic Figs. 11-16 are different schematic views of the first end of the actuator piston rod according to further alternative embodiments, Fig. 17 shows a graph representing a most preferred embodiment of the passage of the passenger compartment. function of increasing overlap time, and Fig. 18 shows graphs representing a most preferred embodiment of the cross-sectional area reduction of the passage, and its derivatives, as a function of increasing overlap.
    Detailed Description of the Preferred Embodiments of the Present Invention The present invention relates to an actuator, generally designated 1, for providing axial displacement of an object, such as actuators 1 providing axial displacement of a valve. Hereinafter, the invention will, by way of example but not limitation, be described in connection with an application in which the actuator 1 is used to control at least one motor valve, i.e. an inlet or outlet valve has an internal combustion engine.
    Reference is made initially to Figures 1 and 2, showing a schematic cross-sectional side view of an actuator 1 according to the invention and an outlet motor valve, 7 generally designated 2. In the embodiment shown, the actuator 1 comprises an actuator head 3, an actuator piston, generally designated 4, and a cylinder. The actuator piston 4 comprises an actuator piston disc 6 and an actuator piston rod 7 having a first, upper end 8 and a second, lower end 9. The actuator piston rod 7 is connected to and projects in the axial direction from the actuator piston disc 6 at said second end 9 actuator 7 is displaceable in the axial direction in a hollow 10 called actuator head 3. The cylinder 5 defines a volume in which the actuator piston disc 6 is displaceable in the axial direction. The actuator piston disc 6 divides the cylinder volume into a first, upper part 11 and a second, lower part 12.
    Furthermore, the actuator 1 comprises a pressure fluid circuit, generally designated 13, arranged for controllable fluid communication with the first part 11 of the cylinder volume. More specifically, the pressure fluid circuit 12 is arranged for controllable supply of a pressure fluid, for example a gas or gas mixture, to the first part 11 of the cylinder volume. axial displacement of the actuator piston 4 from a first, inactive position to a second, active position. In addition, said pressure fluid circuit 13 is arranged for controllable evacuation of pressure fluid from the first part 11 of the cylinder volume to provide a return rate for the actuator piston 4, from said second position to said first position.
    The pressure fluid circuit 13 is connected to a pressure fluid source (HP), i.e. a high pressure head, and a pressure fluid sump (LP), i.e. a legal pressure skull. The pressurized fluid source may be a compressor driven by the internal combustion engine and a tank, or the like. The pressure fluid sink can be any place that has a lower pressure than the pressure fluid source, ie. the atmosphere or a return line leading back to said compressor. In the embodiment shown, the actuator 1 comprises an indirect electrically controlled slave valve 14 which is arranged in the pressure fluid circuit 13 for controlling the pressure fluid in said pressure fluid circuit 13. The slave valve 14 is biased towards an upper position by means of a gas spring, mechanical spring, or the like. In Figure 1, the slave valve 14 has been displaced from the upper position to its lower position, i.e. the slave valve 14 has been caused to open for pressure fluid flow from the pressure fluid source (HP) to the first part 11 of the cylinder volume. A pulse of pressure fluid will act against and displace the actuator piston disk 6 in the cylinder 5 from the position shown in Figure 1 to the position shown in Figure 2. 1 is an instantaneous picture taken when the slave valve 14 has been displaced but the actuator piston 1 has not yet started to move. The actuator piston 1 Or in the first, inactive position and will then be displaced downwards to open the motor valve 2.
    In Figure 2, the actuator piston 4 is in the second, active position, and the pressure fluid communication between the pressure fluid source (HP) and the first part 11 of the cylinder volume has been tapped, into the shown embodiment of the actuator piston rod.
    In the embodiment shown, the actuator 1 controls a motor valve 2. The motor valve comprises a valve stem 15 and a valve plate 16. The valve stem 15 extends sip through a stationary part of the internal combustion engine and into the cylinder 5 of the actuator 1, more precisely into the second part 12 of the cylinder volume. is arranged to cooperate with a valve seat 17 for alternately opening and closing for passage of gas / exhaust gases. The motor valve 2 is displaceable in the axial direction by means of the actuator 1, in that the actuator piston 4 acts against the valve shaft 15 to displace the motor valve 2 from the closed position (figure 1) to the open position (figure 2). Furthermore, the internal combustion engine preferably comprises a valve spring 18 arranged to bring the engine valve 2 back to its closed position. In the embodiment shown, the valve spring 18 consists of a coil spring, but other types of valve springs are tankable, such as a gas spring, other mechanical springs, etc. The valve spring 18 biases the motor valve 2 towards its upper position and acts against a valve spring washer 19 connected to the valve stem 15.
    According to the invention, the actuator 1 also comprises a hydraulic circuit, generally designated 20, comprising a liquid-filled chamber 21. The first end 8 Or of the actuator piston rod 7 is arranged to be displaced in the axial direction in said liquid-filled chamber 21 in connection with axial displacement of the actuator piston 4 between the first position and the second position. An axially extending recess 22 opens into said liquid-filled chamber 21 and is arranged to receive the first end of the actuator piston rod 7 8 dl the actuator piston 4 is in said first position.
    The hydraulic fluid, for example oil, can flow into the liquid-filled chamber 21 via a non-return valve 23 and out of the liquid-filled chamber via a controllable valve, which in the embodiment shown is formed by the slave valve 14. When the actuator piston 4 is displaced from the first position (Figure 1) to the second position (figure 2) the actuator piston rod 7 leaves space for inflow of liquid in the liquid-filled chamber 21 and the recess 22, and when the actuator piston 4 is displaced from the second position to the first position the liquid is forced out of the liquid-filled chamber 21 and the recess 22.
    In figure 2 the controllable valve of the hydraulic circuit is closed and the actuator piston 4 is the load / retainer in its second position, ie. motor valve 2, the hall is fully open for a predetermined, or an adapted, period of time.
    Reference is now also made to Figure 3. In Figure 3, the slay valve 14 has been shifted to the lyre position, evacuating the pressure fluid in the first part 11 of the cylinder volume during a return stroke of the actuator piston 4 from the second position (Figures 2 and 3) to the first position ( figure 1).
    At the same time, the controllable valve of the liquid-filled chamber 21 is opened to evacuate the liquid from the liquid-filled chamber 21, in order to allow displacement of the actuator piston 4 to the first position.
    According to the invention, in the area of the first end 8 of the actuator piston rod 7, the actuator piston rod 7 has a cylindrical outer surface 24. In addition, the recess 22 has a cylindrical inner surface 25, the cylindrical outer surface 24 and the cylindrical inner surface 25 having a matching shape. Furthermore, the actuator 1 comprises a passage which extends between the recess 22 and the liquid-filled chamber 21 and the cylindrical shell surface 24 and the cylindrical inner surface 25 are coated in overlapping configuration.
    Furthermore, there is a maximum overlap determined in front between the cylindrical outer surface 24 and the cylindrical inner surface 25, the actuator piston 4 being in said first position, used in a section of said maximum overlap being formed by a brake overlap 35 (see figure 1). Said passage has at said brake overlap section 35 a cross-sectional area (A1) which decreases as a function of increasing overlap between the cylindrical mantle surface 24 and the cylindrical inner surface 25.
    According to a preferred embodiment, said cross-sectional area (AO of the passage at a beginning of said brake overlap section 35 with decreasing derivatives, as a function of increasing overlap. In addition, it is preferred that said beginning of the brake overlap section 30 represents at least 30%). maximum overlap, preferably at least 40%, and preferably less than 60%.
    According to an alternative or complementary embodiment, said cross-sectional area (A1) of the passage at the end of said brake overlap section with decreasing derivatives decreases, as a function of increasing overlap. In addition, it is preferred that said end of the brake overlap section 35 represents at least 10% of the maximum overlap, preferably at least 20%, and preferably less than 40%.
    The brake overlap section 35 may comprise an intermediate portion between said beginning of the brake overlap section and said end of the brake overlap section 35, in which intermediate part the cross-sectional area (A1) of the passage decreases with constant derivative, or said beginning of the brake surface overlap may be an end portion.
    According to an alternative embodiment, said cross-sectional area (AO of the passage along the entire brake overlap section 35 with constant derivatives decreases, as a function of increasing overlap).
    According to an alternative embodiment, said cross-sectional area (AO of the passage along the entire brake overlap section 35 with increasing derivatives decreases, as a function of increasing overlap.) Preferably, the predetermined maximum overlap, in addition to said brake overlap section 35, includes a settling overlap section 36, the passage having in said settling overlap section 36 a cross-sectional area (A1) which is constant as a function of increasing overlap between the cylindrical shell surface 24 and the cylindrical inner surface 25. the transition between the brake overlap section 36 and the intersection section 35.
    In addition, said settlement overlap section 36 represents less than 20% of the maximum overlap, preferably less than 10%.
    During the return stroke, according to the embodiment shown in Figures 13, the actuator piston 4 will accelerate until the first end 8 of the actuator piston rod 7 enters the recess 22. The liquid trapped in the recess 22 above the actuator piston rod 7 will then be forced through the said decreasing passage and the actuator piston 4 is reduced at a corresponding speed. The speed of the actuator piston 4 decreases below the above-mentioned brake overlap section 35, and below the above-mentioned setting overlap section 36 a selected setting speed for the actuator piston 4 is fixed / maintained.
    Reference is now made to Figure 4, which consists of a set of views showing a first embodiment of the first end 8 of the actuator piston rod 7, used in the actuator piston rod 7 in the region of the first end 8 having an end edge 26 from which the cylindrical shell surface 24 extends. in the axial direction, and which has a recess which forms the said passage. Preferably, said recess is provided by a recess 27 extending from an end surface 28 having the first end 8 of the actuator piston rod 7 to the cylindrical circumferential surface 24. It is also preferred that the axial length of said recess 27 in the said cylindrical circumferential surface 24 be between the cylindrical jacket surface 24 and the cylindrical inner surface 25. By such a construction, the fluid communication between the recess 22 and the fluid-filled chamber 21 is securely held and no fluid will be forced into the recess 22 and prevent the actuator piston from engaging the fresh piston. Said axial length of the maximum overlap is preferably greater than 1 mm and less than 5 mm, preferably said axial length of the maximum overlap is greater than 1.5 mm and less than 3.5 mm. A most ferrroden ldngd dr about 2.0-2.5 mm.
    Referring now to Figure 5. The hydraulic circuit 20 has an inlet conduit 29 leading into the liquid-filled chamber 21 and an outlet conduit 30 leading out of said liquid-filled chamber 21, said outlet conduit having a cross-sectional area (A2) having a minimum area as an area. less than a factor 2 times the maximum area has the cross-sectional area of the passage (A1), preferably less than a factor of 1.5 and most of all less In a factor of 1.1. Preferably, where the minimum area has the cross-sectional area (A2) of the outlet line 30 at least equal to the maximum area, the cross-sectional area (A1) of said passage has. Thus, the acceleration has the actuator piston 4 before the actuator piston rod 7 first end 8 rid /. the recess 22 is controlled / limited, and no sudden differences in speed will occur when the first end 8 of the actuator piston rod 7 enters the recess 22. In the embodiment shown, the minimum cross-sectional area (A2) of the outlet line 30 is constituted by a displacement 31.
    Reference is now made to Figures 6 and 7 which show an alternative embodiment of the recess 22 having the hydraulic circuit 20. The recess 22 has an orifice and the cylindrical inner surface 25 extends in axial direction from said orifice. To this end, said mouth has a depression which forms said passage between the recess 22 and the liquid-filled chamber 21.
    Reference is now made to Figures 8-10, schematically showing alternative embodiments of the first end 8 of the actuator piston rod 7. In order to maximize the weldability of the drawings, the width of the passage is constantly tilted in the figures, the width being taken in a direction perpendicular to the drawings. It should be understood, however, that the width of the passage does not have to be constant.
    Figure 8 illustrates an embodiment in which the cross-sectional area (A1) of the passage at the said brake overlap section 13 decreases with constant derivatives, as a function of increasing overlap. Figure 9 illustrates an embodiment in which the cross-sectional area (A1) of the passage at the end of the brake overlap section 35 decreases with increasing derivatives, as a function of increasing overlap. Figure 10 illustrates an embodiment in which the cross-sectional area (AI) of the passage at the beginning of said brake overlap section 35 decreases with decreasing derivatives, and at the end of the brake overlap section 35 decreases with decreasing derivatives, as a function of decreasing overlap. Suedes, in Figure 10, there is provided a preferred S-shaped reduction of the cross-sectional area (A1) of the passage, in the brake overlap section 35, as a function of increasing overlap between the cylindrical shell surface 24 and the cylindrical inner surface 25.
    Reference is now made to Figures 11-16, which show examples of different sets of views of the first end 8 of the actuator piston rod 7 according to alternative embodiments, in which various steps have been taken to obtain the inventive reduction of the passage cross-sectional area (A1).
    In Figures 11 and 12, the recess 27 comprises a bottom surface 32 which is bag-shaped along the axial extent of the actuator piston rod. In the embodiment shown in Figure 4, the groove 27 comprises a bottom surface which is flat and straight. In Figures 13 and 14, the recess 27 comprises a bottom surface 32 which is bag-shaped along the transverse extension of the actuator piston rod.
    In Figures 4, 11 and 13, the spar 27 comprises parallel side surfaces 33, i.e. constant width, and in the embodiment shown in Figure 12, the recess 27 includes converging side surfaces 33, in the direction from the front end of the actuator piston rod.
    In Figures 15 and 16, the recess is formed by a bevel 34. In the embodiment shown in Figure 15, the bevel 34 is rear-shaped along the axial extent of the actuator piston rod, and in the embodiment shown in Figure 16 the bevel is flat. Each feature has the aforementioned groove 27 (Jailer also has the aforementioned bevel 34, in addition to the features that touch the side surfaces 33 of the spar 27.
    According to an alternative, not shown, embodiment, the cross-sectional area (A1) of the passage along the entire brake overlap section 35 with Okande derivatives decreases, as a function of Okande 14 Overlap, for example the spare may comprise parallel side surfaces and the bottom surface may have the shape of a circular bag.
    According to a most preferred embodiment of the invention, the cross-sectional area (A1) of the passage at said brake overlap section 35 decreases exponentially as a function of increasing overlap time, see Figure 17. To achieve this exponential reduction of passage cross-sectional area, as a function of increasing overlap time, the passage cross-sectional area (A1) approximately according to a polynomial function along the brake overlap section 35, see Figure 18. In Figure 18, the line designated 37, starting at about 2 mm2 of passage cross-sectional area and 0 mm overlap, represents the passage cross-sectional area as a function of overlap. The "U" -shaped line designated 38, represents the derivative of the passage cross-sectional area 37 as a function of overlap. In Figure 18, the cross-sectional area (A1) of the passage decreases at the beginning of said brake overlap section 35 with decreasing derivatives, and at the end of said brake overlap section with increasing derivatives, as a function of increasing overlap between the cylindrical outer surface 24 and the cylindrical inner surface 25.
    Conceivable modifications of the invention The invention is not limited only to the embodiments described above and shown in the drawings, which are for illustrative and exemplary purposes only. This patent application is intended to thank all the adaptations and variants of the preferred embodiments described herein, and consequently the present invention is defined by the wording of the appended claims and thus the equipment may be modified in any conceivable manner within the scope of the appended claims.
    It should also be noted that all information about / moving terms such as above, below, upper, lower, etc., shall be interpreted / read with the equipment oriented in accordance with the figures, with the drawings oriented in such a way that the reference numerals can be read correctly. Thus, such terms indicate only conditions embedded in the embodiments shown, which conditions may be different if the inventive equipment is provided with a different construction / design.
    It should be pointed out that although it is not explicitly stated that features from a specific design can be combined with features from another design, this should be considered as obvious as possible.
    权利要求:
    Claims (17)
    [1] 1. Claimsl. An actuator for axial displacement of an object, theactuator (l) comprises: - an actuator piston (4) comprising an actuator piston rod(9), is displaceable in the axial direction in (7) having a first end (8) and a second end wherein the actuator piston (4)a reciprocating manner between a first position and a secondposition, and - a hydraulic circuit (20) comprising a liquid filled chamber (2l), the first end (8) of the actuator piston rod (7) beingarranged to be displaced in the axial direction within saidliquid filled chamber (2l) in conjunction with axialdisplacement of the actuator piston (4), wherein an axially extending recess (22) mouth in saidliquid filled chamber (2l) and is arranged to receive the first end (8) actuator piston (4) of the actuator piston rod (7) when theis in said first position, characterized in that the actuator piston rod (7) in thearea of the first end (8)(24),cylindrical inner surface(24) presenting matching shapes, presents a cylindrical envelope(22)the cylindrical envelope(25) wherein the actuator comprises a(22)when the cylindrical envelope surface(25) wherein a section of a and in that the recess(25), and the cylindrical inner surface surface presents a surface passage extending between the recessfilled chamber (21)(24) and the cylindrical inner surface overlapping configuration, and the liquid are located in predetermined maximum overlap is constituted by a braking overlap (35), the passage presenting at said braking overlapsection (35) a cross section area (A1) that decrease as afunction of increasing overlap between the cylindrical envelope surface (24) and the cylindrical inner surface (25).
    [2] 2. The actuator according to claim l, wherein said cross(Ai) braking overlap section section area of the passage at a beginning of said(35) as a function of increasing overlap. decrease with decreasing derivative, 17
    [3] 3. The actuator according to claim 2,(35) wherein said beginningof the braking overlap section represent at least 30% ofthe maximum overlap.
    [4] 4. The actuator according to any of claims 1-3, wherein said(Ai) braking overlap section cross section area of the passage at an end of said(35) as a function of increasing overlap. decrease with increasingderivative,
    [5] 5. The actuator according to claim 4, wherein said end of the braking overlap section (35) represent at least 10% of the maximum overlap.
    [6] 6. The actuator according to claim 1, wherein said cross(Ai) decrease with constant derivative, section area(35) of increasing overlap. of the passage at said braking overlap section as a function
    [7] 7. The actuator according to any preceding claim, wherein thepredetermined maximum overlap,(35) (35), in addition to said brakingoverlap section and adjacent an end of the brakingoverlap section(36), the passage presenting at said seating overlap section(36) (AUof increasing overlap between the cylindrical envelope (24) (25). comprises a seating overlap sectiona cross section area that is constant as a functionsurface and the cylindrical inner surface
    [8] 8. The actuator according to claim 7,(36) wherein said seatingoverlap section represent less than 20% of the maximumoverlap.
    [9] 9. The actuator according to any preceding claim, wherein the axial length of the maximum overlap is greater than 1 mm, andless than 5 mm, preferably about 2,5 mm.
    [10] 10. The actuator according to any preceding claim, wherein the actuator piston rod (7) in the area of the first end (8) 18 presents an end edge (26) having an indentation forming said passage.
    [11] 11. The actuator according to claim 10, wherein said indenta-tion is constituted by a groove (27)(28) of the first end (8) (7) to the cylindrical envelope surface extending from an endsurface of the actuator piston rod(24).
    [12] 12. The actuator according to claim 11, wherein the axial length of said groove (27) in said cylindrical envelopesurface (24) is greater than the maximum overlap between thecylindrical envelope surface (24) and the cylindrical innersurface (25).
    [13] 13. The actuator according to claim 11 or 12, wherein said(27) (32) along the axial direction of the actuator piston rod (7). groove comprises a bottom surface that is arced
    [14] 14. The actuator according to any of claims 11-13, wherein said groove comprises parallel side surfaces (33).wherein(29)and an outlet conduit(21), presenting a cross section area
    [15] 15. The actuator according to any preceding claim,(20)into the liquid filled chamber(30) outlet conduit has an inlet conduit(21)leading from said liquid filled chamber said(30) (Åfihaving a minimum area that is less than a factor 2 times the(Ai) the hydraulic circuit leading maximum area of the cross section area of said passage, preferably less than a factor 1,5. wherein the minimum of the outlet conduit
    [16] 16. The actuator according to claim 15,(Äfi(30) is equal to or bigger than the maximum area of the cross(Ai) area of the cross section area section area of said passage.
    [17] 17. The actuator according to any preceding claim, wherein the actuator comprises: 19 - a cylinder (5), wherein the actuator piston (4) comprisesan actuator piston disc (6) displaceable in the axialdirection within said cylinder (5) in conjunction with axialdisplacement of the actuator piston (4), and - a pressure fluid circuit (13) arranged for controllable fluid communication with the cylinder (5).
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    同族专利:
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    EP2978944B1|2019-07-03|
    BR112015024903A2|2017-07-18|
    JP6382300B2|2018-08-29|
    RU2015146056A3|2018-03-06|
    EP2978944A4|2016-11-30|
    CN105143613A|2015-12-09|
    US9964006B2|2018-05-08|
    CN105143613B|2018-05-25|
    JP2016519743A|2016-07-07|
    SE537203C2|2015-03-03|
    WO2014158087A1|2014-10-02|
    RU2651002C2|2018-04-18|
    RU2015146056A|2017-05-18|
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    SE535886C2|2011-06-03|2013-02-05|Ase Alternative Solar Energy Engine Ab|Pressure Pulse Generator|SE540421C2|2015-04-16|2018-09-11|Freevalve Ab|Actuator for axial displacement of an object|
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    SE542266C2|2017-09-11|2020-03-31|Freevalve Ab|Internal combustion engine and method for controlling such an internal combustion engine|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1350398A|SE537203C2|2013-03-28|2013-03-28|Actuator for axial displacement of an object|SE1350398A| SE537203C2|2013-03-28|2013-03-28|Actuator for axial displacement of an object|
    EP14774657.2A| EP2978944B1|2013-03-28|2014-03-27|Actuator for axial displacement of an object|
    US14/780,934| US9964006B2|2013-03-28|2014-03-27|Actuator for axial displacement of an object|
    JP2016505435A| JP6382300B2|2013-03-28|2014-03-27|Actuator for axial displacement of object|
    KR1020157030964A| KR20150134426A|2013-03-28|2014-03-27|Actuator for axial displacement of an object|
    CN201480018100.5A| CN105143613B|2013-03-28|2014-03-27|For the actuator of the axial displacement of object|
    RU2015146056A| RU2651002C2|2013-03-28|2014-03-27|Actuator for axial displacement of object|
    BR112015024903A| BR112015024903A2|2013-03-28|2014-03-27|trigger for axial displacement of an object|
    PCT/SE2014/050366| WO2014158087A1|2013-03-28|2014-03-27|Actuator for axial displacement of an object|
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