• 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:
    The invention relates to an actuator for axial displacement of an object, the actuator comprises an actuator piston disc (4) and an actuator piston rod (7) which together form an actuator piston, a cylinder volume, the actuator piston disc (4) dividing said cylinder volume into a first part (5) and a second part (6) and is displaceable in said cylinder volume between an inactive and an active position, a pressure fluid circuit (10) arranged for controllable fluid communication with the first part (5) of the cylinder volume, and a first hydraulic circuit (21) comprising a liquid-filled space ( 22), wherein the actuator piston rod (7) is arranged to be displaced in axial direction relative to said liquid-filled space (22) in connection with axial displacement of the actuator piston disc. (4) in the cylinder volume. The actuator is characterized by that. the actuator piston comprises a second hydraulic circuit (24), the liquid-filled space (22) being in fluid communication with an inner cavity (25) in the second hydraulic circuit (24) when the actuator piston disk (4) is in said inactive position, said inner cavity (25) ) is partially defined by a positioning piston (29) which is displaceable relative to the actuator piston and which is arranged to abut against said object in the second part (6) of the cylinder volume, the second hydraulic circuit (24) comprising a valve (27) arranged to prevent fluid flow from the inner cavity (25). Publication image: Figure 1
    公开号:SE1250793A1
    申请号:SE1250793
    申请日:2012-07-06
    公开日:2014-01-07
    发明作者:Anders Hoeglund
    申请人:Cargine Engineering Ab；
    IPC主号:
    专利说明:

    The device is to reduce the speed of movement of the engine valve just before the valve plate of the engine valve comes into contact with the valve seat in the cylinder of the internal combustion engine and thereby obtain a controlled closing movement, in order to spare the included parts and reduce wear and noise. When closing the motor valve, the actuator piston rod must come into contact with a mechanical stop in the actuator housing at the same time as the motor valve comes into contact with its seat, in order to obtain correct braking of the motor valve and the actuator piston in connection with closing the motor valve.
    It is of utmost importance that the mutual distance between the hydraulic brake device of the actuator piston rod and the valve plate of the motor valve is equal to the mutual distance between the mechanical stop and the seat of the motor valve. The problem with known actuators is that the actuator piston rod does not reach its mechanical stop in the actuator housing, whereupon the braking effect varies or is completely absent.
    Due to the fact that the motor valve is exposed to high temperatures during operation, its valve stem will undergo dimensional changes, which directly affects the above condition. In addition, the manufacturing costs will be high if the dimensional tolerances in the manufacture of the included parts are tight, alternatively less tight dimensional tolerances are used, which entails a need to use shims / spacers or the like to adjust the mutual positions of the parts. Furthermore, the constituent parts wear during operation, which further affects the mutual positions of the parts.
    It should be mentioned that the actuator piston rod, in addition to the hydraulic brake device, also has other functions where its position relative to the actuator housing is used for different purposes, to determine the size of the first part of the cylinder volume, to regulate fluid communication with the first part of the cylinder volume, etc. Brief Description of the Objects 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 invention is to provide an improved actuator of the initially defined type, which ensures that the actuator piston rod always assumes a pre-defined inactive position when the actuator is in the rest position.
    Brief description of the features of the invention According to the invention, at least the basic object is achieved by means of the initially defined actuator, which has 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 comprises a second hydraulic circuit, the liquid-filled space of the first hydraulic circuit being in fluid communication with an inner cavity in the second hydraulic circuit when the actuator piston disk is position, said inner cavity being partially delimited by a positioning piston, which is axially displaceable back and forth relative to the actuator piston and which is arranged to abut against said object, which for example consists of a motor valve, in the second part of the cylinder volume, the second hydraulic circuit comprises a valve arranged to prevent fluid flow from the inner cavity.
    Thus, the present invention is based on the insight that by means of a movable positioning piston relative to the actuator piston it can be ensured that the actuator piston rod always assumes a pre-defined inactive position when the motor valve is closed and the actuator inactive.
    According to a preferred embodiment of the present invention, the actuator piston rod has a free end, which is arranged to abut at least partially against a stop surface in the liquid-filled space, when the actuator piston disc is in the inactive position.
    In a further preferred embodiment, the actuator piston rod in the region of its free end has a hydraulic braking device, which is arranged to reduce the speed of movement of the actuator piston before the free end of the actuator piston rod comes into contact with said stop surface.
    Additional advantages and features of the invention will be apparent from the 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 preferred embodiments when taken in conjunction with the accompanying drawings, in which: Fig. 1 is a schematic, sectional side view; of an actuator according to a first embodiment, the actuator piston being located in an inactive position, Fig. 2 is a schematic, sectioned side view of the actuator piston showing the actuator shown in Fig. 1, Fig. 3 is an enlargement of a part of the actuator according to Figures 1 and 2, showing the inner cavity of the second hydraulic circuit, Fig. 4 is a schematic, sectioned side view of an actuator according to a second embodiment, the actuator piston being located in an inactive position, and Figs. 5 is a schematic, sectional side view of the actuator showing the actuator piston in an active position.
    Detailed Description of Preferred Embodiments The present invention relates to an actuator, an object. generally designated 1, for axial displacement of the invention will now be described, by way of example but not limitation, with reference to an application in which the actuator 1 is used for driving one or more inlet valves or outlet valves in the cylinder of an internal combustion engine.
    Reference is made initially to Figures 1 and 2, which show a first embodiment of the actuator 1 according to the invention. The actuator 1 comprises an actuator housing 2, a cylinder 3 delimiting a cylinder volume or chamber, an actuator piston disc 4 which is axially displaceable back and forth in said the cylinder volume between an inactive position (Figure 1) and an active position (Figure 2).
    The actuator piston disc 4 divides said cylinder volume into a lower part 6.
    Furthermore, the actuator 1 comprises an actuator piston rod, first, upper part 5 and a second, generally designated 7, which is fixedly connected to and axially projecting from the actuator piston disk 4, and which together with the actuator piston disk forms an actuator piston.
    In the embodiment shown, the actuator piston rod 7 has a first, coarser portion 8, which is located at a distance from the actuator piston disc 4 and which closes tightly against a bore in the actuator housing 2, and a second, tapered portion 9 which extends between and connects the coarser portion 8. and the actuator piston disc 4.
    The actuator 1 also comprises a pressure fluid circuit, generally designated 10, arranged for controllable supply of a gas or gas mixture to the first part 5 of the cylinder volume to start a pressure pulse, and arranged for controllable evacuation of the gas or gas mixture from the cylinder volume first part 5 to terminate said pressure pulse.
    The pressure fluid circuit 10 is connected to a pressure fluid source (HP) (LP). The source of pressure fluid can be a compressor belonging to the engine with an associated tank and a pressure fluid sink or only a pressure tank. The pressure fluid sink can be any point with a lower pressure than that generated in the pressure fluid source, leading back to the compressor. for example the atmosphere or a line which in the embodiment shown comprises the actuator 1 a directly or indirectly, electrically controlled first valve body 11, which first valve body 11 is arranged in the pressure fluid circuit 10 for controlling the pressure fluid flow in the pressure fluid circuit 10. By electrically controlled is meant controlled by means of an electromagnetic device, by means of a piezoelectric device, etc. In a preferred embodiment, the actuator 1 further comprises a so-called pilot valve 12 in the form of a three-way valve, which pilot valve 12 is arranged to be driven by an electromagnet 13. The pilot valve can also consists of a piezoelectric valve, or other such electrically controlled valve. The pilot valve 12 is arranged to alternately open to an activation channel 14 for fluid communication with the pressure fluid source (HP) (LP).
    Furthermore, the upper end of the first valve body 11 is arranged in the respective pressure fluid lowering the activation channel 14, whereupon the pressure fluid flow from the pressure fluid source can act against and displace the first valve body 11 downwards. The pilot valve 12 is preferably biased in a first direction (to the right) by means of a gas spring, mechanical spring or the like, whereupon an activation of the electromagnet 13 causes the pilot valve 12 to be displaced in a second direction (to the left) and when the electromagnet 13 is turned off pilot valve 12 by displacing in the other direction (to the right). The figures thus show that the first valve body 11 is indirectly electrically controlled. In the case where the electromagnet 13 acts directly on the first valve body 11, the first valve body 11 is directly electrically controlled, i.e. in this embodiment the pilot valve and the activation channel are missing.
    When the pilot valve 12 opens for pressurized fluid flow from the pressurized fluid source to the actuation channel 14, the first valve body 11 is displaced to a lower position, shown in Figure 1. Thus, the first valve body 11 is caused to open for pressurized fluid flow in the pressurized fluid circuit with which the pressurized fluid circuit 10 is to the first part of the cylinder volume 5. A pulse of pressure fluid will then act against and displace the actuator piston disk 4 in the cylinder volume from the position shown in Figure 1 to and past the position shown in Figure 2. Figure 1 thus shows an instantaneous image when the first valve body 10 has been displaced but the actuator piston disc 4 has not yet begun to move. Thus, in Figure 1, the actuator piston remains in its inactive position, and will then begin its downward movement to generate a pressure pulse.
    Figure 2 shows the actuator piston disc 4 in its active position, and the coarser portion 8 of the actuator piston rod 7 has closed the pressure fluid circuit 10 to prevent further inflow of pressure fluid from the pressure fluid source to the first part of the cylinder volume. Figure 2 also shows that the pilot valve 12 has been displaced in the second direction (to the right) to allow fluid communication between the pressure fluid lowering and the actuating channel 14, and thus the first valve body 11 which is biased in the upward direction by means of a gas spring, or the like, a mechanical spring, has been displaced to the upper position, for evacuating the gas in the first part 5 of the cylinder volume to allow return movement of the actuator piston disc 4 from its active position to its inactive position. Thus, when evacuation occurs, the actuator piston disk 4 returns to the inactive position shown in Figure 1.
    In the embodiments shown, the actuator 1 cooperates with a motor valve, generally designated 15, valve stem 16 and a valve plate 17. having a valve stem 16 extending through a stationary part of the internal combustion engine and into the cylinder 3 of the actuator 1, and more specifically into the second part 6 of the cylinder volume, and the valve plate 17 is arranged to cooperate with a valve seat 18 in order to alternately allow and prevent the passage of gas / air to the cylinder of the internal combustion engine. The motor valve 15 is displaceable in the axial direction by means of the actuator 1, in that the actuator piston disc 4 of the actuator 1 acts indirectly on an upper end of the valve stem 16 of the valve 15 to displace the valve 15 to its open position (Figure 1). ). Furthermore, the internal combustion engine preferably comprises a conventional, schematically shown, valve spring 19, which is arranged to return the valve 15 from its open position to its closed position. The valve spring 19 acts at its lower end directly or indirectly against the stationary part of the internal combustion engine, and at its upper end against a driver 20, or valve spring washer, which is connected to the valve stem 16 in the region of its upper end.
    The actuator 1 also comprises a first hydraulic circuit, generally designated 21, 22, the actuator piston rod 7 being arranged to be displaced in axial comprising a liquid-filled space joint relative to said liquid-filled space 22 in connection with axial displacement of the actuator piston disc 4 in the cylinder volume. Liquid can flow into the liquid-filled space 22 via a non-return valve 23 and out of the liquid-filled space 22 via a controllable valve, which in the shown actuator-to-actuator piston rod 7 the embodiment consists of the first valve 11. the piston is displaced from the inactive position (figure 1) the active position (figure 2) place for inflow of liquid into the liquid-filled space 22, and when the actuator piston is displaced from the active position to the inactive position, liquid is forced out of the liquid-filled space 22.
    Reference is now also made to Figure 3, which enlarged shows a part of the actuator according to the embodiment shown in Figures 1 and 2. According to the actuator 1 according to the invention, the actuator piston comprises a second hydraulic circuit, designated 24, when the actuator piston disc 4 is in said inactive position, is generally which in turn comprises an inner cavity 25. the liquid-filled space 22 of the first hydraulic circuit 21 in fluid communication with the inner cavity 25 in the second hydraulic circuit 24. end in the inner cavity 25 and in a second end in An inner channel 26 opens into a first circumferential surface of the coarser portion 8 of the actuator piston rod 7. The second end of the inner channel 26 should thus be arranged in fluid communication with the liquid-filled space 22 when the actuator piston disc 4 is in the inactive position, and further said fluid communication broken when the actuator piston disc 4 is in the active position.
    Furthermore, the second hydraulic circuit 24 comprises a valve 27 arranged to prevent fluid flow from the inner cavity 25 to the liquid-filled space 22. Preferably, said valve 27 is a non-return valve, which is held in a position sealing the inner channel 26 by means of a non-return valve. valve spring 28.
    The inner cavity 25 is partially delimited by a positioning piston 29, which is axially displaceable back and forth relative to the actuator piston and which is arranged to act on the motor valve 15 in the second part 6 of the cylinder volume. The liquid contained in the inner cavity 25 is allowed to leak past the positioning piston 29 into the second part 6 of the cylinder volume.
    The actuator piston rod 7 has a free end 30, which is arranged to lie at least partially than against a stop surface 31 in the liquid-filled space 22. In the embodiment according to the figures when the actuator piston disc 4 is in the inactive position. 1-3, the positioning piston 29 is biased towards the second part 6 of the cylinder volume by means of a spring 32 arranged in the inner cavity 25. When the valve plate 17 of the motor valve 15 reaches its seat 18 and the free end 30 of the actuator piston rod 7 does not abut said stop surface 31. The positioning piston 29 will abut the motor valve 15 and the spring 32 will push the actuator piston axially upwards until the free end 30 of the actuator piston rod 7 abuts against the stop surface 31, while liquid is pressed in and retained in the inner cavity 25. Thus, the task of the positioning piston 29 is to position the actuator piston in the correct position each time the actuator piston disc 4 is in the inactive position.
    The positioning piston 29 has a pressurized area, i.e. an area constituted by the axially projecting area of the positioning piston against which the liquid in the inner cavity 25 acts to prevent the positioning piston 29 from being pressed into the inner cavity 25. In the embodiment according to Figures 1-3 the pressurized area of the positioning piston 25 is facing the inner cavity 25, equal to or less than the pressurized area of the free end 30 of the actuator piston rod 7.
    In the shown embodiments of the actuator 1 according to the invention, the actuator piston rod 7 in the region of its free end has a hydraulic braking device, which is arranged to reduce the speed of movement of the actuator piston before the free end 30 of the actuator piston 7 comes into contact with said stop valve 31. speed of movement before the motor valve 15 comes into contact with its seat 18. The hydraulic brake device consists of a geometric constriction between the actuator piston rod 7 and the liquid-filled space 22, which geometric constriction decreases as the free end 30 of the actuator piston rod 7 approaches said stop end. now to Figures 4 and 5, whereby the braking force increases. which show the actuator 1 according to the invention according to a second embodiment. Only differences in relation to the first embodiment will be described. In this second embodiment, the pressurized area of the positioning piston 29 facing the inner cavity 25 is larger than the pressurized area of the free end 31 of the actuator piston rod 7. At the same time, no spring is needed which pushes apart the positioning piston 29 and the actuator piston, such as is required in the embodiment according to Figures 1 to 3. However, the location of the other end of the inner channel 26 which opens into the outer surface of the coarser portion 8 of the actuator piston rod 7 is extremely important. The other end of the inner channel 26 should be arranged in fluid communication with the liquid-filled space 22 when the actuator piston disc 4 is in the inactive position, and further said fluid communication should be broken immediately after the actuator piston disc 4 has left the inactive position. If the internal channel 26 is not broken when the actuator piston disc 4 is in the active position, the actuator piston will be pressed upwards and thereby prevent the motor valve 15 from closing correctly.
    Possible modifications of the invention The invention is not limited only to the embodiments described above and shown in the drawings, which have only illustrative and exemplary purposes. This patent application is intended to cover all adaptations and variants of the preferred embodiments described herein, and consequently the present invention is defined by the wording of the appended claims and their equivalents. Thus, the equipment can be modified in any conceivable way within the scope of the appended claims.
    It should also be pointed out that all information about / concerning is to be interpreted / read with the equipment oriented in accordance with terms such as above, below, upper, lower, etc., the figures, with the drawings oriented in such a way that the reference numerals can be read correctly.
    Thus, such terms only indicate the mutual relations in the embodiments shown, which conditions can be changed if the equipment according to the invention is provided with a different construction / design. 12 It should be pointed out that even if it is not explicitly stated that features of a specific design can be combined with the features of another design, this should be considered obvious when possible.
    权利要求:
    Claims (7)
    [1]
    Actuator for axial displacement of an object, the actuator comprising - an actuator piston disc (4), - an actuator piston rod (7), which is fixedly connected to and (4), and which together with the actuator piston disk forms an actuator piston, axially projecting from the actuator piston disc - a cylinder volume, the actuator piston disc (4) dividing said cylinder volume into a first part (5) and a second part (6) and being axially reciprocable in said cylinder volume between an inactive position and an active position, (10 ) communication with the first part (21) of the cylinder volume, wherein the actuator piston rod (7) arranged for controllable fluid (5), comprising a liquid-filled - a pressure fluid circuit and - a first hydraulic circuit (22), is displaced in axial direction relative to said liquid-filled space (22) ( 4) in the cylinder volume, space is arranged to be in connection with axial displacement of the actuator piston disc characterized in that the actuator piston comprises a second hydraulic circuit (24), the first hydraulic The liquid-filled space (22) of the circuit (21) is in fluid communication with an inner cavity (25) in the other is in said (25) which in the axial direction the hydraulic circuit (24) wherein said inner cavity (29) is reciprocated displaceable relative to the actuator piston and when the actuator piston disc (4) is inactive position, partially delimited by a positioning piston which is arranged to press said object in cylinder (6), a valve comprises the second part of the valve, the second hydraulic circuit (24) (27) fluid flow from the internal cavity arranged to prevent (25).
    [2]
    An actuator according to claim 1, wherein the valve (27) in said second hydraulic circuit (24) is a non-return valve. 10 15 20 25 14
    [3]
    Actuator according to claim 1 or 2, (29) second part (6), wherein the positioning piston is biased in the direction into the cylinder volume by means of a spring (32).
    [4]
    An actuator according to any one of claims 1-3, wherein the actuator (30), arranged to abut at least partially against a stop surface (22), is in the inactive position. the piston rod (7) has a free end which is (31) in the liquid-filled space when the actuator piston disc (4)
    [5]
    The actuator of claim 4, wherein the positioning piston (29) (25) is equal to or less than the pressurized area of the actuator (30). pressurized area facing the inner cavity free end of the piston rod (7)
    [6]
    The actuator according to claim 4, wherein the positioning piston (29) (25) is larger than the pressurized area of the actuator piston rod (7) (30). pressurized area, facing the free end of the inner cavity, the actuator- (30) UPPV- which is arranged to
    [7]
    Actuator according to any one of claims 4-6, the piston rod (7) in the region of its free end icing a hydraulic brake device, reducing the speed of movement of the actuator piston before the free end (30) of the actuator piston rod (7) comes into contact with said stop surface (31).
    类似技术:
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    同族专利:
    公开号 | 公开日
    JP2015522120A|2015-08-03|
    BR112015000007A2|2017-08-01|
    RU2015103924A|2016-08-27|
    US20150184558A1|2015-07-02|
    KR20150036415A|2015-04-07|
    EP2872748B1|2018-11-14|
    JP6200499B2|2017-09-20|
    CN104641080B|2017-06-23|
    CN104641080A|2015-05-20|
    EP2872748A4|2016-04-20|
    SE543886C2|2021-09-14|
    RU2628465C2|2017-08-17|
    EP2872748A1|2015-05-20|
    WO2014007727A1|2014-01-09|
    US9228459B2|2016-01-05|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1250793A|SE543886C2|2012-07-06|2012-07-06|Actuator for axial displacement of a gas exchange valve at an internal combustion engine|SE1250793A| SE543886C2|2012-07-06|2012-07-06|Actuator for axial displacement of a gas exchange valve at an internal combustion engine|
    BR112015000007A| BR112015000007A2|2012-07-06|2013-06-26|actuator for axial displacement of a gas exchange valve in a combustion engine|
    JP2015520121A| JP6200499B2|2012-07-06|2013-06-26|Actuator for axial displacement of gas exchange valve in combustion engine|
    PCT/SE2013/050780| WO2014007727A1|2012-07-06|2013-06-26|Actuator for axial displacement of a gas exchange valve in a combustion engine|
    US14/408,625| US9228459B2|2012-07-06|2013-06-26|Actuator for axial displacement of a gas exchange valve in a combustion engine|
    CN201380035998.2A| CN104641080B|2012-07-06|2013-06-26|Actuator for moving axially the scavenging air valve in internal combustion engine|
    EP13813244.4A| EP2872748B1|2012-07-06|2013-06-26|Actuator for axial displacement of a gas exchange valve in a combustion engine|
    KR20157003169A| KR20150036415A|2012-07-06|2013-06-26|Actuator for axial displacement of a gas exchange valve in a combustion engine|
    RU2015103924A| RU2628465C2|2012-07-06|2013-06-26|Actuating unit for axial deflection of gas-exchanging valve in combustion engine|
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