• 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:
    24 Summary The invention relates to an actuator for axial displacement of an object. The actuator comprises an actuator piston disc which is displaceable in a cylinder volume, an inlet channel (11), a first inlet valve body (15) arranged in the inlet channel (11), a second inlet valve body (9) operatively connected to an actuator piston ( 11), an outlet channel (13) and an outlet valve body (17) arranged therein. The actuator is characterized in that it comprises an electrically controlled pilot valve (19) arranged to communicate a first control pressure to the first inlet valve body (15) via a first control pressure passage (21) and arranged to communicate a second control pressure to the outlet valve body (17) (22), wherein the pilot valve (19) is arranged to assume a dormant state, in which the first control pressure channel (21) Or in fluid communication with a control fluid inlet (25) has the pilot valve (19) and the second control pressure channel (22) Or in fluid communication with a control fluid outlet (26) has the pilot valve (19) and an active state, respectively, in which the first control pressure channel (21) Or in fluid communication with the control fluid outlet (26) and the second control pressure channel (22) Or in fluid communication with the control fluid inlet (25).
    公开号:SE1350849A1
    申请号:SE1350849
    申请日:2013-07-08
    公开日:2015-01-09
    发明作者:Anders Höglund
    申请人:Freevalve Ab；
    IPC主号:
    专利说明:

    The present invention relates to an actuator for axial displacement of an object. The dangerous invention is particularly useful in applications which have requirements for high speeds and precise controllability having the axial displaceability, as well as requirements for low operating noise. In particular, the present invention relates to a gas exchange valve actuator for internal combustion engines, where the actuator is proposed to be used for driving one or more inlet valves or outlet valves which control the supply and evacuation of air relative to the cylinder of the internal combustion engine. The actuator according to the invention is thus specially lit for driving motor valves and thus eliminates the need for one or more camshafts in an internal combustion engine.
    The actuator according to the invention comprises an actuator piston disc and a cylinder volume, the actuator piston disc dividing said cylinder volume in a first part and a second part and Or in axial direction forwards and displaceably in said cylinder volume between a rest position and an active position, and further comprises an inlet channel extends between a pressure fluid inlet and the first part of the cylinder volume, a first inlet valve body and a second inlet valve body 25 arranged in said inlet duct, an outlet duct extending between the first part of the cylinder volume and a pressure fluid outlet, and an outlet outlet valve name body.
    Background of the Invention and Prior Art An actuator, commonly known as a pneumatic actuator, thus includes an actuator piston disk that is displaceable in the axial direction between a first position (rest position) and a second position (active / extended position). The displacement is obtained by controlling supply 2 of a pressure fluid, such as pressurized gas / air, which acts against the actuator piston disc. The actuator piston disc in turn acts directly or indirectly against the object to be displaced, for example a motor valve, to control its position.
    When the actuator piston disc is in the rest position, the motor valve is in contact with the same sate, and when the actuator piston disc is in the active position, the motor valve is open, ie. coated at a distance from the same seat.
    Applicant's own document WO 2013-058704 describes an actuator in a pressure pulse which is drilled by a first inlet valve body opening and allowing pressure fluid from a pressure fluid source to act against and drive the actuator piston disc from its resting, phase to rise by a second valve is fixedly connected to and coincidentally displaceable with the actuator piston disc, cuts off the flow from the pressure fluid source and clamed rods the inlet duct. This design provides a direct correlation between pulse length and the motion of the actuator piston disk.
    However, the valve bodies that open / close the inlet duct and the outlet duct in this document have a relatively large mass and small passage areas. It is also possible that some applications require high working pressure / high pressure, for example 20-25 Bar, in order to obtain the correct function of the actuator, ie. be able to work together with an internal combustion engine with a speed range up to 8-10 thousand vary per minute. Furthermore, in such applications it is desired to avoid the temperature rising in the actuator and surrounding parts / fluids, as a result of the actual operation of the actuator and associated compressor, and this is achieved by keeping the pressure ratio set and thus using a so-called increased return pressure. / basic pressure. In other words, the pressure of the pressure fluid which is coated downstream of the actuator and upstream of the compressor is much higher in atmospheric pressure, for example 4-6 Bar. The relatively large mass has the valve bodies, so that the valve bodies cid the 3 must assume their respective resting positions risk bouncing against their sates whereby noises and vibrations arise and / or the input details are damaged, and entails inaccurate control of the pressure fluid in the inlet duct and outlet duct.
    The relatively small flow areas in combination with the high return pressure mean that when returning the actuator to the idle state, the evacuation of pressure fluid from the first part of the cylinder risks being insufficient, leading to slow return of the actuator piston disc. Brief description of the invention eliminate the above 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 eliminates the occurrence of noise from the actuator.
    A further object of the present invention is to provide an actuator which can have a high return pressure and at the same time have a lower ratio between working pressure and return pressure.
    It is another object of the present invention to provide an actuator which has larger passage areas having the actuator's first inlet valve, second inlet valve and outlet valve, respectively.
    It is another object of the present invention to provide an actuator, with a direct correlation between pulse length and the operation performed by the actuator piston disk.
    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 4 has the features defined in the independent claims. Hazardous embodiments of the present invention are further defined in the dependent claims.
    According to a first aspect of the present invention, there is provided an actuator of the initially defined type, which is characterized in that it comprises an electrically controlled pilot valve arranged to communicate a first control pressure to the first inlet valve body via a first control pressure channel and arranged to communicate second control pressure to the outlet valve body via a second control pressure duct. The pilot valve is arranged to assume a rest state, in which the first control pressure channel is in fluid communication with a control pressure inlet of the pilot valve and the second control pressure channel is in fluid communication with a control pressure outlet having the pilot valve and an active state in which the first control pressure communication is in with the control pressure outlet and the second control pressure duct being in fluid communication with the control pressure inlet, and that the inlet duct is kept closed by the second inlet valve body and the actuator piston disc are coated at at least a predetermined distance from the rest position thereof.
    Thus, the present invention is based on the insight that by having separate valve bodies open and close the inlet duct and the outlet duct, respectively, the weight of the usual valve body can be reduced, and that the high control pressure from the pilot valve is always used to alternately close the first inlet valve body.
    According to a preferred embodiment of the present invention, the actuator comprises a hydraulic circuit, which comprises a lead volume, a non-return valve and a hydraulic valve, the actuator piston rod being arranged to be displaced axially relative to said lead volume in connection with axial displacement of the actuator piston disc in cylinder volume. This means that the actuator piston disc can be held in its active position / lower torque for a predetermined or adapted time.
    Further advantages and features of the invention will be apparent from the other independent 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 view of the side of an actuator according to the invention according to a first embodiment, where the actuator is in its rest state, Fig. 2 is a schematic sectional view from the side corresponding to Fig. 1, where the actuator piston disc is in its lower rotation, Fig. 3 is a schematic section Fig. 4 is a schematic sectional side view corresponding to Fig. 3, in which the pilot valve has been activated but the actuator piston disc is still in its rest position, Figs. 4 is a side view of the actuator according to a second embodiment, where the actuator is in its idle state. 5 is a schematic sectional view from the side corresponding to Figure 3, where the actuator piston disc is in rotation see below and the pressure pulse is cut off by the second inlet valve body, Fig. 6 is a schematic sectional view from the side corresponding to Figure 3, where the actuator piston disc has stopped and is in its lower rotation, Fig. 7 is a schematic sectional view from the side corresponding to Fig. 3, where the pilot valve has been deactivated but the actuator piston disc is still in its lower water layer, Fig. 8 is a schematic sectional side view corresponding to Fig. 3, where the actuator piston disc is in upward movement and braking of the return movement is started, Fig. 9 is a a schematic sectional side view of an actuator according to the invention according to a third embodiment, where the actuator is in its rest state, Fig. 10 is a schematic sectional side view corresponding to Figure 9, in which the actuator piston plate moves downwards and the pressure pulse is cut off by the second inlet valve body, Fig. 11 is a schematic sectional side view of an actuator according to the invention according to a fourth embodiment, where the actuator is in its rest state, and Fig. 12 is a schematic sectional side view corresponding to Fig. 11, where the actuator piston disc has stopped and is in its lower vdndldge, and Fig. 13 is a schematic sectional side view corresponding to Figs. 11, where the actuator piston plate is in motion up and should just open the second inlet valve body.
    Detailed Description of the Preferred Embodiments References are initially made to Figures 1 and 2. The present invention relates to an actuator, generally designated 1, for axial displacement of an object, such as an actuator 1 for axial displacement of a gas shift valve 2 having an internal combustion engine. 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 2 in an internal combustion engine. In the embodiment shown, the actuator 1 comprises an actuator housing 3, a cylinder 4 defining a cylinder volume or chamber, an actuator piston disc 5 which is arranged in and which is axially displaceable in the said cylinder volume between an inactive rest position (figure 1) and an active position / lower vdndldge (Figure 2). The actuator piston disc 5 divides said cylinder volume into a first, upper part 6 and a second, lower part 7. The valve stem of the gas exchange valve 2 terminates in the second part 7 of the cylinder volume, and the gas exchange valve 2 is biased in the direction of a conventional valve spring or gas spring (not shown). ). The actuator piston disc 5 returns to its rest position by being a father bucket, preferably with the aid of a spring member, in the upward direction. The spring means may be a mechanical spring 15 or a gas spring, the bellows in the second part 7 of the cylinder volume. In the case that the actuator piston is connected to and drives an inlet or outlet valve to an internal combustion engine, the spring may be a valve spring which lifts gas exchange valve to its support valve. Alternative readings on how the bias is to be realized are conceivable, however, and within the scope of the present invention. Further, the actuator 1 comprises an actuator piston rod, generally designated 8, which is fixedly connected to and axially projecting from the actuator piston disk 5, which forms an actuator coil . The actuator piston rod 8 eliminates the risk of tilting of the actuator piston disc 5. In the embodiment shown, the actuator piston rod 8 has a first, coarser portion 9, which is bellows at a distance from the actuator piston disc 5 and which closes tdu at a second actuator, 10 which extends between and connects the coarser portion 9 and the actuator piston disc 5. In this embodiment, the coarser portion forms a second inlet valve body which will be described below.
    The actuator 1 also comprises a pressure fluid circuit, preferably pneumatic, arranged for controllable supply of a gas or gas mixture, for example air, to the first part 6 of the cylinder volume to create a displacement of the actuator piston disc 5, and arranged for controllable evacuation of the gas or gas mixture the first part 5 6 of the cylinder volume to create a return movement of the actuator piston disc 5.
    The pressure fluid circuit comprises an inlet duct 11, which extends between a pressure fluid inlet 12 in the actuator housing 3 and the first part 6 of the cylinder volume, and an outlet duct 13, which extends between the first part 6 and 10 of the cylinder volume, a pressure fluid outlet 14 in the actuator housing 3. The said inlet duct 11 12 connected to a pressure fluid source (HP), and said outlet channel 13 Or connected via the pressure fluid outlet 14 to a pressure fluid source (LP). In other words, the pressure fluid inlet 12 of the actuator 1 is arranged to be connected to the pressure fluid source (HP), and the pressure fluid outlet 14 is arranged to be connected to the pressure fluid sink (LP). The pressure fluid source can be a compressor connected to the engine with or without an associated tank, or only a pressure tank. The pressure fluid can be any point 20 with lower pressure On that generated in the pressure fluid column, for example a line leading back to the compressor. The pressure fluid circuit Or preferably a closed system with increased return pressure, ie. the pressure fluid anchor (LP) has, for example, 4-6 bars of pressure, and the pressure fluid source (HP) has, for example, 15-25 bars of pressure.
    The actuator 1 comprises a first inlet valve body 15 arranged in said inlet channel 11 for controlling the flow of pressure fluid in the inlet channel 11 past the position where the first inlet valve body 15 is coated, i.e. arranged to open and close the respective inlet duct 11. The first inlet valve body 15 is preferably a sate valve, and preferably the same is provided with a spring 16 in a direction of insertion of the inlet duct 11. The first inlet valve body 15 preferably comprises a guide pin 15 'to eliminate the risk of tilting thereof. Preferably, the first inlet valve body 15 has an axial 9 abutment against the surrounding actuator housing 3 in its two abutments, i.e. fully open and fully closed, to obtain good sealing without leakage.
    The actuator 1 comprises an outlet valve body 17 arranged in said outlet channel 13 for controlling the flow of pressure fluid in the outlet channel 13 past the position where the outlet valve body 17 is bellows, i.e. arranged to open and close the respective outlet channel 13. The outlet valve 17 is preferably a seat valve, and preferably the same is biased by a spring 18 in a direction of the outlet channel 13. The outlet valve body 17 preferably comprises a guide pin 17 'to eliminate the risk of tilting thereof. Dangerously, the outlet valve body 17 has an axial abutment against the surrounding actuator housing 3 in its two abutments, i.e. fully open and fully closed, to obtain good sealing without leakage.
    The actuator 1 also comprises a second inlet valve body, which in the embodiment shown consists of the coarser portion 9 of the actuator piston rod 8 and which is arranged in said inlet channel 11, i.e. arranged to open and close the respective inlet duct 11. The second inlet valve body is arranged to keep the inlet duct 11 closed when the actuator piston disc 5 is bellows at at least one predetermined distance from the rest position thereof.
    According to the embodiment shown, the first inlet valve body 15 and the second inlet valve body 9 are arranged in series with each other, and preferably the second inlet valve body 9 is arranged between the first inlet valve body 15 and the first part 6, 30 of the cylinder volume because the first inlet valve supply valve on the second inlet valve body 9.
    Central to the actuator 1 is that it comprises an electrically controlled pilot valve, generally designated 19, which is arranged to control the first inlet valve body 15 and the outlet valve body 17. By electrically controlled is meant controlled by an electromagnetic device, such as a solenoid 20, by means of a piezoelectric device. , etc. In all drawings the pilot valve 19 is drawn beldgen outside the actuator housing 3, which is fully tankable, however it is preferred that the pilot valve 19, the first control pressure channel 21 and the second control pressure channel 22, are all beldg completely or partially mom the actuator housing 3 .
    In the embodiment shown, the actuator 1 comprises a first control pressure duct 21 and a second control pressure duct 22, the first control pressure duct 21 extending between a first outlet 23 of the pilot valve 19 and a space having the actuator housing 3 partially defined by an upper side of the first inlet valve body 15. , and wherein the second control pressure passage 22 extends between a second outlet 24 has the pilot valve 19 and a space has the actuator piston housing 15 which is partially defined by an upper side has the outlet valve body 17. Thus, the pilot valve 19 is arranged to communicate a first control pressure to the first inlet valve body first control pressure duct 21 and arranged to communicate a second control pressure to the outlet valve body 17 via the second control pressure duct 22.
    The pilot valve 19 comprises a control fluid inlet 25, which is arranged to be connected to the pressure fluid valve (HP), and a control fluid outlet 26, which is arranged to be connected to the pressure fluid tank (LP). The pilot valve 19 is arranged to assume a rest state (inactivated solenoid) in which the first control pressure channel 21 is in fluid communication with the control fluid inlet 25 has the pilot valve 19 and the second control pressure channel 22 is in fluid communication with the control fluid outlet 26 has the pilot valve 19, respectively ), in which the first control pressure channel 21 is in fluid communication with the control fluid outlet 26 and the second control pressure channel 22 is in fluid communication with the control fluid inlet 25.
    The pilot valve 19 preferably comprises a pilot valve body 27, which is forwards and again displaceable between a rest position and an active position, the pilot valve body 27 being biased by a spring 28 in the direction of its rest position. In the embodiment shown, the pilot valve body 27 is constituted by a slide valve, however, other types of pilot valve bodies are conceivable. Thus, the solenoid 5 is arranged to displace the pilot valve body 27 in the direction of its active position when the said solenoid 20 is activated. It follows from the description above that the first control pressure acts on the upper side of the first inlet valve body 15 and the fluid pressure present in the inlet duct 11, i.e. Same as in the pressure fluid source (HP), acts on an outer part of the underside of the first inlet valve body 15. When the first control pressure is high, the first inlet valve body 15 closes the inlet channel 11, and when the first control pressure is applied, the first inlet valve body opens channel 11.
    Furthermore, the second control pressure acts on the upper side of the outlet valve body 17 and the fluid pressure present in the first part 6 of the cylinder volume acts on an inner part of the underside of the outlet valve body 17. When the second control pressure is high, the outlet valve body 17 closes to the outlet valve the pressurized area on the upper side is larger than the inner pressurized area on the underside, and when the second control pressure is applied, the outlet valve body 17 is arranged to open the outlet channel 13.
    Now, the operation of the actuator 1 according to the first embodiment, shown in Figures 1 and 2, will be described.
    Figure 1 shows the actuator 1 in its resting state, i.e. the pilot valve 19 is in the idle state and the solenoid 20 is deactivated. DA acts high fluid pressure in the first control pressure passage 21 and applied fluid pressure acts in the second control pressure passage 22. This means that the actuator piston disc 5 is in the rest position / 5th turning position, the first inlet valve body 15 is in the closed position, the second inlet valve position is in the up position due to the fact that the actuator 35 piston disc 5 is in the rest position, and the outlet valve body 12 17 is in the closed position due to the fact that it is a spring bias in the direction of the outlet channel 13.
    When a signal is given by, for example, a control unit that the actuator 1 is to carry out a displacement of the object / motor valve, the solenoid 20 is activated and the pilot valve 19 transitions to the active state. This means that applied fluid pressure acts in the first control pressure passage 21 and high fluid pressure acts in the second control pressure passage 22. The first inlet valve body 15 is opened by the pressure from the pressure fluid source (HP) acting at the pressure fluid inlet 12. Pressure fluid flows into the first part of the cylinder volume 6 11 and acts against the upper side of the actuator piston disc 5 and displaces the actuator piston in the downward direction. Outlet valve body 17 halls closed. When the actuator piston disc 5 has been displaced a distance determined at a pre-determined distance, the second inlet valve 9 cuts off the pressure fluid flow in the inlet channel 11, i.e. prevents further inflow of pressure fluid from the pressure fluid source (HP) to the first part 6 of the cylinder volume, the actuator piston disc 5 continuing its displacement and occupying its active position / lower water layer, as shown in Figure 2. The actuator piston disc 5 continues its displacement downwards after the second inlet valve 9 is cut off by the inlet to the first part 6 of the cylinder volume due to the gas in the first part 6 of the cylinder volume expanding and compressing the valve spring of the engine valve. Since it is known how the starting pressure is the pressure fluid source (HP), how strong the volume of the first part 6 of the cylinder volume is when the second inlet valve body 9 cuts the inlet, the force characteristic of the valve spring, etc. allows the length of the continued displacement of the actuator piston disk 5 to be controlled with sufficient precision.
    Then the solenoid 20 is deactivated, i.e. the pilot valve 19 assumes its dormant state. High fluid pressure operates again in the first control pressure duct 21 and added fluid pressure acts again in the second control pressure duct 22 to allow return movement of the actuator piston disc 5. The first inlet valve body 15 closes the inlet duct 11, the outlet valve valve body 17 is opened by the cylinder 6, and the actuator piston disc 5 is displaced upwards by, for example, the valve spring, whereupon the pressure fluid in the first part 6 of the cylinder volume is evacuated through the outlet channel 13. When the pressure in the first part 6 of the cylinder volume has decreased, the outlet valve body 17 is closed by the biasing spring 1. The actuator piston disc 5 returns to its rest position, with the aid of a biased spring member, in the upward direction. The spring means may be a mechanical spring or a gas spring, the bellows in the second part 7 of the cylinder volume. In the case that the actuator piston is connected to and drives an inlet or outlet valve to a combustion engine, the spring may be a valve spring which lifts the gas exchange valve to its rod. However, alternative solutions to how the bias voltage is to be realized are conceivable and within the scope of the present invention.
    Reference is now made to Figures 3-8, which show a second embodiment of the actuator according to the invention 1. Only differences in relation to the first embodiment will be described.
    In the embodiment shown, the actuator 1 also comprises a first hydraulic circuit, comprising a welding volume 29, the actuator piston rod 8 being arranged to be displaced in the axial direction relative to the said reading volume 29 in connection with axial displacement of the actuator piston disc 5 in the cylinder volume. Liquid (oil) is allowed to flatten into the liquid-filled welding volume 29 via a non-return valve 30 and out of the welding volume 29 via a hydraulic valve 32. The hydraulic valve 32 comprises a hydraulic valve body 33 which is reciprocable between a rest position and an active position, the hydraulic valve body 33 is biased by a spring 34 in the direction away from its resting position. Thus, the hydraulic valve body 33 is not dependent on the function of the spring 34 to assume the rest position. The pilot valve 19 is arranged to communicate said first control pressure to the hydraulic valve body 33, the hydraulic valve 32 being open when the pilot valve 19 is in its rest position, and the hydraulic valve 32 being closed when the pilot valve 19 is in its active state. In other words, when the actuator piston is shifted from the rest position (Figure 3) to the active position (Figure 6), the actuator piston rod 8 leaves room for tightening of liquid into the welding volume 29 and the hydraulic valve 32 is closed, and when the actuator piston is shifted from the active position to the rest position. the hydraulic valve 32 is first opened and the liquid is forced out of the volume 29.
    In an alternative embodiment of the hydraulic valve, the hydraulic body is biased by a spring in the direction of its rest position, and in this embodiment the pilot valve 19 is arranged to communicate said second control pressure to the hydraulic valve body, the hydraulic valve 32 being open when the pilot valve 19 is in its rest position. 32 is closed when the pilot valve 19 is in its active state.
    Furthermore, in the embodiment shown of the actuator 1 according to the invention according to Figures 3-8, the actuator piston rod 8 in the region of its free spirit has a hydraulic braking device, which is arranged to reduce the movement speed of the actuator piston before the actuator piston rod 8 stops, and thus the motor is reduced. 2 Movement speed before the motor valve 2 comes into contact with the same valve. The hydraulic brake device consists of a geometric displacement between the actuator piston rod 8 and the welding volume 29, which geometric displacement decreases as the free sand of the actuator piston rod 8 approaches its stop position, whereby the speed decreases.
    Now, the operation of the actuator 1 according to the second embodiment, shown in Figures 3-8, will be described.
    Figure 3 shows the actuator 1 in its resting state, i.e. the pilot valve 19 is in the idle state and the solenoid dr is deactivated. Then high fluid pressure acts in the first control pressure duct 21 and added fluid pressure acts in the second control pressure duct 22. The first inlet valve body 15 is in the closed position, the actuator piston disc 5 dr in the rest position / barrel water layer and the second inlet valve body 9 dr in the open valve position, in the closed position due to the fact that it pulls the spring bias in the outlet channel 13 in the closing direction, and the hydraulic valve 32 is open.
    In Figure 4, a signal has been given by a control unit that the actuator 1 is to perform a displacement of the object / motor valve. The solenoid 20 has been activated and the pilot valve 19 has been switched to the active state. This causes applied fluid pressure to act in the first control pressure passage 21 and high fluid pressure to act in the second control pressure passage 22. The first inlet valve body 15 is opened by the pressure from the pressure fluid source (HP) acting at the pressure fluid inlet 12. The hydraulic valve 32 is shut off.
    In Figure 5, pressure fluid has begun to flow into the first part 6 of the cylinder volume via the inlet duct 11 and acts against the upper side of the actuator piston disc 5 and displaces the actuator piston downwards. The fluid is sucked into the load volume 29 past the non-return valve 30. The outlet valve body 17 is held upright. When the actuator piston disc 5 is displaced a predetermined distance, the second inlet valve 9 cuts off the pressure fluid flow in the inlet channel 11, i.e. prevents continued inflow of pressure fluid from the pressure fluid source (HP) to the first part 6 of the cylinder volume, furthermore the actuator piston disk continues its displacement a distance.
    In Figure 6, the actuator piston disc 5 has assumed its active position / lower water layer. In this layer, the actuator piston disc 5 can be welded (retained) as a result of the liquid in the welding volume 29 not being allowed to evacuate.
    In Figure 7 here the solenoid 20 has been deactivated, i.e. the pilot valve 19 regains its dormant state. High fluid pressure acts in the first control pressure duct 21 and added fluid pressure acts in the second control pressure duct 22. The 16 first inlet valve body 15 closes the inlet duct 11, the hydraulic valve 32 is opened to allow evacuation of liquid from the volume 29, the outlet acts as an outlet valve the first part 6 of the cylinder volume, and the actuator piston disc 5 can be displaced upwards by the spring means.
    In Figure 8, the actuator piston plate 5 is displaced upwards, whereby the pressure fluid in the first part 6 of the cylinder volume is evacuated through the outlet duct 13. Further, braking of the movement of the actuator piston plate 5 upwards is started by the passage area on the sub-duct extending from the hydraulic valve. actuator piston. When the actuator piston plate 5 has assumed the rest position and the pressure in the first part 6 of the cylinder volume has decreased, the outlet valve body 17 is closed by the biasing spring 18.
    Whereby the actuator 1 is back in the idle state shown in Figure 3.
    Reference is now made to Figures 9 and 10, which show a third embodiment of the actuator 1 according to the invention.
    Only differences in relation to the first and the second embodiment will be described.
    In this embodiment, the actuator 1 comprises a second inlet valve body 9 'which is separate from the actuator piston rod 8. The second inlet valve body 9' extends in the axial direction and Or in contact with the part of the actuator piston disc 5 facing the first part 9 of the cylinder volume. 'Or preferably a wear valve. The second inlet valve body 9 'is father clamped in an inlet duct 11 in the vertical direction by means of a spring 35. In other words, the actuator piston plate 5 prevents the second inlet valve body 9 'from closing the inlet duct 11 until the actuator piston plate 5 is displaced by a predetermined distance from it.
    In an alternative embodiment, the second inlet valve body 9 'is fixedly connected to and axially displaceable together with the actuator piston disc 5, the spring 35 not moving.
    The second inlet valve body 9 'holds the inlet duct 11 closed so that the long actuator piston disc 5 is at least the predetermined distance from the rest position thereof.
    This third embodiment means that the diameter of the actuator piston rod 8 can be reduced, which means that the load volume 29 becomes smaller and thus a smaller amount of liquid / oil needs to pass past the non-return valve 30 and through the hydraulic valve 32 each displacement of the actuator piston disc 5.
    Reference is now made to Figures 11-13, which show a fourth embodiment of the actuator according to the invention. Only differences in relation to the other embodiments can be described.
    Like the third embodiment described above, the fourth embodiment comprises a second inlet valve body 9 "which differs from the actuator piston housing 8. In this embodiment, the second inlet valve body 9" is preferably a seat valve. When the actuator 1 is in its rest state (see figure 11), the second inlet valve body 9 "is via a lower spring 36 in contact with the side of the actuator piston disc 5 facing the first part 6 of the cylinder volume. The lower spring 36 is in its upper upper connections with the second inlet valve body 9 ". The lower spring 36 biases the second inlet valve body 9 "in an opening direction in the inlet channel 11, in which the actuator piston disc 5 is in its rest position. Furthermore, an additional spring 37 acts on the second inlet valve body 9", which upper spring 37 fjdder 36.
    In Figure 11, the actuator 1 is in its rest position, and the second valve body 9 "is tilted into an upper position. When the actuator 1 is activated, the actuator piston disc 5 begins its movement downwards and at the same time the lower spring 36 of the second inlet valve body 9 begins to expand in length and the second inlet valve body 9 "is retained in its Upper position. In connection with the actuator piston disc 5 being displaced downwards, the force with which the lower spring 36 acts against the second inlet valve body 9" decreases. After a certain displacement of the actuator piston disc 5, and simultaneous expansion of the lower spring 36, the force with which the upper spring 37 acts against the second inlet valve body 9 "exceeds the force of the lower spring 36, the second inlet valve body 9" being displaced downwards in an inlet duct 11 closing direction. When the actuator piston disc 5 is displaced a predetermined distance from its resting position, the second inlet valve body 9 "closes the inlet channel 11, and preferably the lower spring 36 ceases to be in contact with the actuator piston disc 5. In Figure 12, the actuator piston disc 5 in the water piston chamber 5.
    In Figure 13, the actuator piston plate 5 is on its way upwards and in the inlet channel 11 a high-pressure pressure fluid quantity is trapped between the first inlet valve body 15 and the second inlet valve body 9 ", which counteracts displacement above the second inlet valve body 9". In Figure 13, the lower spring 36 has been compressed and the upper side of the actuator piston disc 5 comes into contact with the second inlet valve body 9 "and then the second inlet valve body 9" is pushed up into the burr position by the spring force in the lower spring 36, and the actuator 1 ends up dter in its dormant state according to Figure 11.
    Conceivable 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 thank all the adaptations and variants of the preferred embodiments described, 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 under the appended claims.
    It should also be noted that all information about / moving terms such as above, below, byre, 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 only indicate that conditions are embedded in the embodiments shown, which conditions may be different if the equipment according to the invention is provided with a different construction / design.
    It should be noted that although it is not explicitly stated that features from a specific embodiment can be combined with features in another embodiment, this should be considered obvious as far as possible.
    权利要求:
    Claims (2)
    [1]
    1. 3 2324 22 4 / - 6
    [2]
    2. // 1 26 19 17/22 21) 13/13 23 22 214
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    同族专利:
    公开号 | 公开日
    EP3019753B1|2019-04-10|
    SE538239C2|2016-04-12|
    US9885261B2|2018-02-06|
    CN105378299B|2017-08-08|
    CN105378299A|2016-03-02|
    EP3019753A1|2016-05-18|
    WO2015005856A1|2015-01-15|
    US20160369666A1|2016-12-22|
    EP3019753A4|2017-04-12|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1350849A|SE538239C2|2013-07-08|2013-07-08|Actuator for axial displacement of an object|SE1350849A| SE538239C2|2013-07-08|2013-07-08|Actuator for axial displacement of an object|
    US14/903,878| US9885261B2|2013-07-08|2014-07-07|Actuator for axial displacement of an object|
    PCT/SE2014/050864| WO2015005856A1|2013-07-08|2014-07-07|Actuator for axial displacement of an object|
    CN201480039059.XA| CN105378299B|2013-07-08|2014-07-07|Actuator for the axial displacement of object|
    EP14822299.5A| EP3019753B1|2013-07-08|2014-07-07|Actuator for axial displacement of an object|
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