瑞典专利SE1150976A1 Actuator

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专利摘要:
An actuator, comprising a cylinder (1), an actuator piston (2) slidably arranged in the cylinder (1), a pressure fluid circuit with a channel (3) opening into said cylinder (1), a direct or indirect, electrically controlled first valve body ( 4), arranged in said channel (3) for controlling a flow of a pressure fluid in said channel (3), and a second valve body (5), arranged in or at said channel (3) for opening and closing the channel (3, respectively) ). The second valve body (5) is an element fixedly connected to the actuator piston (2), the first valve body (4) and the second valve body (5) being arranged in series with each other in said channel (3). Publication picture: Figure 1
公开号:SE1150976A1
申请号:SE1150976
申请日:2011-10-21
公开日:2013-04-22
发明作者:Anders Hoeglund；Mats Hedman
申请人:Cargine Engineering Ab；
IPC主号:

专利说明:

an inlet or outlet valve to an internal combustion engine. The two adjacent valve bodies are driven by means of an electromagnet each, the activation of which is controlled by a control unit connected to the internal combustion engine provided with software suitable for the purpose.
A pressure pulse is produced by opening the one of the two valve bodies which in the channel in which the valve bodies are located closest to a high pressure source while the second valve body is kept in its closed position, whereupon the first valve body is caused to close and the second valve body is caused to Open. Thereby, a pulse of pressure ﬂ uid corresponding to the amount of pressure ﬂ uid of high pressure which has been in the channel between said valve bodies will be transmitted further in the channel in the direction of actuator piston which is thereby set in motion. An overlap of the time during which the two valve bodies open for pressure ﬂ uid- ﬂ fate can also occur in order to increase the size of the generated pressure pulse.
However, such a construction has the disadvantage that the size of the pulse is determined in advance in the control unit and does not directly correlate to the displacement of the actuator piston that is sought. To ensure that the pulse does not become too small, the pulse must be dimensioned so that it is certainly sufficient for a given displacement of the actuator piston. Thus, an unnecessary amount of energy is required for a given displacement of the piston, since a safety margin is required.
US 5,193,495 discloses a valve control device comprising an actuator piston which is slidably arranged in a chamber. Furthermore, the valve control device shown comprises a first valve which is arranged in a first channel of a pressure circuit, which first channel opens into said chamber and the first valve is arranged to control a fate of a pressure circuit in this first channel. In addition, the valve control device shown comprises a second valve body which is arranged in a second channel of the pressure circuit, which second channel opens into said chamber and the second valve is arranged to open and close this second channel.
Thus, the first valve and the second valve body are not arranged in series in one and the same channel of the pressure circuit. Brief Description of the Object of the Invention The present invention aims to obviate the above-mentioned disadvantages and shortcomings of prior art pressure pulse generators and actuators and to provide an improved actuator.
It is also an object of the present invention to provide an actuator which comprises few electrical control devices, most preferably only one electrical control device.
Brief description of the features of the invention The object of the invention is solved with the aid of the initially actuated actuator, which has the features defined in the independent claims.
Preferred 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 the second valve body is an element fixedly connected to the actuator piston, the first valve body and the second valve body being arranged in series with each other in said channel. At least from an initial position, a pulse produced by opening the first valve body, while the second valve body is in an open position, will result in a displacement of the actuator piston and thus a displacement of the second valve body so that the latter cuts off the fate communication. in the duct and thereby closes the duct, whereby the pulse driving the actuator piston ceases. This gives a direct correlation between pulse length and the movement that the actuator piston performs.
Preferably, said element forming the second valve body is a pin projecting from one end of the piston and into said channel.
It is further preferred that the pin projects into the channel in a cylinder head arranged at one end of the cylinder.
Preferably, the second valve body is arranged to open for ﬂ uid- ﬂ fate in the channel in a first end position of the actuator piston. When the first valve body is opened in said end position, pressure ﬂ uid will act on the actuator piston which is displaced in the direction of a second end position. The second valve body is then arranged so that, as a result of the displacement of the actuator piston, it is displaced to a position in which it closes for continued flow from the high-pressure source in the direction of the actuator piston.
According to the invention, the second valve body is arranged to close for ﬂ uid ﬂ in the channel in position between the first end position and a second end position of the actuator piston. To effect a return of the actuator piston to the first position, the actuator therefore comprises an evacuation channel which opens into said cylinder and which also preferably is opened / closed by said first valve or houses an additional valve, suitably a direct or indirect, electrically controlled / driven valve. . When this evacuation channel is opened, while the actuator piston is in its second end position, pressure ﬂ uid is evacuated and the actuator piston returns to its first end position. To enable such a return, the piston is suitably biased, preferably by means of a spring means, in the direction of the first end position. The spring means may be a mechanical spring or a gas spring. In the case that the actuator piston is connected to and drives an inlet or outlet valve to an internal combustion engine, the spring can be constituted by a spring which lifts this valve to its closed position.
It is further preferred that the pin of the actuator piston comprises a tapered portion, which tapered portion in said first end position lies in the middle of the channel and opens for pressure ﬂ uid ﬂ desert through it. The duct preferably has a first branch, which is straight and in which the pin is arranged to be displaced, and a second branch transversely of this branch, in which the first valve body is arranged. The pin has a portion with a cross section corresponding to the cross section of the first branch, which portion closes the channel as long as it is located in the middle of the second branch or in the first branch between the second branch and the mouth into the cylinder, here defined as downstream of the second branch . The tapered portion of the pin is preferably located closer to the actuator piston than the coarser portion. In the first end position of the actuator piston, this has been pushed to a position in which the coarser portion no longer closes for id uid ﬂ fate through the first branch and the second branch into the cylinder.
According to a preferred embodiment of the invention, the actuator forms part of a valve actuator, which comprises a valve for the combustion chamber of an internal combustion engine 10, the actuator piston being operatively connected to and driving said valve.
According to a preferred embodiment of the invention, said channel leads to a high pressure source for said pressure ﬂ uid and the first position of the actuator piston is a position in which the piston is retracted and will slide towards the second end position when the channel is opened and the pressure ﬂ uid is allowed to communicate with and actuate the actuator piston. said cylinder.
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 a first, upper position, Fig. 2 is a schematic, sectional side view of the actuator piston showing the actuator shown in Fig. 1 in a second position, Fig. 3 is a counter to Fig. 1 Fig. 4 is a schematic, sectional side view of an actuator according to a second embodiment, and Fig. 4 is a schematic, sectional side view corresponding to Fig. 2 of the actuator shown in Fig. 3.
Detailed Description of Preferred Embodiments Figures 1 and 2 show a first, preferred embodiment of the present invention. Figures 1 and 2 thus show an actuator. The actuator forms, in the preferred embodiment shown, part of a valve actuator for an internal combustion engine. The actuator comprises a cylinder 1, an actuator piston 2 displaceably arranged in the cylinder 1, a pressure circuit with a channel 3 which opens into said cylinder 1, a direct or indirect, electrically controlled first valve body 4, which first valve body 4 is arranged in said channel 3 for controlling a fate of a pressure id outside the channel 3, and a second valve body 5, which is arranged in or at the channel 3 for opening and closing the channel, respectively. The second valve body 5 is formed by a pin projecting from one end of the actuator piston 2 and into the channel 3. The first valve body 4 and the second valve body 5 are arranged in series in said channel 3, and the mutual order of the first the valve body 4 and the second valve body 5 are of minor importance, however, from a manufacturing perspective it is preferred that the second valve body 5 is located between the cylinder 1 and the first valve body 4. By electrically controlled is meant controlled by means of an electromagnetic device, by means of a piezoelectric device, etc. Said first valve body 4 can also be called first slave valve.
The channel 3 can be said to be divided into a first branch 3 ', which extends in the longitudinal direction of the piston and in which the pin 5 is slidably arranged, and a second branch 3 ", which extends across said first branch 3' and opens from the side into the first branch 3 ". The pin 5 has a first, coarser portion 5 ', which is located remote from the actuator piston 2 and tapered portion 5" which is located closer to the actuator piston 2 than the coarser portion and which is connected to the coarser portion 5' and the actuator piston. 2. The first, coarser portion 5 'has a cross-section corresponding to the cross-section of the first branch 3' of the channel 3, and which consequently seals against the passage of pressure ﬂ uid where it is located in the channel 3. The tapered portion extends a distance equal to or longer than the distance from the intersection between the branches 3 ', 3 ”of the channel 3 and the mouth of the channel 3 out into the cylinder 1.
Thus, when the tapered portion 5 "of the piston 5" abuts at the mouth of the second branch 3 "in the first branch 3 ', it allows pressure ﬂ uid to pass through the channel 3 into the cylinder 1. This position corresponds to the first, upper end position of the actuator piston 2.
In a preferred embodiment, the actuator further comprises a three-way valve. In the embodiment shown in Figures 1 and 2, said three-way valve consists of a so-called pilot valve 18 which is arranged to be driven by an electromagnet 6. The three-way valve can also consist of a piezoelectric valve or the like electrically controlled valve. The pilot valve 18 is arranged to alternately open for pressure ﬂ uid ﬂ desolation from a high pressure source (HP) and pressure ﬂ uid ﬂ desolation from a low pressure source (LP), the selected pressure ﬂ uid ﬂ desolation being allowed to flow into an actuation channel 19. Furthermore, the upper valve body 19 act against and displace the first valve body 4 downwards. The pilot valve 18 is preferably biased in an upward direction by means of a gas spring, mechanical spring or the like, whereupon an activation of the solenoid 6 causes the pilot valve 18 to be displaced in a first direction (downwards) and when the solenoid 6 is switched off the pilot valve 18 returns by displacing in a second direction (upwards). The figures thus show that the first valve body 4 is indirectly electrically controlled. In the case where the electromagnet 6 acts directly on the first valve body 4, the first valve body 4 is directly electrically controlled, i.e. in this embodiment the pilot valve and the activation channel are missing.
When the pilot valve 18 opens for pressure fluid discharge from a high pressure source HP to the actuation channel 19, the first valve body 4 is moved to a lower position, shown in Figure 1. Thus, the first valve body 4 is caused to open pressure pressure outlet in the channel 3 from a high pressure source HP with which the channel 3 are connected. A pulse of pressure ﬂ uid will then act against and displace the actuator piston 2 in the cylinder 1 from the position shown in Figure 1 to and past the position shown in Figure 2, and a further distance to a lower end position (not shown), the further due of the kinetic energy of the actuator piston 2 and the prevailing overpressure which still prevails in the cylinder 1. Figure 1 thus shows an instantaneous picture when the first valve body has been displaced but the actuator piston 2 has not yet started to move. The two positions correspond to the upper end position of the piston 2, as well as a position when the pin 5 has just cut the i in the channel 3. The actual lower end position of the actuator piston 2 is not shown in the figures. On its way to the second end position (ﬁ gur 2), the coarser portion 5 'of the pin 5 will position itself opposite the mouth of the second branch 8' in the first branch 3 'and thereby close the channel 8 for continued pressure tryck uid id desolation.
The actuator piston 2 is biased towards the first, upper position by means of a spring 17. In the preferred embodiment, the actuator piston is connected to and drives an inlet or outlet valve 15 to the combustion chamber of an internal combustion engine. The bias is then suitably realized by a spring which biases said inlet or outlet valve to its closed position. Alternative solutions on how the bias voltage is to be realized are, however, conceivable and within the scope of the present invention.
To enable a return movement of the actuator piston 2, the actuator comprises an evacuation channel 7, which leads to a low pressure source (LP).
Both the first-mentioned high-pressure source HP conducting channel 3 and the evacuation channel 7 are arranged in the cylinder head 8 of the cylinder 1. In the exemplary embodiment shown in Figures 1 and 2, the first valve body 4 is also arranged in said evacuation channel 7 for controlling a fate of a pressure ﬂ uid in the evacuation channel 7. The movement of the first valve body 4 thus also controls when the evacuation channel 7 is to be opened and evacuation of pressure ﬂ uid from the cylinder 1 is to take place. Figure 2 shows that the pilot valve 18 has been displaced to open communication between a low pressure source (LP) and the actuation channel 19, and thus the first valve body 4 which is biased in the upward direction by means of a gas spring, a mechanical spring, or the like, has been displaced thereto. upper position. While the first valve body 4 has been displaced, the channel 3 has been closed and then the evacuation channel 7 has been opened to allow evacuation of pressure from the cylinder 1. Alternatively, there may be a small overlap between closing the channel 3 and opening the evacuation channel 7, to shorten the stroke of the first valve body 4. When evacuation takes place, the actuator piston 2 returns, thanks to its bias voltage, from its lower end position, via the position shown in figure 2 to the first, upper end position shown in figure 1. In the case that a gas spring is arranged below the first valve body 4, the area of the upper end of the first valve body 4 located in the actuating channel 19 must be larger than the lower end, in order to allow biasing in the upward direction. Preferably, the upper area should be fifty percent larger than the lower area. Evacuation can be further improved / accelerated by allowing an additional duct (not shown) connected to a low pressure source to be connected to the duct 3 at a position located between the first sub-duct 3 'and the first valve body 4.
This duct (not shown) must be opened at the same time as the evacuation duct 7 by means of the first valve body 4.
The actuator further comprises a hydraulic lock 1 1, consisting of an extension of the first branch 3 ”of the channel 3. This extension forms a channel 12 in which a non-return valve 13 is arranged. The channel 12 forms part of a hydraulic circuit. The non-return valve 13 is arranged to allow liquid to pass in the direction of the part of the channel which constitutes the extension of the channel into which the pin 5 projects, and to prevent ﬂ fate in the opposite direction. In addition, there is a hydraulic valve in the channel 12, which is arranged to open for evacuation of liquid from said extension of the branch 3 'in connection with evacuation of the pressure outside the cylinder 1 when the actuator piston 2 is to make a return movement to the upper end position. In the embodiment shown, the hydraulic valve is connected to the first valve body 4 and thus follows its movement, in such a way that it closes the hydraulic channel 12 when the first valve body 4 closes the evacuation channel 7, and opens the hydraulic channel 12 when the first valve body 4 opens the evacuation channel 7. thus, thanks to the hydraulic lock, the actuator piston 2 is prevented from undesirably swinging back from the second end position, shown in Figure 2, until the time in a cycle when the evacuation channel 7 is opened for evacuation and return of the actuator piston 2. It shall It is pointed out that the hydraulic valve opens just before evacuation via the evacuation channel 7 takes place.
According to a preferred embodiment, the actuator is controlled, by control from a control unit provided with software suitable for the purpose, to deliver pressure pulses used for recurring opening and closing of an inlet or outlet valve 15 to a combustion engine combustion chamber 16. The actuator's actuator piston 2 is previously mentioned, preferably operatively connected to said inlet or outlet valve and directly transmits its movement thereto. A firing pulse which pushes the actuator piston 2 from the first upper end position shown in Figure 1 is effected by activating and thereby opening the channel 3 by means of the first valve body 4 while the evacuation channel 7 is kept closed by the first valve body 4. Pressure in the channel 3 will then to generate a pressure in the cylinder 1 which displaces the piston 2 towards said second position. When the first, coarser portion 5 'of the pin 5 is displaced so far as to cover the second branch 3 "of the channel 3, it closes the channel 3 and thereby cuts off the pulse. The piston 2 continues to move due to its kinetic energy and the overpressure which still prevails in the cylinder, and then reaches the second end position when the spring has absorbed that energy.Now the motor valve driven by the actuator is open, and the software in the control unit determines how long it should be so with regard to additional operating parameters of the actuator. Meanwhile, from the time when the pin 5 is closed for failure in the channel 3, the first valve body 4 is controlled to close the channel 3. When the motor valve is to be closed again, the electromagnet 6 and the first valve body 4 are first closed the channel 3 and then opens the evacuation channel 7, whereby the actuator piston 2 biased by means of a spring 17 returns to the position shown in figure 1.
Figures 1 and 2 also show a position sensor 20, which is preferably of the contact type. A spring-loaded ball of electrically conductive material is mounted in an electrically insulated sleeve in the cylinder head 8. The ball protrudes into the first branch 3 ”of the channel 3”. In the initial position, the ball is not grounded. When the actuator is activated and the coarser portion 5 'of the pin 5 passes the ball, electrical contact with earth occurs. Since the ball is connected to a current source via a resistor, a signal can be taken out at a signal output 21 which indicates that the pin 5 and thus the actuator piston 2 has passed a certain position. This signal can then be used as an on / off sensor for indicating the position of the actuator piston 2. The pin 5 can also be provided with additional grooves which provide electrical contact or interruption in the event of further movement of the pin 5. Thereby, multiple positions on the actuator piston 2 can be identified. This can be used for calibration of valve lifts and for other purposes depending on the application.
Figures 3 and 4 show a second embodiment of the present invention. Equal parts have the same reference numerals and only that which differs from the first embodiment will be described.
Unlike the first embodiment shown in Figures 1 and 2, the second embodiment has shown in Figures 3 and 4 also a third valve body 9 which is arranged in said evacuation channel 7 for controlling a de fate of a pressure ﬂ uid in the evacuation channel 7. By controlling the the second valve body 9 is determined when the evacuation channel 7 is to be opened and evacuation of pressure from the cylinder 1 is to take place. The upper end of the second valve body 9 arranged in the actuating channel 19, whereupon said pressure ﬂ uid ﬂ destiny can act against and displace the second valve body 9 in a similar manner as the first valve body 4. When the second valve body 9 and the first valve body 4 both ends in the same actuating channel 19 displacement of the second valve body 9 and the first valve body 4 to take place in parallel. In the second embodiment shown, the hydraulic valve is connected to the second valve body 9 and thus follows its movement, in such a way that it closes the hydraulic channel 12 when the second valve body 9 closes the evacuation channel 7, and opens the hydraulic channel 12 when the second valve body 9 opens the evacuation channel 7.
The pilot valve 18 and the solenoid 6 are an example of a three-way valve that can be designed in a number of ways with pressure-relieved or non-pressure-relieving technology. In the current construction, it is not pressure-relieved and the high pressure is used to return the pilot valve 18, such as a gas spring. Without pressure relief, the closing speed increases with the pressure, which counteracts the effect of the driving pressure on the duration of the valve time when the actuator is used as a valve actuator. The duration of the valve actuator thus becomes less sensitive to variations in the drive pressure. In the preferred embodiment shown, the pilot valve 18 has two valve cones which are spherical or conical, in order to obtain improved centering and sealing.
Spherical are also insensitive to angular errors. In order to reduce the force for opening the pilot valve, it is advantageous if the cone angle ß, alternatively the abutment angle of the sphere in the seat is designed so that sealing takes place as close to the center of the hole as possible. It is advantageous if the cone angle, or alternatively the abutment angle of the sphere in the seat, is designed so that the opening area is maximized under the secondary condition that sufficiently good self-centering is achieved at the same time. Preferably with a cone angle ß on the valve cone in the range 80-130 degrees, preferably 106 degrees. Preferably, both the valve cone and the seat are of metal where the valve cone should be harder than the valve seat. The seat is preferably made of such a soft material and designed so that it is initially shaped and adapts to the valve cone so that good tightness is achieved.
Another advantage of a so-called seat valve, in contrast to a slide valve shown in the other figures, is that tightness can be achieved in the end positions and that a relatively large area can be achieved for a given hole diameter and stroke. To further reduce leakage and to dampen bounces, it is possible to coat valve seats with an elastomer such as, for example, vulcanized rubber.
In the inactivated position, the high pressure closes the pilot valve 18 so that the control pressure becomes low. When activated, the high-pressure line is opened and the low-pressure line is closed so that the control pressure becomes high. Return spring is therefore not necessary. 10 15 20 12 However, with an extra return spring, the return can be accelerated, which can be advantageous at low drive pressures.
Possible 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 cover all modifications and variations of the preferred embodiments described herein, and accordingly, 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 be noted that all information about / concerning terms such as above, below, upper, lower, etc., should 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 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.
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 (8)
[1]
Actuator, comprising - a cylinder (1), - an actuator piston (2) slidably arranged in the cylinder (1), - a pressure circuit with a channel (3) opening into said cylinder (1), - a direct or indirect, electrically controlled first valve body (4), arranged in said channel (3) for controlling a ﬂ fate of a pressure ﬂ uid in said channel (3), and - a second valve body (5), arranged in or at said channel (3) for opening respective closing of the duct (3), characterized in that the second valve body (5) is an element fixedly connected to the actuator piston (2), the first valve body (4) and the second valve body (5) being arranged in series with each other in said channel (3).
[2]
Actuator according to claim 1, characterized in that the second valve body (5) is a pin projecting from one end of the piston (2) and into said channel (3).
[3]
Actuator according to claim 2, characterized in that the second valve body (5) projects into the channel (3) in a cylinder head (8) arranged at one end of the cylinder (1).
[4]
Actuator according to one of Claims 1 to 3, characterized in that the second valve body (5) is arranged to open for discharge in the channel (3) in a first end position of the actuator piston (2).
[5]
Actuator according to any one of claims 1-5, characterized in that the second valve body (5) is arranged to close for de uid ﬂ fate in the channel (3) in position between the first end position and a second end position of the actuator piston (2).
[6]
Actuator according to claim 2, characterized in that said pin (5) comprises a tapered portion, which tapered portion lies in the middle of the channel (3) and opens for pressure ﬂ uid ﬂ desert through it in said first end position.
[7]
Actuator according to one of Claims 1 to 6, characterized in that it forms part of a valve actuator which comprises a valve (15) for the combustion chamber (16) of an internal combustion engine, and that the actuator piston (2) is operatively connected to and drives said valve (15).
[8]
Actuator according to any one of claims 1-7, characterized in that said channel (3) leads to a high pressure source (HP) for said pressure ﬂ uid and that the first position of the actuator piston (2) is a position in which the piston (2) is retracted and will be pushed to the second position while the channel (3) is caused to open and the pressure ﬂ uiden is allowed to communicate with and act on the actuator piston (2) in said cylinder (1).

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同族专利:

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引用文献:

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法律状态:

优先权:

申请号 | 申请日 | 专利标题

SE1150976A|SE544218C2|2011-10-21|2011-10-21|Pressure fluid controlled actuator|SE1150976A| SE544218C2|2011-10-21|2011-10-21|Pressure fluid controlled actuator|

US14/353,052| US9347466B2|2011-10-21|2012-10-19|Actuator|

PCT/SE2012/051121| WO2013058704A1|2011-10-21|2012-10-19|Actuator|

CN201280051639.1A| CN104081011B|2011-10-21|2012-10-19|Actuator|

EP12841388.7A| EP2769059B1|2011-10-21|2012-10-19|Actuator|

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