• 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:
    SUMMARY: Distribution valve (7) for directing the hydraulic flow to different consumers, the distribution valve comprising a front and rear valve slide (8). The valve slide (8) comprises a central, axially extending bore (38, 39), which cooperates with a plunger (35) abutting against a valve end (11) for driving the valve slide (8) under pressurized condition. The plunger comprises an outer piston portion (36) of reduced diameter (d), which, in a bearing area of the valve slide, is arranged to establish, together with a cooperating portion (38) of the bore of reduced diameter (d), a steam chamber (40). For vapor deposition of the valve slide (8). The invention also relates to a rock drilling machine. Fig. 2
    公开号:SE1450300A1
    申请号:SE1450300
    申请日:2014-03-18
    公开日:2015-09-19
    发明作者:Ulf Nilsson；Thomas Johansson
    申请人:Atlas Copco Rock Drills Ab；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION The invention relates to a distribution valve for controlling the hydraulic flow to different consumers, the distribution valve comprising a valve slide arranged in a valve chamber in axial directions and the valve stem in the axial direction. and a second valve end. The invention also relates to a hydraulic rock drilling machine including such a device.
    BACKGROUND ART Distribution valves for periodic supply of pressure fluid to various types of consumers or their evacuation are known for use in a wide range of technical applications.
    When it comes to hydraulic hitting rock drills, it is a good idea to set up a distribution valve, which is controlled by means of a connection to the percussion drill.
    The purpose of the distribution valve is to provide intermittent pressurization of the drive chamber of the percussion piston by obtaining the desired effect. For this purpose, the reciprocating valve slide is controlled by means of pilot pressure to impart drive pressure to the rock chamber of the rock drill.
    Previous distribution valves for striking rock drills as well as for other applications, selection works at the frequencies and pressures that are relevant for today's machines. At Unskemal with higher operating frequencies, however, there is a risk of increased costs for the valve and thus the machine as a whole, as more sophisticated constructions of distribution valves with higher half-strength requirements may need to be used. Even with existing machines, such as the rock drilling rig area 77747 20140123 2 and other technical areas, there are requests for valves further developed for more reliable operation.
    OBJECTS AND MOST IMPORTANT CHARACTERISTICS OF THE INVENTION It is an object of the present invention to provide a further development of distribution valves as above and to provide an economically manufacturable distribution valve which is capable of being used in demanding operation.
    This object is achieved in a device according to the above in that the valve slide comprises a central bore extending in the axial direction, which cooperates with a plunge connecting to the second valve end to form a pressurizable space, and that the plunger comprises an outer piston portion directed from the second valve end. with reduced diameter, which, in a bearing area for the valve slide, is arranged to, together with a portion of the bore with the corresponding reduced diameter, cooperate to establish a steam chamber for bearing damping of the valve slide.
    In this way it is achieved that the axial movement speed of the valve slide can be steamed efficiently and safely in a breathing area of its movement area. This has several advantages over the background technology, such as: - The impact force against a valve end will be lower.
    The surveys of associated components are therefore stored.
    The ventricular damping is preferably arranged for movements in the directions of the most probable parts of the distribution valve, which may risk being damaged by impact at full speed by a valve slide.
    - The valve slide can be assumed to have a higher speed than otherwise during the main part of its movement between the breaths.
    A higher conversion speed is thus permitted, which means that it is possible for the frequency to be increased by a machine such as a rock drilling machine, in which the invention is applied.
    Because the steam chamber will operate with a constant pressurized medium, the risk of cavitation on recovery will be minimized.
    - Because the steam chamber will work with a constant pressurized medium, a predictable and repeatable accurately calculable steaming will be present at the preferably small volume of the steam chamber.
    The small volume of the steam chamber in turn makes it possible to keep the steam chamber axially short, so that the valve slide can have a preferred high speed over the majority of its movement.
    The valve according to the invention is easily and economically manufacturable. The finishing of the valve slide can be carried out in a processing set-up, which results in faster and safer production with more accurate obtaining of desired tolerances.
    The saval portions of the bore as the portions of the plunger are circular-cylindrical.
    In the case of an established steam chamber, there is preferably a steam gap between the outer piston portion and the cooperating portion of the bore. In the steam gap, kinetic energy is converted in flowing hydraulic medium to heat energy in the hydraulic medium, which results in aspirated energy absorption. The person skilled in the art can, within the framework of his normal operation, dimension the steam gap by adapting to current parameters such as speed and the hydraulic medium used to ensure that the desired steam distance and steam characteristics are obtained.
    Lamply, the valve in or in the area of the first valve end comprises a pressurizable chamber, which receives a valve slide belonging to a central duck piston portion with a face surface which in a pressurized state of the chamber drives the valve slide in the direction of the second valve end. In particular, in the pressurized state of the space and the pressurized state of the chamber, it is provided to drive the valve slide in the direction of the second valve end.
    It is preferred that the plunger be arranged to be free from the other valve end. The plunger will then be pressed into abutment against the second valve end by the pressure in said bore in the valve slide and is allowed to be free from the lateral force action of the second valve end and instead be completely controlled by the bore. This entails a minimized risk of cutting because the plunger is preferably guided in a radial direction towards the valve slide, which in turn is controlled by a valve liner / valve housing, without any radial forces entering between the plunger and the valve slide. This also allows manufacturing with reduced tolerance requirements as well as the required narrow choke gap / steam gap can be arranged between the valve slide and the plunger without cutting tendencies arising. The plunger is then particularly variable in a radial joint in relation to the second valve end when it is pressed against it.
    The plunger can, however, be connected to the second valve end, with the consent of relative movement in a radial joint in relation to the second valve end. Due to the inwardness of this board, it is permitted that the plunger can in some extent follow the curves of the valve slide in the radial direction, which at least reduces the risk of cutting. It is conceivable, but in most cases not appropriate, that the plunger and the other valve end are firmly connected to each other. This is not preferred as there is a risk of cutting tendencies during this loading.
    At least one slide for the bore is suitably arranged in a cradle of the valve slide to allow permanent pressurization of the space, and to allow permanent pressurization directly from one of the ports of the distribution valve. The permanent pressurization is preferably provided by a system pressure switch connected to the distribution valve. 77747 20140123 The person skilled in the art advantageously dimensions a sloping cross-sectional area / initial steam chamber volume (in the case of a steam chamber just established) as required and area of application for obtaining the desired speed reduction at the same time as the desired length of the steam section.
    The invention also relates to a hydraulic rock drilling machine with a machine housing, which accommodates a working cylinder with a reciprocating percussion piston, the rock drilling machine comprising a valve as above.
    The said valve is suitably accommodated in the machine housing, which meant integration advantages, which have to do with manufacturing and spatial aspects. The distribution valve has a shaft, which is preferably parallel to a shaft of the working cylinder, which makes it possible to build the rock drilling machine slim and space-saving.
    It is also preferred that the rock drilling machine has a machine end for the working cylinder, which machine end also closes a space for receiving the distribution valve. This results in a single dividing plane that can be used for both the working cylinder and the distribution valve, which provides further reduced costs and substantial benefits. Further features and advantages of the invention will become apparent from the following description of exemplary embodiments.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described in more detail with reference to exemplary embodiments and with reference to the accompanying drawings, in which: Fig. 1 shows a rock drilling machine equipped with a distribution valve according to the invention in an axial section, Fig. 2 shows an enlarged section of a distribution valve according to the invention in a first layer, Figs. 3a and 3b show an enlarged section and a partial enlargement of the distribution valve in Fig. 2 in a second layer, respectively, and Fig. 4 shows an enlarged section of the distribution valve in Fig. 2 in a third ldge.
    DESCRIPTION OF EXEMPLARY EMBODIMENTS Fig. 1 thus shows in an axial section a rock drilling machine 1 including a machine housing 2, in which a percussion piston 3 is axially forward and reciprocal inside a cylinder space projecting a working cylinder 4. The percussion piston 3 extends against a stroke in a drill neck 5 IDA in and f8r forward kdrit sdtt.
    At the rear end area of the rock drilling machine 1, a distribution valve 7 is arranged for distributing pressure fluid to the drive chambers of the rock drilling machine for driving the percussion piston 3 back and forth.
    In Fig. 1, the distribution valve 7 is shown with its valve axis parallel to the axis of the percussion piston 3 and the working cylinder 4, which is the axis of the percussion device with the rock drilling machine 1.
    This has the advantage that the rock drill can be made slim and space-saving IDA its rear part.
    It also allows a rear housing end to be arranged to be common to the working cylinder and the distribution valve so that an otherwise necessary dividing plane can be saved.
    Through the design with parallel shafts and a common rear end, the advantage is achieved with lower machining costs and thus a lower cost for the drilling machine. In addition, the risk of moisture and contaminants entering the machine is reduced, as well as the risk of the oceans entering through unintentionally loosening screws.
    Fig. 2 shows the distribution valve 7 on an enlarged scale, it being shown that the distribution valve 7 has a valve slide 8 in front and in a valve liner 9, which is movable between two ends defined by abutments against a first valve end 10 and against a second one, respectively. valve end 11. The valve liner 9 defines a valve chamber 33 for receiving the valve slide 8 and has conventional bores, which provide channel openings for channels connected to the distribution valve 7. The valve liner 9 is provided with precisely defined guide edges for cooperation with the corresponding guide projections on the valve slide 8.
    In the layer shown in Fig. 2, the valve slide 8 of the distribution valve 7 is in a first abutment with a first abutment end 21 in abutment with a first end stop 17 on the first valve end 10 for the valve slide 8. The valve slide 8 is in this layer with a second stop 22 at a distance from a second breath stop 34 on the second valve end 11.
    The layer of the valve slide in Fig. 2 arises due to the fact that a chamber 14, which receives a valve slide 8 belonging to the central duck piston portion 23 with a breath surface 15, is in a pressure-loaded condition.
    Furthermore, a space 16 is provided inside the valve slide 8, which space 16 during operation is permanently pressurized by forming a hole 27 in the cradle of the valve slide from an equally permanently pressurized valve port.
    The pressure in this space 16 acts against the end face 24 of the space 16 and forms in the pressureless state of the chamber 14 to drive the valve slide 8 to the left in the figure towards its first face.
    The permanently pressurized space 16 is defined by a bore coaxial with the valve slide axis.
    The axially second spirit of the space 16, opposite the end face 24, is delimited by a plunging 35 extending into the bore, which is pressed against the second valve end 11 by the pressure present in the space 16. 77747 20140123 8 There is further between the bore and the plunger through a narrow gap sealing cooperation while allowing the valve slide to be axially movable in relation to the second valve end and to the plunger.
    The layer shown in Fig. 3a has arisen in that an intermittent pressurized channel (not shown) leading from a valve portion of the working cylinder 4 (Fig. 1) to the chamber 14 due to the bearing of the percussion piston 3 during its stroke cycle is pressurized with system pressure. It should be noted that also others stated that intermittently pressurized chamber 14 may occur.
    Thereby the chamber 14 is pressurized so that a hydraulic pressure acts on the end face 15 of the central duck piston portion 23 of the valve slide 8. Because the area of the end face 15 is larger than the area of the end face 24 and typically the same pressure lines in the chamber 14 and in the space 16 will the valve slide to start is driven in the direction of its second abutment and after a certain period of time is in the layer shown in Fig. 3a.
    With the valve slide in the layer shown in Fig. 3a, an outer piston portion 36 of the plunger 35, which outer piston portion 36 has a smaller diameter d compared to a larger diameter D of a main part 37 of the plunger, just at night a portion 38 of the bore with substantially the smaller diameter d (deviates slightly due to the presence of a gap between the elements). The main part 37 of the plunger is moreover always in a portion 39 of the bore with (mainly) the larger diameter D (deviates somewhat due to the fact that a gap is present between the elements).
    In this layer of the valve slide, a steam chamber 40 is arranged to be established by co-operation between the outer piston portion 36 and the portion 38 of the bore with the smaller diameter d.
    The steam chamber, as can be seen from the detail enlargement in Fig. 3b, is substantially limited by: a radially outwardly directed surface of the outer piston portion 36, 43, an axially directed end face of the main part of the plunger, which is coated radially outside the outer piston portion 36, 44, an axially directed end face of the portion of the larger diameter bore coated radially outside the portion of the smaller diameter bore, 45, a radially inwardly directed surface of the portion of the larger diameter bore. As the valve slide continues to move in the direction of the second valve end 11, from the layer in Fig. 3a, when the steam chamber 40 has been established until the valve slide has its second abutment at night, the volume of the steam chamber will decrease. As a result, the hydraulic medium present in the steam chamber 40 will, in consequence of the volume reduction, protrude through a steam gap 41 formed between the radially outwardly directed outer surface of the outer piston portion 36 and an inner surface of the smaller diameter portion 38 of the bore.
    The hydraulic medium will thereby protrude through the steam gap 41 against the pressure in the permanently pressurized space 16 inside the valve slide 8. The steaming is taken care of by converting the kinetic energy in the valve slide into heat absorbed by the hydraulic medium as it passes through the steam gap.
    The hydraulic medium present in the steam chamber will mainly be forced out through the steam gap 41, but also to a lesser extent as leakage through the gap formed between the main part 37 of the plunger and the portion 39 of the larger diameter bore.
    In the second end of the valve slide 8 shown in Fig. 4, the valve slide 8 is in abutment with the second stop end 22 against the second stop stop 34 on the second valve end 11.
    Starting from this, the pressurization of the chamber 14 is now interrupted, which in the stable is connected to a return duct / to the atmosphere / to a lower pressure, whereby the valve slide Ater 77747 20140123 10 is driven towards the layer shown in Fig. 2, after which the above-described weirdness pattern is repeated.
    The invention can be modified within the scope of the claims. As an alternative or as a complement to the arrangement with the steam gap 41, it is possible but not preferred that a channel 46 (indicated by a dashed line in Fig. 4) be connected to the steam chamber, in which a steam throttle 47 is arranged, which can be fixed or adjustable. . This provides opportunities for control and entails less need for dimensioning of the steam gap.
    In order to reduce tendencies to cavitation, it is possible but not preferable to connect to the steam chamber a pressure cold P for delivery of hydraulic medium with the same pressure as rows in the space 16. In a channel 48 (indicated by a dashed line in Fig. 4) from this pressure cold is aptly inserted one in the direction of the steam chamber Open one-way valve.
    Both the first and the second valve ends 10, 11 may be so that both valve ends are pressurized against abutments in the direction of each other to define two defined surfaces of the valve slide 8. However, it is within the scope of the invention that the valve ends are fixed to the valve housing. put through, for example, screwing, bolting, being inserted and fixed transversely, etc.
    The distribution valve 7 can also be designed without a specific valve liner 9.
    The invention is, as stated above, also applicable to more conventionally constructed distribution valves with fixed valve ends. One or both of the valve ends can furthermore also be integrated in a housing for the distribution valve, whereby by "valve end" is meant the duct wall for a valve chamber.
    The term "depressurized state" for the chamber 14 means that the chamber is disconnected from high pressure / system pressure and instead connected to legal pressure or atmospheric pressure. 77747 20140123 11
    权利要求:
    Claims (13)
    [1]
    A PATENT REQUIREMENT: 1. Distribution valve (7) for guiding the hydraulic surface to different users, wherein the distribution valve comprises a valve slide (8) arranged in an axial direction (33) in axial directions and wherein the valve chamber in axial direction is defined by a first and a second valve end (10, 11), characterized in that the valve slide (8) comprises a central, axially extending bore (38, 39), which cooperates with a plunger (35) connecting to the second valve end (11). ) forming a pressurizable space (16), and 2. that the plunger comprises an outer piston portion (36) of reduced diameter (d) directed from the second valve end, which, in a bearing area of the valve slide, is arranged to, together with a portion (38) of the bore of corresponding reduced diameter (d), cooperate to establish a steam chamber (40) for surface steaming of the valve slide (8).
    [2]
    Valve according to claim 1, characterized in that in the case of an established steam chamber (40), a steam gap (41) is present between the outer piston portion (36) and the portion (38) of the bore with reduced diameter.
    [3]
    Valve according to claim 1 or 2, characterized in that it comprises in or in the region of the first valve end a pressurizable chamber (14), which receives a valve slide (8) belonging to a central duck piston portion (23) with a face surface (15) in the pressurized state of the chamber (14) drive the valve slide in the direction of the second valve end.
    [4]
    Valve according to claim 3, characterized in that in the pressurized state of the space (16) and the non-pressurized state of the chamber (14), it is arranged for driving the valve slide (8) in the direction of the second valve end (11).
    [5]
    Valve according to one of Claims 1 to 4, characterized in that the plunger (35) is free from the second valve end and can be pressed against the second valve end by pressure radiating into the space (16).
    [6]
    Valve according to claim 5, characterized in that the plunger (35) is movable in a radial direction relative to the second valve end when pressed against it.
    [7]
    Valve according to one of Claims 1 to 4, characterized in that the plunger (35) is connected to the second valve end, with the consent of relative movement in a radial joint in relation to the second valve end.
    [8]
    Valve according to one of Claims 1 to 4, characterized in that the plunger (35) is fixedly connected to the second valve end.
    [9]
    Valve according to one of Claims 1 to 8, characterized in that at least one slide (27) for the bore (38, 39) is provided with a cradle in the valve slide, which allows permanent pressurization of the space (16).
    [10]
    Hydraulic rock drilling machine (1) with a machine housing (2), which accommodates a working cylinder (4) with a forward and rearward percussion piston (3), characterized in that the rock drilling machine comprises a distribution valve according to any one of claims 1-9.
    [11]
    Hydraulic rock drilling machine according to claim 10, characterized in that said distribution valve is accommodated in the machine housing. 77747 20140123 13
    [12]
    Hydraulic rock drilling machine according to claim 10 or 11, characterized in that the distribution valve has a shaft (18) which is parallel to a shaft of the working cylinder (4).
    [13]
    Hydraulic rock drilling machine according to any one of claims 10 - 12, characterized in that the rock drilling machine carried a machine end (6) for the working cylinder (4), which machine end also closes a space (20) receiving a distribution valve. 77747 20140123 I Tr-1 _mud. 4, wirojp 41. 0-011 -b) „F - 9t-
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    同族专利:
    公开号 | 公开日
    SE538091C2|2016-03-01|
    WO2015142259A1|2015-09-24|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FI751895A|1975-06-26|1976-12-27|Xandor Ag|
    GB2100364B|1981-04-23|1985-01-09|Musso Mario|A hydraulic percussive drill|
    SE465938B|1986-03-21|1991-11-18|Zahnradfabrik Friedrichshafen|DISTRIBUTOR VALVE WITH CONTROL Piston FOR AT LEAST TWO WORKING CIRCUITS|
    JP4514900B2|2000-05-31|2010-07-28|古河機械金属株式会社|Shock absorber of hydraulic striking device|
    SE536903C2|2012-11-28|2014-10-21|Atlas Copco Rock Drills Ab|Device at distribution valve for a rock drill and rock drill|
    SE538113C2|2013-01-30|2016-03-08|Atlas Copco Rock Drills Ab|Procedure for damping at a drilling machine, drilling machine and vehicles carrying a drilling machine|
    法律状态:
    2016-11-01| NUG| Patent has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    SE1450300A|SE538091C2|2014-03-18|2014-03-18|Distribution valve and rock drill|SE1450300A| SE538091C2|2014-03-18|2014-03-18|Distribution valve and rock drill|
    PCT/SE2015/050299| WO2015142259A1|2014-03-18|2015-03-17|Distribution valve and rock drilling machine|
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