Source: https://patents.google.com/patent/WO2015115106A1/en
Timestamp: 2020-02-20 02:26:22
Document Index: 481699319

Matched Legal Cases: ['art 22', 'art 62', 'art 51', 'art 52', 'art 51', 'arts 62', 'arts 62', 'art 62', 'art 52']

WO2015115106A1 - Hydraulic hammering device - Google Patents
WO2015115106A1
WO2015115106A1 PCT/JP2015/000409 JP2015000409W WO2015115106A1 WO 2015115106 A1 WO2015115106 A1 WO 2015115106A1 JP 2015000409 W JP2015000409 W JP 2015000409W WO 2015115106 A1 WO2015115106 A1 WO 2015115106A1
PCT/JP2015/000409
匡弘 小泉
年雄 松田
後藤　智宏
駿介 越後谷
2015-01-30 Application filed by 古河ロックドリル株式会社 filed Critical 古河ロックドリル株式会社
2015-08-06 Publication of WO2015115106A1 publication Critical patent/WO2015115106A1/en
239000002321 cushion Substances 0 abstract claims description 81
238000009527 percussion Methods 0 claims description 50
239000010720 hydraulic oil Substances 0 claims description 40
230000003628 erosive Effects 0 description 33
A hydraulic hammering device which uses a scheme in which a front chamber is switched to a low-pressure circuit when a piston moves forward, wherein the occurrence of "galling" of the piston in a sliding contact portion with a front-chamber liner is reduced. The front chamber (2) has the front-chamber liner (30) fitted to an inner surface of a cylinder (10). A liquid chamber space communicating with the front chamber (2) and filled with hydraulic fluid is formed as a cushion chamber (3) on the inner peripheral surface of a rear portion of the front-chamber liner (30). The cushion chamber (3) has a second drain circuit (from first end face grooves (46) to slits (48) to second end face grooves (47)) which is provided separately from a drain circuit that guides the hydraulic fluid passing through a liner bearing of the front-chamber liner (30) to the low-pressure circuit.
Hydraulic striking device
The present invention relates to a hydraulic hitting device such as a rock drill or a breaker.
As this type of hydraulic striking device, for example, a technique described in Patent Document 1 is known.
The hydraulic striking device described in Patent Document 1 includes a piston having a large diameter portion at the center in the axial direction and small diameter portions formed before and after the large diameter portion. The piston is slidably fitted into the cylinder, so that a front chamber and a rear chamber are defined between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder.
The front chamber is always communicated with the high pressure circuit, while the rear chamber is alternately communicated with the high pressure circuit and the low pressure circuit by the switching valve mechanism. When the rear chamber communicates with the high-pressure circuit, the front and rear pressure receiving areas are made different so that the piston moves in the striking direction, so that the forward and backward movements of the piston are repeated in the cylinder (hereinafter referred to as the following). , Also called “rear chamber alternating switching method”).
By the way, the hydraulic striking device described in Patent Document 1 adopting the “rear chamber alternate switching method” moves the piston in the striking direction by the pressure receiving area difference at the time of striking as described above. Therefore, the hydraulic oil on the front chamber side acts to resist the movement of the piston in the striking direction. For this reason, there is room for consideration in further improving the hitting efficiency.
On the other hand, for example, Patent Document 2 discloses a hydraulic striking device that switches a front chamber and a rear chamber alternately between a high-pressure circuit and a low-pressure circuit (hereinafter, also referred to as “front and rear chamber alternate switching method”). . With the hydraulic striking device of the “front / rear chamber alternate switching method”, the front chamber is switched to the low pressure circuit when the piston moves forward, so that the hydraulic oil on the front chamber side does not resist the movement of the piston in the striking direction. Therefore, it is suitable for improving the hitting efficiency.
Japanese Utility Model Publication No. 61-169588 JP-A-46-1590 Japanese Utility Model Publication No. 5-39877
However, in the hydraulic striking device of the “front / rear chamber alternating switching system”, the hydraulic oil undergoes a rapid pressure fluctuation in the front chamber in a normal striking phase in which the piston reverses from the striking process in which the piston moves forward and shifts to the retreating process. Such hydraulic oil pressure fluctuations in the front chamber are not a serious problem in the hydraulic rear impact device of the “rear chamber alternate switching system” because the front chamber is always in communication with the high pressure circuit. On the other hand, in the hydraulic striking device of the “front and rear chamber alternate switching method”, there is a problem that many micro bubbles, that is, cavitation easily occur in the hydraulic oil. There is also a problem that erosion is caused by the impact pressure due to the disappearance of cavitation.
Further, the inventors of the present invention found that the problem of cavitation in the anterior chamber is that the anterior chamber becomes a low pressure when the piston moves forward because the anterior chamber is switched to a low pressure circuit when the piston moves forward. I thought. That is, in addition to the above-mentioned “front and rear chamber alternate switching method” in which the front chamber becomes low pressure when the piston moves forward, the “front chamber alternate switching method” in which the rear chamber is always connected to high pressure and the front chamber is alternately switched between high pressure and low pressure. (For example, see Patent Document 3), there is a similar problem.
Therefore, the present invention has been made paying attention to such problems, and prevents or suppresses cavitation in the front chamber in a hydraulic striking device that switches the front chamber to a low pressure circuit when the piston moves forward. It is an object of the present invention to provide a hydraulic striking device to be obtained.
Here, in the hydraulic striking device, for example, in a rock drill (drifter), a cushion chamber is provided in the front chamber as a braking mechanism in order to prevent the large-diameter portion of the piston from colliding with the cylinder at the piston front stroke end. Things have been done.
As shown in an example in which a cushion chamber is provided in the front chamber in FIG. 7, in this example, a liquid chamber space filled with hydraulic oil is defined at the rear portion of the front chamber liner 130, and this liquid chamber space is defined as the front chamber. The cushion chamber 103 communicates with 102. The cushion chamber 103 restricts the movement of the piston 120 by closing the liquid chamber when the large-diameter portion 121 of the piston 120 enters the cushion chamber 103. At this time, if the pressure oil flows out from the cushion chamber 103 toward the front chamber 102 at a high speed, local cavitation occurs at a location where the flow velocity of the pressure oil is high.
Therefore, in order to solve the above-mentioned problem, the hydraulic striking device according to the first aspect of the present invention is a hydraulic striking device that strikes a striking rod by moving a piston slidingly fitted in a cylinder back and forth. A front chamber and a rear chamber defined between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder and spaced apart from each other; and switching the front chamber to a low-pressure circuit when the piston moves forward A switching valve mechanism for supplying and discharging hydraulic oil so that the forward and backward movements of the piston are repeated, and the front chamber has a front chamber liner fitted to the inner surface of the cylinder, and the front chamber liner Is provided with a liquid chamber space that is communicated with the front chamber and filled with hydraulic oil as a cushion chamber, and the cushion chamber guides the hydraulic fluid that passes through the liner bearing portion of the liner for the front chamber to a low-pressure circuit. Installed separately from the drain circuit It is in and having a second drain circuit through a portion other than the liner bearing portion.
According to the hydraulic striking device according to the first aspect of the present invention, the second drain circuit is a drain circuit (hereinafter referred to as a “first drain circuit”) that guides hydraulic fluid passing through the liner bearing portion of the front chamber liner to the low pressure circuit. Since it is provided separately from the drain circuit portion and passes through a portion other than the liner bearing portion, the hydraulic oil in the cushion chamber can be leaked from the portion other than the liner bearing portion to the low pressure circuit. Therefore, when the pressure oil is compressed in the cushion chamber and becomes an ultra-high pressure state, such as in the “shank rod forward state”, the hydraulic oil that flows out of the cushion chamber in the front chamber liner is removed from the liner bearing part. From this point, it is possible to escape to the “second drain circuit”. The second drain circuit leaks hydraulic oil from a location other than the liner bearing portion to the low pressure circuit, so that the necessary clearance can be maintained in the liner bearing portion, and the impact efficiency during normal striking can be reduced as much as possible. Can be prevented.
Thereby, compared with the case where the “second drain circuit” shown in FIG. 7 as a comparative example is not provided, the adiabatic compression in the cushion chamber is reduced according to the hydraulic striking device according to the first aspect of the present invention. Therefore, the oil temperature rise of the hydraulic oil is also suppressed. Furthermore, since the flow velocity of the hydraulic oil flowing into the front chamber is reduced, the occurrence of local cavitation is suppressed. Next, although the front chamber is switched to a high pressure by the switching valve mechanism, since cavitation is suppressed, heat generation due to the compression of cavitation is mitigated, and the rise in hydraulic oil temperature can be dramatically reduced. Therefore, expansion of the copper alloy part of the liner for the front chamber accompanying this is also eased. Therefore, it is possible to reduce the occurrence of “squeezing” of the piston at the sliding contact portion with the front chamber liner. The passage area due to the “first drain circuit” decreases rapidly due to the expansion due to the temperature rise, whereas the passage area due to the “second drain circuit” is hardly affected by the temperature rise.
Furthermore, focusing on the piston operation when the piston moves forward to the front end of the stroke and stops in the cushion chamber, the pressure oil supplied to the front chamber by valve switching is cushioned from the gap between the inner diameter of the rear liner and the large diameter portion of the piston. It is fed into the room and the piston turns backward. At this time, a part of the pressure oil is discharged from the “second drain circuit”, so that the pressure rise in the cushion chamber is moderate. Therefore, the retreat speed of the piston becomes slow, and the number of hits per hour in the “shank rod advance state” decreases, so that the oil temperature rise in the front chamber is mitigated.
Here, in the hydraulic striking device according to the first aspect of the present invention, the second drain circuit is a hydraulic oil in the cushion chamber via one or a plurality of communication holes passing through a portion other than the liner bearing portion. The total passage area of the one or more communication holes is the clearance amount of the liner bearing portion (inner and outer diameter directions between the small diameter portion of the piston and the sliding surface of the inner periphery of the front liner). Is preferably set to an area within a predetermined range defined in the following (Equation 1).
0.1 Apf <A <2.5 Apf (Formula 1)
However, Apf: liner bearing clearance amount A: total passage area of the communication hole With such a configuration, a decrease in impact efficiency at the time of normal impact is suppressed as much as possible, while in the “shank rod advance state” Thus, it is suitable for suppressing the rise in the hot water temperature when the pressure oil is compressed in the cushion chamber to be in an ultra-high pressure state. In addition, it is preferable to attach a throttle mechanism to the second drain circuit in which one or a plurality of communication holes are always communicated with the low-pressure circuit.
Further, in the hydraulic striking device according to the first aspect of the present invention, the front chamber liner communicates with the cushion chamber as the one or a plurality of communication holes and is separated in the circumferential direction and in the radial direction. And a slit formed in the outer circumferential surface of the front chamber liner along the axial direction so as to communicate with the radial communication path in accordance with the position of the radial communication path. A drain port communicating with the axial communication path is formed between the outer peripheral surface on the front end side of the liner for the front chamber and the inner peripheral surface of the cylinder. The drain port is connected to a low-pressure port that is always in communication with the low-pressure circuit, and the second drain circuit supplies hydraulic oil in the cushion chamber to the radial communication passage, the axial communication passage, and the drain. Port this It is preferable that always communicates with the low pressure circuit in communication with. Such a configuration eliminates the need for a dedicated low-pressure port for the “second drain circuit”, which is suitable for providing the “second drain circuit” while simplifying the structure.
In order to solve the above-mentioned problem, the hydraulic striking device according to the second aspect of the present invention is a hydraulic striking device that strikes a striking rod by moving a piston fitted in the cylinder back and forth. A front chamber and a rear chamber defined between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder and spaced apart from each other; and switching the front chamber to a low-pressure circuit when the piston moves forward A switching valve mechanism for supplying and discharging hydraulic oil so that the forward and backward movements of the piston are repeated, and the front chamber has a front chamber liner fitted to the inner surface of the cylinder in front of the front chamber. The front chamber liner is composed of a front liner and a rear liner which are divided into two parts in the axial direction, and the front liner is made of a copper alloy and serves as a bearing member that supports sliding of the piston, The rear liner is more functional than the front liner. Characterized in that the strength is made higher alloy.
According to the hydraulic striking device according to the second aspect of the present invention, the front chamber liner in front of the front chamber is divided into a front liner on the front side and a rear liner on the rear side, and the front liner is made of a copper alloy. Since the rear liner is made of an alloy having higher mechanical strength than the front liner, the cavitation erosion is made of an alloy having higher mechanical strength than the front liner. The bearing function for receiving and supporting the piston by the rear liner can be received by the front liner made of copper alloy. Therefore, while maintaining the piston sliding support function as a required bearing on the front chamber side with the front liner, the rear liner on the front chamber side resists the impact pressure caused by the disappearance of cavitation in the front chamber, and is resistant to erosion. Can be increased. Therefore, the malfunction caused by cavitation erosion in the front chamber can be minimized.
Further, according to the results of the experimental study by the present inventor, the cavitation erosion in the front chamber is unevenly distributed on the farthest side in the circumferential direction with respect to the opening of the front chamber passage through which the hydraulic oil in the front chamber is supplied and discharged. It was confirmed that this occurred.
Therefore, in the hydraulic striking device according to the second aspect of the present invention, the cylinder inner surface has a front chamber port formed in an annular shape facing the outer peripheral surface on the rear side of the front chamber liner, A front chamber passage for switching high and low pressures of hydraulic fluid in the front chamber is connected so as to communicate with the front chamber port, and the front chamber liner extends to a position facing the front chamber port, and It is preferable that a plurality of through-holes spaced in the circumferential direction are formed through the surface facing the anterior chamber port in the radial direction.
In such a configuration, a front chamber port formed in an annular shape is provided on the inner surface of the cylinder, and a front chamber passage for switching between high and low pressures is connected so as to communicate with the front chamber port. A plurality of through-holes extending in a radial direction are formed in a surface facing the front chamber port and extending in a radial direction on a surface facing the front chamber port, so that a plurality of through-holes in the rear liner are formed. The holes serve as a dispersion region for the generated cavitation.
Accordingly, cavitation generated inside the front chamber liner is dispersed before entering the front chamber port by the plurality of through holes of the rear liner. Therefore, even if cavitation occurs, the uneven distribution of cavitation in the portion farthest in the circumferential direction with respect to the opening of the front chamber passage is alleviated. Therefore, intensive erosion in this portion can be effectively suppressed. Furthermore, since the rear side of the rear liner extends to the rear of the front chamber port, the occurrence of erosion on the cylinder inner diameter sliding surface can be prevented. Therefore, consumable parts due to erosion can be minimized.
Further, the present inventors have devised the liquid chamber shape and volume of the cushion chamber to solve the problem of cavitation at the time of the sudden pressure fluctuation and the local cavitation, thereby reducing the pressure of the hydraulic oil in the front chamber. Suppressing the occurrence of cavitation at the time of reduction as much as possible. Even if cavitation occurs and erosion occurs, if erosion occurs in a place that does not affect the sliding with the piston, it is caused by cavitation erosion It was found that it was possible to minimize the damage and prevent it from being immediately hitless.
Furthermore, in order to solve the above-mentioned problem, the hydraulic striking device according to the third aspect of the present invention is a hydraulic striking device that strikes a striking rod by moving a piston slidingly fitted in a cylinder back and forth. A front chamber and a rear chamber defined between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder and spaced apart from each other; and switching the front chamber to a low-pressure circuit when the piston moves forward A switching valve mechanism for supplying and discharging hydraulic oil so that the forward and backward movements of the piston are repeated, and the front chamber has a front chamber liner fitted to the inner surface of the cylinder, and the front chamber liner Is provided with a liquid chamber space communicating with the front chamber and filled with hydraulic oil as a cushion chamber. The cushion chamber includes a first annular portion on the rear end side, and the first annular portion. Than the first ring part formed adjacent to the front of And having a second annular parts of the diameter.
According to the hydraulic striking device according to the third aspect of the present invention, the cushion chamber is formed adjacent to the first annular portion on the rear end side and the front of the first annular portion. Since the second annular portion having a larger diameter than the annular portion is provided, the pressure drop of the hydraulic oil can be reduced by the volume expansion by the second annular portion 52 provided on the front side of the first annular portion. Therefore, the occurrence of cavitation in the front chamber 2 can be suppressed.
Here, in the hydraulic striking device according to the third aspect of the present invention, it is preferable that the front end surface forming the second annular portion is an orthogonal surface orthogonal to the axial direction. With such a configuration, even if cavitation occurs in the second annular portion of the cushion chamber and erosion occurs, the front end surface forming the second annular portion is orthogonal to the axial direction. Therefore, the cavitation toward the front liner side having a bearing function can be retained in the second annular portion by this orthogonal surface, and erosion can be generated at a position that does not affect the sliding with the piston. For this reason, it is possible to minimize a problem caused by cavitation erosion and to prevent an impossibility of hitting immediately.
As described above, according to the present invention, cavitation in the front chamber can be prevented or suppressed in the hydraulic striking device that switches the front chamber to the low pressure circuit when the piston moves forward.
It is sectional drawing explaining one Embodiment of the hydraulic striking device which concerns on 1 aspect of this invention, The figure has shown the cross section along an axis line. It is an enlarged view of the principal part (front chamber liner part) of FIG. FIG. 3 is a cross-sectional view of a main part of the liner for the front chamber of FIG. 2, in which FIG. 2 (a) is a cross-sectional view along the line AA in FIG. 2, FIG. It is CC sectional drawing. It is a perspective view of the back liner which constitutes the liner for front rooms of Drawing 2, The figure (a) shows the 1st example, (b) shows the 2nd example, and (c) shows the 3rd example. Yes. BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view explaining operation | movement of one Embodiment of the hydraulic striking device which concerns on 1 aspect of this invention, The figure has shown the shank rod part collectively in the example applied to a rock drill. (A) shows the normal striking position, (b) is when the piston is retracted in normal striking, and the upper side of the center line shows the time of deceleration in the backward direction, and the lower side of the center line shows the piston behind (C) is the state of forward movement of the shank rod, and the upper side of the center line in the figure shows when the piston enters the cushion chamber, and the lower side of the center line shows when the piston stops. Show. It is a schematic diagram explaining the effect of several through-hole parts formed in the back liner, The figure (a) is an example which does not provide an inner surface side annular groove in several through-hole parts, ) Is a view taken in the direction of arrow D in (a), and FIG. 5B is an example in which inner surface side annular grooves are provided in a plurality of through-hole portions, and FIG. E view is shown. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the comparative example with respect to the hydraulic-type impact apparatus which concerns on 1 aspect of this invention, and its one embodiment, The figure is a longitudinal cross-sectional view which shows a shank rod part typically in the application example of a rock drill It is.
The hydraulic striking device 1 according to the present embodiment is a “front / rear chamber alternating switching” striking device, and as shown in FIG. 1, the piston 20 is a solid cylindrical shaft member having a central axial direction. Large diameter portions 21 and 22 and small diameter portions 23 and 24 formed before and after the large diameter portions 21 and 22. The piston 20 is slidably fitted into the cylinder 10 so that the front chamber 2 and the rear chamber 8 are defined between the outer peripheral surface 20g of the piston 20 and the inner peripheral surface 10n of the cylinder 10, respectively. Has been. The step portion where the large-diameter portion 21 and the small-diameter portion 23 on the front side in the axial direction are connected is a pressure-receiving surface on the front chamber 2 side for applying thrust in the traveling direction of the piston 20, The pressure receiving surface on the front chamber 2 side is a conical surface 26 that decreases in diameter from the large diameter portion 21 side toward the small diameter portion 23 side. On the other hand, the step portion where the large-diameter portion 22 and the small-diameter portion 24 on the rear side in the axial direction are connected is a pressure receiving surface on the rear chamber 8 side, and in this embodiment, the pressure receiving surface on the rear chamber 8 side is large. The end face on the diameter part 22 side is an orthogonal surface 27 orthogonal to the axial direction.
Between the large diameter portions 21 and 22, a control groove 25 is formed by a concave stepped portion. The control groove 25 is connected to the switching valve mechanism 9 via a plurality of control ports. The front chamber 2 and the rear chamber 8 are connected to the switching valve mechanism 9 via the high / low pressure switching ports 5 and 85, respectively. The switching valve mechanism 9 allows hydraulic oil to be supplied and discharged at a desired timing, so that the front chamber 2 and the rear chamber 8 are alternately communicated with the high-pressure circuit 91 and the low-pressure circuit 92, respectively, and the pressure receiving surface is made of hydraulic oil. By being pushed in the axial direction by hydraulic pressure, the forward and backward movements of the piston 20 are repeated in the cylinder 10. A front head 6 and a back head 7 corresponding to a striking device such as a rock drill or a breaker are mounted on the front and rear of the cylinder 10, respectively.
Here, the front chamber 2 has a front chamber liner 30 provided in front of the front chamber 2 and fitted to the cylinder inner peripheral surface 10n. An annular seal retainer 32 is fitted to the cylinder inner peripheral surface 10 n on the front side of the front chamber liner 30. In the seal retainer 32, packing or the like is fitted in a plurality of annular grooves 32a formed at appropriate positions on the inner and outer peripheral surfaces of the seal retainer 32, thereby preventing the hydraulic oil from leaking to the front of the front chamber 2. The rear chamber 8 has a cylindrical rear chamber liner 80 provided behind the rear chamber 8 and fitted to the cylinder inner peripheral surface 10n.
The rear chamber liner 80 integrally includes a rear chamber defining portion 81, a bearing portion 82, and a seal retainer portion 83 in order from the front in the axial direction. The rear chamber 8 is defined by a cylindrical space on the front inner periphery of the rear chamber defining portion 81, a liquid chamber space between the inner peripheral surface of the cylinder 10 and the outer peripheral surface of the small diameter portion of the piston 20. A rear chamber passage 85 is connected to the inner peripheral surface of the cylinder 10 that defines the rear chamber 8. The bearing portion 82 is in sliding contact with the outer peripheral surface of the small-diameter portion on the rear side of the piston 20 and pivotally supports the rear portion of the piston 20. On the inner peripheral surface of the bearing portion 82, a plurality of annular oil grooves 82a are separated in the axial direction to form a labyrinth. In the seal retainer portion 83, packing or the like is fitted into a plurality of annular grooves 83a formed at appropriate positions on the inner and outer peripheral surfaces thereof to prevent the hydraulic oil from leaking to the rear of the rear chamber 8. A drain communication hole 84 is formed in the radial direction between the bearing portion 82 and the seal retainer 83, and the communication hole 84 is connected to a rear chamber low pressure port (not shown).
The front chamber liner 30 is composed of a pair of front liner 40 and rear liner 50 in the axial direction. That is, in the present embodiment, the front chamber liner 30 is divided by the separate liners on the front side and the rear side in the axial direction. In the present embodiment, the front liner 40 is not provided with a liquid chamber, the liquid liner space is provided only in the rear liner 50, and the liquid chamber space formed in communication with the front chamber 2 at the rear portion of the rear liner 50. Is the cushion chamber 3. In order to prevent the large-diameter portion 21 of the piston 20 from colliding with the cylinder 10 at the stroke front end of the piston, the cushion chamber 3 has a liquid chamber as a closed space when the large-diameter portion 21 of the piston 20 intrudes. 20 movements are restricted.
Specifically, the front liner 40 is made of a copper alloy, and has a flange portion 41 that protrudes in an annular shape toward the radially outer side at the front end portion, as shown in an enlarged view in FIG. The rear portion is also a cylindrical bearing portion 42. A drain port 45 having an annular shape is formed between the outer periphery of the flange portion 41 and the inner peripheral surface of the cylinder 10, and the drain port 45 is connected to a drain passage 49.
The front liner 40 has an outer circumferential surface of the small-diameter portion 23 of the piston 20 having a facing gap narrower than a predetermined facing gap (clearance between the outer diameter of the piston 20 and the inner diameter of the liner) of the small-diameter portion 54 on the inner periphery of the front end side of the rear liner 50. It is in sliding contact with 23g. A plurality of annular oil grooves 40m are separated in the axial direction on the sliding contact surface 40n on the inner periphery of the front liner 40 to form a labyrinth. The front liner 40 is not provided with a liquid chamber space other than the oil groove 40m, and serves as a bearing for slidingly supporting the piston 20.
The rear end surface 42t of the front liner 40 is in contact with the front end surface 50t of the rear liner 50, and a plurality of first end surface grooves 46 are provided on the rear end surface 42t of the front liner 40 so as to be spaced apart from each other in the circumferential direction. A passage is formed along the radial direction. In this example, the plurality of first end face grooves 46 are spaced apart in the circumferential direction and equally distributed at four locations (see FIG. 3B).
Further, in the front liner 40, a plurality of slits 48 are formed as axial communication paths along the axial direction on the outer peripheral surface 42g of the cylindrical bearing portion 42 in accordance with the formation position of the first end surface groove 46. ing. In this example, the plurality of slits 48 are equally arranged at four locations in accordance with the position of the first end face groove 46 (see FIG. 3A). Further, a plurality of second end face grooves 47 are formed as radial communication paths along the radial direction on the surface of the front liner 40 facing the rear side of the collar portion 41 in accordance with the positions of the plurality of slits 48. .
The plurality of second end surface grooves 47 communicate with the drain port 45 provided on the outer periphery of the flange portion 41 of the front liner 40. As a result, the hydraulic oil in the cushion chamber 3 of the rear liner 50 is passed through the predetermined gap of the small-diameter portion 54 on the front end side of the rear liner 50, and further, “first end surface groove 46 to slit 48 to second end surface groove 47 to It is possible to escape to the drain passage 49 through the drain port 45 ".
In other words, this circuit functions as a “drain circuit”. In addition, the drain circuit of pressure oil (hereinafter referred to as “first drain circuit”) passing through the liner bearing portion (opposite clearance in the inner and outer diameter direction between the small diameter portion 23 of the piston 20 and the sliding contact surface 40 n on the inner periphery of the front liner 40). This circuit can be referred to as a “second drain circuit”.
In the communication hole composed of “first end face groove 46 ˜slit 48 ˜second end face groove 47”, the passage areas of the first end face groove 46, slit 48, and second end face groove 47 are set to substantially equal areas. . In addition, although the four communication holes of this embodiment are formed in four places, the “total passage area of the communication holes” obtained by adding the passage areas of the plurality of communication holes is the “clearance amount of the liner bearing portion”. On the other hand, it is set to an area within a predetermined range defined in the following (Equation 1), whereby the leak amount of pressure oil from the “second drain circuit” is limited to a predetermined amount. Here, “the clearance amount of the liner bearing portion” is an area of an annular clearance formed by a facing clearance in the inner and outer diameter direction between the small diameter portion 23 of the piston 20 and the sliding contact surface 40 n on the inner periphery of the front liner 40. is there.
Where Apf: liner bearing clearance A: total passage area of communication hole
The rear liner 50 is made of an alloy having higher mechanical strength than the front liner 40 made of the copper alloy. In this embodiment, the mechanical strength of the alloy steel is improved by heat treatment of the alloy steel. For example, carburizing, quenching, and tempering can be performed on the case-hardened steel to form a hardened layer on the surface. The rear liner 50 has a cylindrical shape, and the outer diameter of the cylindrical shape is the same as the outer diameter of the bearing portion 42 of the front liner 40. The inner diameter of the rear liner 50 is such that the inner diameter of the inner peripheral portion 50n on the rear end side is a slidable contact surface with a slight gap from the large diameter portion 21 of the piston 20. On the other hand, the dimension of the small-diameter portion 54 on the inner periphery of the front end side of the rear liner 50 is larger than the inner diameter dimension of the sliding contact surface 40 n on the inner periphery of the front liner 40, and the liner bearing described above with respect to the outer peripheral surface of the piston 20. A predetermined facing gap larger than the clearance of the part is separated.
An annular front chamber port 4 is formed between the outer peripheral surface 50g on the rear side of the rear liner 50 and the inner peripheral surface of the cylinder 10, and the front chamber for switching the high and low pressures of the front chamber 2 to the front chamber port 4 is formed. A passage 5 is connected. In other words, the rear liner 50 of the present embodiment has the extending portion 55 that extends rearward from the front chamber port 4.
In the present embodiment, the rear liner 50 is formed with an outer surface-side annular groove 56 on the outer peripheral surface of the extending portion 55 at a position facing the front chamber port 4, and the inner periphery of the extending portion 55. An inner surface side annular groove 57 is formed on the surface. A plurality of circumferentially spaced through holes 58 are formed in the inner and outer annular grooves 56 and 57 in the radial direction.
It is preferable that the plurality of through holes 58 are equally arranged in the circumferential direction (in the example shown in FIG. 3C, the through holes 58 are equally arranged at 16 locations). The shape of the plurality of through-holes 58 is not particularly limited. For example, as shown in FIG. 4 (a) or a rectangle (the corner is R-shaped) or an ellipse, as shown in FIG. 4 (b). Can do. If the through hole 58 has a “slot shape (long hole shape)” in which the circumferential direction is longer than the axial direction, such as a rectangle or an ellipse, the passage area of each through hole 58 is increased. This is preferable for reducing the generation of cavitation by suppressing the flow rate of the cavitation.
As shown in FIG. 4C, the rear liner 50 can be further divided. In the example shown in the figure, a split structure is formed at the position of the rear side edge surface of the through-hole 58 having the “slot shape” shown in FIG. 4B, so that the rear liner (front) 63 and the rear liner ( The rear liner 50 is composed of the rear 64. By dividing the rear liner 50 into two parts at this position, the column part 62 formed between the through holes 58 adjacent in the circumferential direction extends from the rear end of the rear liner (front) 63 toward the rear. It is a beam.
Further, as shown in FIG. 2, the cushion chamber 3 is formed on the inner peripheral surface on the rear side of the rear liner 50. In the present embodiment, the cushion chamber 3 includes a first annular part 51 on the rear side in the axial direction and a second annular part 52 formed in front of the first annular part 51. A portion where the first annular portion 51 and the second annular portion 52 are connected is a conical surface 59 whose diameter increases from the first annular portion 51 side toward the second annular portion 52 side.
The first annular portion 51 communicates with the inner surface side annular groove 57 over the entire circumference at the rear in the axial direction. The first annular portion 51 has a diameter (small diameter) shallower than the depth (inner diameter) of the inner surface side annular groove 57, and the rear side thereof is formed adjacent to the front side of the inner surface side annular groove 57. . The second annular portion 52 has a larger diameter than the first annular portion 51, and the rear of the second annular portion 52 is formed adjacent to the front of the first annular portion 51. An end surface on the front side that forms the second annular portion 52 is an orthogonal surface 53 that is orthogonal to the axial direction.
Next, the operation, action, and effect of the hydraulic striking device 1 will be described. Here, as an example in which the hydraulic striking device 1 of the present embodiment is applied to a rock drill, it will be described with reference to FIG. 5 as appropriate. As shown in FIG. 5A, the rock drill has a shank rod 60 in front of the piston 20 of the hydraulic striking device 1. The shank rod 60 has a spline 61 formed at the rear, and is supported by the front cover 70 so as to be slidable in the axial direction within a predetermined range. The shank rod 60 is restricted in its rearward movement limit by a damper mechanism (not shown). Further, the rock drill includes a feed mechanism and a rotation mechanism (not shown), and the shank rod 60 can be rotated by a rotation mechanism meshing with the spline 61, and the cylinder 10 side of the hydraulic striking device 1 is a feed mechanism. Is fed according to the amount of crushing.
Normal striking is performed when the striking efficiency of the piston 20 is maximum in the rearward movement limit of the shank rod 60 shown in FIG. When the shank rod 60 is hit by the piston 20, a shock wave generated by the hit is propagated from the shank rod 60 to the bit at the tip (not shown) through the rod, and the bit is used as energy for crushing the rock mass. The cylinder 10 side is fed according to the amount of crushing by a feed mechanism (not shown). When hydraulic oil is supplied and discharged at the expected timing by the switching valve mechanism 9 of the hydraulic striking device 1, the piston 20 is retracted in the cylinder 10 as shown in FIG. Is then decelerated at a predetermined position in the backward direction shown on the upper side of the center line, and then, as shown on the lower side of the center line, the piston 20 starts moving again in the forward direction at the rear dead center.
Here, in the hydraulic striking device 1, when hydraulic oil is supplied and discharged at a predetermined timing by the switching valve mechanism 9, the front chamber 2 and the rear chamber 8 are connected to the high and low pressure switching ports 5 and 85, respectively. Thus, the high pressure circuit 91 and the low pressure circuit 92 are alternately communicated, whereby the piston 20 is repeatedly advanced and retracted in the cylinder 10. That is, in the hydraulic striking device 1, the hydraulic oil on the front chamber 2 side does not resist the movement of the piston in the striking direction due to the “front / rear chamber alternating switching system” striking. Therefore, it is suitable for improving the hitting efficiency.
Here, in the drill hole, if the bit does not rock normally due to entering the hollow band, the shank rod 60 moves forward from the normal striking position as shown in FIG. A "shank rod advance state" occurs. At this time, in order to prevent the large-diameter portion 21 of the piston 20 from colliding with the cylinder 10 at the piston front stroke end, the cushion chamber 3 communicating with the front chamber 2 is provided. As shown in the upper side of the center line in FIG. 3C, the cushion chamber 3 restricts the movement of the piston by closing the liquid chamber when the large diameter portion 21 of the piston 20 enters the cushion chamber 3. As a result, as shown on the lower side of the center line in FIG. 5C, the end of the large diameter portion 21 of the piston 20 (the position of the conical surface 26) stays in the cushion chamber 3, so The large diameter portion 21 of the piston 20 can be prevented from colliding with the cylinder 10.
Here, in this type of “front and rear chamber alternate switching type” hydraulic striking device, a negative pressure state is generated in the hydraulic pressure in the front chamber, and cavitation is likely to occur. Further, when the piston is braked by the cushion chamber, the pressure oil is compressed in the cushion chamber to be in an ultra-high pressure state. For this reason, compression in the cushion chamber, local cavitation at a location where the flow rate of pressurized oil is high, and temperature rise of the hydraulic oil accompanying compression become problems. Further, since the gap between the piston and the front chamber liner is reduced, the drain function is lowered and the discharge of high-temperature pressure oil is suppressed, so that the temperature rise is accelerated.
Specifically, in the hydraulic striking device of the “front / rear chamber alternate switching system”, for example, in a rock drill (drifter), a braking mechanism is used to prevent the large-diameter portion of the piston from colliding with the cylinder at the piston front stroke end. A cushion chamber is provided in the front chamber. FIG. 7 shows a comparative example for this embodiment.
In the comparative example shown in the figure, a shank rod 160 is disposed in front of the piston 120. An annular front chamber port 104 is formed on the front side inside the cylinder 110, and an integrated front chamber liner 130 made of a copper alloy is fitted to the inner surface of the cylinder 110 in front of the front chamber port 104. ing. A liquid chamber space filled with hydraulic oil is defined at the rear portion of the front chamber liner 130, and the liquid chamber space is a cushion chamber 103 communicating with the front chamber 102.
The piston 120 hits the rear end of the shank rod 160 when the hitting efficiency is maximum. When the shank rod 160 is hit by the piston 120, a shock wave generated by the hit is propagated to the bit (not shown) at the tip through the rod on the tip of the shank rod 160 and used as drilling energy.
Here, in the drill hole, if the bit does not land normally due to entering the hollow zone, the bit, the rod and the shank rod 160 are fastened with screws, so Thus, a state of projecting forward (a state in which the shank rod 160 has advanced from the normal striking position) occurs (hereinafter also referred to as “shank rod advance state”). When the piston 120 operates in this “shank rod advance state”, the large-diameter portion 121 of the piston 120 enters the cushion chamber 103 and receives braking. Therefore, the pressure oil is compressed in the cushion chamber 103 to be in an ultrahigh pressure state.
Therefore, the hydraulic oil temperature rises due to compression in the cushion chamber 103. Furthermore, when the inside of the cushion chamber 103 becomes extremely high pressure, the flow rate of the pressurized oil from the cushion chamber 103 to the front chamber 102 becomes excessive. Therefore, cavitation occurs locally at a location where the flow rate of the pressurized oil is high, and then the front chamber 102 is switched to high pressure, so that the generated cavitation is compressed and heat is generated to further increase the oil temperature. As the oil temperature rises, the copper alloy portion of the front chamber liner 130 expands and contracts in diameter, and so-called “galling” may occur at the sliding contact portion with the piston 120. Note that the rise in the oil temperature in the front chamber 102 and the cushion chamber 103 is proportional to the amount of advance of the piston 120, and thus becomes maximum when the shank rod 160 moves to the front end of the stroke.
As shown in this comparative example, in the hydraulic striking device of the “front and rear chamber alternating switching method”, the problem that “caulking” is likely to occur due to the occurrence of local cavitation and the temperature rise of hydraulic oil accompanying compression. There is. In particular, the risk of the occurrence of “Kaziri” tends to increase as the number of hits increases. Further, since the gap between the piston and the front chamber liner is reduced, the drain function is lowered and the discharge of high-temperature pressure oil is suppressed, so that the temperature rise is accelerated.
On the other hand, according to the hydraulic striking device 1 of the present embodiment, the cushion chamber 3 is defined as “one or more communication holes that pass through a portion other than the liner bearing portion” by the “second drain circuit”. The hydraulic oil in the cushion chamber 3 is always communicated with the low-pressure circuit via a passage formed by the end face groove 46, the slit 48, and the second end face groove 47 ". That is, the cushion chamber 3 has the “second drain circuit” provided separately from the drain circuit that guides the hydraulic oil passing through the liner bearing portion of the liner 30 for the front chamber to the drain passage 49 that is a low-pressure circuit. When the pressure oil is compressed in the cushion chamber 3 to be in an ultrahigh pressure state, the hydraulic oil flowing out from the cushion chamber 3 in the front chamber liner 30 can be released from the “second drain circuit”.
Thereby, compared with the case where the “second drain circuit” is not provided, the compression in the cushion chamber 3 is relieved, so that the increase in the oil temperature of the hydraulic oil is also suppressed. Furthermore, since the flow rate of the hydraulic oil flowing into the front chamber 2 is reduced, the occurrence of local cavitation is suppressed. Next, although the front chamber 2 is switched to a high pressure by the switching valve mechanism 9, since the cavitation is suppressed, heat generation due to the compression of the cavitation is mitigated, and the rise in the operating oil temperature can be dramatically reduced.
Therefore, the expansion of the copper alloy portion of the front chamber liner 30 (in this embodiment, the front liner 40 constituting the front chamber liner 30) associated therewith is also relieved, so that the sliding contact location with the front chamber liner 30 is reduced. The occurrence of “galling” of the piston 20 can be reduced. The passage area due to the “first drain circuit” rapidly decreases due to the expansion due to the temperature rise, whereas the passage area due to the “second drain circuit” is hardly affected by the temperature rise.
Further, paying attention to the piston operation when the piston 20 moves forward to the front end of the stroke in the cushion chamber 3 and stops, the pressure oil supplied to the front chamber 2 by valve switching is larger than the inner diameter of the rear liner 50 and the piston 20. The piston 20 is supplied into the cushion chamber 3 from the gap of the diameter portion 21 and turns backward. At this time, a part of the pressure oil is discharged from the “second drain circuit”. The pressure rise is moderate. Accordingly, the retreat speed of the piston 20 is slowed, and the number of hits per hour in the “shank rod advance state” is reduced, so that the oil temperature rise in the front chamber 2 is alleviated.
In the present embodiment, the total passage area of the passage composed of the “first end face groove 46 to the slit 48 to the second end face groove 47” as the plurality of communication holes is equal to the clearance amount of the liner bearing portion. Since it is set to an area within the predetermined range defined in Equation 1), while suppressing the reduction of the striking efficiency at the time of normal striking as much as possible, in the cushion chamber as in the “shank rod advance state”, etc. An increase in hot water temperature when the pressure oil is compressed to an ultra-high pressure state can be suppressed.
Further, the second drain circuit of the present embodiment passes the hydraulic oil of the cushion chamber 3 through the first end surface groove 46 that is a radial communication path, the slit 48 that is an axial communication path, and the drain port 45 in this order. Therefore, since the drain passage 49 of the low pressure circuit is always in communication, a dedicated low pressure port is not required for the “second drain circuit”. Therefore, the “second drain circuit” can be provided while simplifying the structure.
Here, the hydraulic striking device of the “front / rear chamber alternating switching method” causes a sudden pressure fluctuation of the hydraulic oil in the front chamber in a normal striking phase in which the piston reverses from the striking process in which the piston moves forward and shifts to the retreating process. . The hydraulic oil pressure fluctuation problem in the front chamber is not a serious problem in the hydraulic rear impact device of the “rear chamber alternate switching method” because the front chamber is always in communication with the high pressure circuit. On the other hand, in the hydraulic striking device of the “front / rear chamber alternate switching method”, a negative pressure state occurs, so that cavitation is likely to occur. Also, erosion due to impact pressure due to the disappearance of cavitation is likely to occur.
That is, for example, in a rock drill (drifter), a shank rod is arranged in front of the piston, and the piston moves forward to hit the rear end of the shank rod. Here, in the hydraulic striking device of the “front / rear chamber alternate switching system”, in the striking phase, when the front chamber is communicated with the low pressure circuit, when the piston strikes the shank rod, the piston is suddenly braked. At this time, even if the piston is suddenly braked, the hydraulic oil continues to flow out due to inertia, so a negative pressure state occurs in the front chamber. Therefore, cavitation tends to occur when the pressure of the hydraulic oil becomes lower than the saturated vapor pressure for a very short time. Then, when the piston moves to the retreating process after the impact, the front chamber is communicated with the high pressure circuit by the switching valve mechanism. Therefore, there is a problem that erosion is likely to occur in the front chamber due to the impact pressure when the generated cavitation is compressed and disappears.
On the other hand, according to the hydraulic striking device 1 of the present embodiment, the cushion chamber 3 is formed adjacent to the first annular portion 51 on the rear end side and the front of the first annular portion 51. And the second annular portion 52 having a diameter larger than that of the first annular portion 51, the pressure of the hydraulic oil is reduced by the volume expansion by the second annular portion 52 provided on the front side of the first annular portion 51. Can be relaxed. Therefore, the occurrence of cavitation in the front chamber 2 can be suppressed. Moreover, even if cavitation occurs, it is possible to suppress rupture and erosion. Therefore, it is more suitable for suppressing the hot water temperature rise.
Further, since the front end surface forming the second annular portion 52 of the cushion chamber 3 is an orthogonal surface 53 orthogonal to the axial direction, the cavitation is temporarily performed in the second annular portion 52 of the cushion chamber 3. Even if erosion occurs and erosion is reached, cavitation toward the front liner 40 side having a bearing function may be retained in the cushion chamber 3 by the orthogonal surface 53, and erosion may be generated at a location that does not affect sliding with the piston. it can. For this reason, it is possible to minimize a problem caused by cavitation erosion and to prevent an impossibility of hitting immediately.
Furthermore, according to the hydraulic striking device 1 of the present embodiment, the front chamber liner 30 is constituted by a front liner 40 and a rear liner 50 that are divided into two in the axial direction, and the front liner 40 is made of a copper alloy. Thus, a liquid chamber space other than the oil groove 40m is not provided to provide a bearing member that supports the sliding of the piston 20, and the rear liner 50 is made of an alloy steel having a hardened layer formed on the surface thereof. Since the liquid chamber space that is communicated and filled with hydraulic oil is provided as the cushion chamber 3, the cavitation erosion is handled by the inner wall surface of the liquid chamber space of the cushion chamber 3 of the rear liner 50 made of high-hardness steel. The bearing function for slidingly supporting the piston 20 can be handled by a copper alloy front liner 40 that does not provide a liquid chamber space.
Therefore, while maintaining the piston sliding support function as a necessary bearing on the front chamber 2 side with the front liner 40, the rear liner 50 resists the impact pressure caused by the disappearance of cavitation in the front chamber 2 and increases the resistance to erosion. be able to. Therefore, the malfunction caused by cavitation erosion can be minimized.
Further, according to the results of experimental research by the present inventors, in the hydraulic striking device of the “front and rear chamber alternate switching method”, cavitation erosion in the front chamber is caused by the high and low pressure switching port that supplies and discharges hydraulic oil from the front chamber. It was confirmed that the occurrence was unevenly distributed on the farthest side in the circumferential direction with respect to the opening.
On the other hand, according to the hydraulic striking device 1 of the present embodiment, the front chamber port 4 formed in an annular shape is provided on the inner surface of the cylinder 10, and before the high and low pressures are switched so as to communicate with the front chamber port 4. The rear liner 50 connected to the chamber passage 5 and constituting the front chamber liner 30 extends to a position facing the front chamber port 4 and is spaced circumferentially on a surface facing the front chamber port 4. Since the plurality of through holes 58 are formed so as to penetrate in the radial direction, the plurality of through holes 58 serve as a dispersion region of the generated cavitation.
Thus, cavitation generated inside the rear liner 50 constituting the front chamber liner 30 is dispersed before entering the front chamber port 4 by the plurality of through holes 58 formed in the rear liner 50. Therefore, even if cavitation occurs, the uneven distribution of cavitation in the portion farthest in the circumferential direction with respect to the opening of the opening of the front chamber passage 5 is alleviated. Therefore, intensive erosion in this portion can be effectively suppressed.
Furthermore, since the rear side of the rear liner extends to the rear of the front chamber port, the occurrence of erosion on the cylinder inner diameter sliding surface can be prevented. Therefore, consumable parts due to erosion can be minimized.
Further, in the present embodiment, the plurality of through holes 58 are provided in an inner surface side annular groove 57 formed on the inner peripheral surface of the extending portion 55, and the first annular portion 51 has an axial rear side. Since it communicates with the inner surface side annular groove 57 over the entire circumference, the cushioning effect by the cushion chamber 3 can be started at a desired position, and a reduction in impact efficiency can be prevented.
That is, as shown in FIG. 6A, if the inner surface side annular groove 57 is not provided in the plurality of through-holes 58, the large-diameter portion 21 of the piston 20 is directly connected to the through-hole 58. It will pass in sliding contact. Therefore, when the large-diameter portion 21 of the piston 20 passes through the portion of the through hole 58, the change in the pressure oil outflow passage area toward the low pressure side (the front chamber port 4 side) as shown in FIG. (The two-dot chain line in the figure shows an image of the process in which the large-diameter end ridge line passes). Therefore, the cushioning action is generated from the stage before entering the cushion chamber 3, and the impact efficiency is lowered.
On the other hand, as shown in FIG. 5B, when the inner surface side annular groove 57 is provided as in the present embodiment, when the large diameter portion 21 of the piston 20 passes through the portion of the through hole 58, By passing through the inner surface side annular groove 57, the rate of change of the pressure oil outflow passage area to the low pressure side can be made constant as shown in FIG. . Therefore, the occurrence of the cushioning action at the stage before entering the cushion chamber 3 is prevented, and from the intended position, that is, from the rear end position of the first annular portion 51 following the front end portion of the inner surface side annular groove 57. The desired cushion effect can be started.
Here, it is preferable that the plurality of column portions 62 formed between the through holes 58 adjacent in the circumferential direction are cantilever beams. In this case, as in the third embodiment shown in FIG. 4C, the rear liner 50 is divided by dividing the rear liner 50 at the position of the rear side edge surface of the through hole 58 having a “slot shape”. It is preferable that the rear liner 50 is composed of 63 and the rear liner (rear) 64.
That is, when a surge pressure is generated as the piston 20 reciprocates, in the case of a column portion having a double-sided structure as shown in FIG. Acts as Therefore, when erosion progresses in the column portion, the column portion may not withstand the tensile pressure and may be broken. On the other hand, as shown in FIG. 4C, if the plurality of column parts 62 are cantilever beams, tensile pressure due to surge pressure does not act on the column parts 62. Therefore, destruction of the column part 62 due to surge pressure can be prevented or suppressed.
As described above, according to this hydraulic striking device, cavitation in the front chamber can be prevented or suppressed. Then, it is possible to suppress the rise of the hot water temperature in the front chamber and to reduce the occurrence of “galling” of the piston at the sliding contact portion with the front chamber liner. Furthermore, it is possible to effectively prevent or suppress cavitation erosion in the front chamber, or to minimize problems caused by cavitation erosion. It should be noted that the hydraulic striking device according to the present invention is not limited to the above-described embodiment, and it goes without saying that various modifications are possible without departing from the spirit of the present invention.
For example, the hydraulic striking device 1 of the above embodiment has been described by taking the “front / rear chamber alternate switching system” striking device as an example. However, the present invention is not limited to this, and the present invention switches the front chamber to the low pressure circuit when the piston moves forward. It can be applied to the hydraulic striking device. For example, the present invention can also be applied to a “front chamber alternate switching type” striking device as disclosed in Patent Document 3.
In other words, in the “front chamber alternate switching type” striking device, the rear chamber is always communicated with the high pressure circuit, while the front chamber is alternately communicated with the high pressure circuit and the low pressure circuit by the switching valve mechanism. When the front chamber communicates with the high-pressure circuit, the front and rear pressure receiving areas are made different so that the piston moves in the backward direction, whereby the forward and backward movement of the piston is repeated in the cylinder. Therefore, since the front chamber is switched to the low pressure circuit when the piston moves forward, the front chamber becomes a low pressure when the piston moves forward, and problems such as preventing the occurrence of galling of the piston due to the oil temperature rise in the front chamber are similar. Since it occurs in the mechanism, the present invention can be applied.
Further, for example, in the above-described embodiment, the front chamber liner 30 has been described as being configured by the front liner 40 and the rear liner 50 that are divided into the front and rear in the axial direction. However, the present invention is not limited to this, and the comparative example of FIG. As shown in the figure, the front chamber liner 30 may be constituted by a monolithic liner.
However, while maintaining the piston sliding support function as a necessary bearing on the front chamber 2 side with the front liner 40, the rear liner 50 increases resistance to erosion against the impact pressure caused by the disappearance of cavitation in the front chamber 2. In the above, as in the above-described embodiment, the front chamber liner 30 is composed of a front liner 40 and a rear liner 50 that are divided in the longitudinal direction, and the rear liner 50 is an alloy having higher mechanical strength than the front liner 40. It is preferable to make it.
In the case where the front liner 40 and the rear liner 50 are divided into two parts, in the above-described embodiment, the rear liner 50 is made of “hardened steel” having a hardened layer formed on the surface by carburizing, quenching and tempering. Although the example used was demonstrated, the back liner 50 should just be a product made from an alloy whose mechanical strength is higher than the front liner 40. FIG.
For example, in order to improve mechanical strength, various curing treatments such as heat treatment, physical treatment, and chemical treatment can be employed. In addition, for example, various mechanical structural alloy steels can be employed in addition to chromium steel, chromium molybdenum steel, nickel chromium steel, and the like. In addition, the mechanical strength is not limited to forming a hardened layer on the surface, the whole may be hardened using an alloy tool steel such as SKD, and the presence or absence of a hardening treatment is not limited, For example, an alloy such as stellite may be used.
Further, for example, in the above-described embodiment, the rear liner 50 extends to a position facing the front chamber port 4, and a plurality of through holes 58 spaced in the circumferential direction are formed on the surface facing the front chamber port 4 in the radial direction. Although described in the example in which it is perforated, the position of the rear end of the front chamber liner 30 (rear liner 50) is not limited to this, as shown in the comparative example of FIG. It is also possible to set the length to the position in front of the chamber port 4.
However, the rear liner 50 is extended to a position facing the front chamber port 4 in order to more suitably mitigate the uneven distribution of cavitation in the portion farthest in the circumferential direction with respect to the opening of the front chamber passage 5. It is preferable that a plurality of through holes 58 that are spaced apart in the circumferential direction are formed in the surface facing the front chamber port 4 so as to penetrate in the radial direction. Further, in order to prevent the occurrence of erosion at the inner diameter portion of the cylinder 10, it is preferable to extend the rear liner 50 to the rear side of the front chamber port 4.
Further, for example, in the above-described embodiment, as the “second drain circuit”, the boundary portion between the front liner 40 and the rear liner 50, which is a position in front of the cushion chamber 3, is separated in the circumferential direction in the radial direction. The first end surface groove 46 is formed along the first end surface groove 46, and a plurality of communication holes including “first end surface groove 46 to slit 48 to second end surface groove 47” are always communicated with the low-pressure circuit. It is not limited to.
For example, the “second drain circuit” is formed separately from the “first drain circuit” of the pressure oil passing through the liner bearing portion, and communicates with the cushion chamber 3 through a portion other than the liner bearing portion. If so, various modifications are possible. Further, in the “second drain circuit”, it is preferable to provide a plurality of communication holes at a position in front of the cushion chamber 3, but the plurality of communication holes are formed at the boundary between the front liner 40 and the rear liner 50. It is not limited to the department. The same applies to the case where the front chamber liner 30 is constituted by a monolithic liner, as well as the case where the front chamber liner 30 is constituted by the front liner 40 and the rear liner 50.
However, when the front chamber liner 30 is constituted by the front liner 40 and the rear liner 50, an increase in the oil temperature in the cushion chamber 3 is suppressed, and the piston 20 at the sliding contact position with the front chamber liner 30 is suppressed. In order to reduce the occurrence of “galling”, a plurality of radial communication paths are formed at the boundary between the front liner 40 and the rear liner 50 so as to be circumferentially separated and penetrated along the radial direction. It is preferable to configure the “second drain circuit” so that the radial communication path is always in communication with the low-pressure circuit.
Further, for example, in the above embodiment, the cushion chamber 3 is configured from the first annular portion 51 and the second annular portion 52 having a larger diameter than the first annular portion 51 with respect to the liquid chamber shape and volume of the cushion chamber 3, Although the example in which the front end surface forming the second annular portion 52 is the orthogonal surface 53 orthogonal to the axial direction has been described, the present invention is not limited to this, and the liquid chamber shape of the cushion chamber 3 is, for example, illustrated in FIG. As shown in the comparative example of FIG. 7, it may be composed of only one annular portion.
However, in order to more suitably suppress the occurrence of cavitation when the hydraulic oil pressure drops in the front chamber 2, the cushion chamber 3 is provided on the first annular portion 51 and on the front side of the first annular portion 51. It is preferable that the second annular portion 52 has a large volume. Moreover, you may comprise the front end surface which forms the 2nd ring part 52 by an inclined surface like the form shown in the comparative example of FIG. 7, for example. However, in order to more suitably suppress cavitation toward the front liner 40 having a bearing function, the front end surface forming the second annular portion 52 is preferably an orthogonal surface 53 orthogonal to the axial direction. .
DESCRIPTION OF SYMBOLS 1 Hydraulic type impact device 2 Front chamber 3 Cushion chamber 4 Front chamber port 5 Front chamber passage 6 Front head 7 Back head 8 Rear chamber 9 Switching valve mechanism 10 Cylinder 20 Piston 21, 22 Large diameter portion 23, 24 Small diameter portion 25 For control Groove portion 26 Conical surface 27 Orthogonal surface 30 Front chamber liner 32 Seal retainer 40 Front liner 41 Brim portion 42 Bearing portion 45 Drain port 46 First end surface groove (first radial communication path)
47 Second end face groove (second radial communication path)
48 Slit (Axial communication path)
49 Drain passage 50 Rear liner 51 First annular portion 52 Second annular portion 53 Orthogonal surface 54 Small-diameter portion 55 Extension portion 56 Outer surface side annular groove 57 Inner surface side annular groove 58 Through hole 59 Conical surface 62 Column portion 63 Rear liner (front)
80 Rear chamber liner 81 Rear chamber defining portion 82 Bearing portion 83 Seal retainer portion 84 Drain communication hole 85 Rear chamber passage 91 High pressure circuit 92 Low pressure circuit
A hydraulic striking device for striking a striking rod by advancing the piston fitted in the cylinder back and forth,
A front chamber and a rear chamber defined between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder and spaced apart from each other; and when the piston moves forward, the front chamber is switched to a low pressure circuit. A switching valve mechanism for supplying and discharging hydraulic oil so that the forward and backward movements are repeated,
The front chamber has a front chamber liner fitted to the inner surface of the cylinder, and the front chamber liner is provided with a liquid chamber space communicating with the front chamber and filled with hydraulic oil as a cushion chamber. And
The cushion chamber has a second drain circuit that is provided separately from a drain circuit that guides hydraulic oil that passes through the liner bearing portion of the liner for the front chamber to a low-pressure circuit and passes through a portion other than the liner bearing portion. A hydraulic striking device.
The second drain circuit always communicates the hydraulic oil in the cushion chamber to the low-pressure circuit through one or a plurality of communication holes that pass through locations other than the liner bearing portion.
The total passage area of the one or more communication holes is set to an area within a predetermined range defined in the following (Formula 1) with respect to the clearance amount of the liner bearing portion. The hydraulic striking device according to 1.
The front chamber liner, as the one or a plurality of communication holes, communicates with the cushion chamber and is spaced apart in the circumferential direction and formed through the radial direction, and the radial communication passage. An axial communication path comprising a slit formed along the axial direction on the outer peripheral surface of the front chamber liner so as to communicate with the radial communication path according to the position of
A drain port communicating with the axial communication path is formed between the outer peripheral surface on the front end side of the front chamber liner and the inner peripheral surface of the cylinder, and the drain port is always communicated with the low pressure circuit. Is connected to the low-pressure port,
The second drain circuit is always in communication with the low-pressure circuit through the hydraulic fluid in the cushion chamber through the radial communication path, the axial communication path, and the drain port in this order. The hydraulic striking device according to claim 1 or 2.
The front chamber has a front chamber liner fitted to the inner surface of the cylinder in front of the front chamber, and the front chamber liner includes a front liner and a rear liner that are divided into two parts in the axial direction. Configured,
The front liner is made of a copper alloy and is a bearing member that supports sliding of the piston, and the rear liner is made of an alloy having higher mechanical strength than the front liner. apparatus.
There is a front chamber port formed in an annular shape on the inner surface of the cylinder so as to face the outer peripheral surface on the rear side of the rear liner, and high and low pressures of hydraulic fluid in the front chamber can be communicated with the front chamber port. The front chamber passage to be switched is connected,
The rear liner extends to a position facing the front chamber port, and a plurality of through holes spaced in the circumferential direction are formed through the surface facing the front chamber port in a radial direction. The hydraulic striking device according to claim 4.
The cushion chamber has a first annular part on the rear end side and a second annular part formed adjacent to the front of the first annular part and having a larger diameter than the first annular part. A hydraulic striking device characterized by that.
The hydraulic striking device according to claim 6, wherein an end face on the front side forming the second annular portion is an orthogonal surface orthogonal to the axial direction.
PCT/JP2015/000409 2014-01-31 2015-01-30 Hydraulic hammering device WO2015115106A1 (en)
JP2015559827A JP6438897B2 (en) 2014-01-31 2015-01-30 Hydraulic striking device
KR1020167014347A KR20160118210A (en) 2014-01-31 2015-01-30 Hydraulic hammering device
CN201580004614.XA CN105916633B (en) 2014-01-31 2015-01-30 Fluid pressure type percussion mechanism
EP15743909.2A EP3100828A4 (en) 2014-01-31 2015-01-30 Hydraulic hammering device
US15/113,664 US10493610B2 (en) 2014-01-31 2015-01-30 Hydraulic hammering device
WO2015115106A1 true WO2015115106A1 (en) 2015-08-06
JPS57174594A (en) * 1981-04-22 1982-10-27 Furukawa Kogyo Kk Strike mechanism of liquid pressure type rock drilling machine
JPS5871082A (en) * 1981-07-17 1983-04-27 Montabert Ets Impact device with sealing device between liquid working medium and external medium
JPH09109064A (en) * 1995-10-16 1997-04-28 Furukawa Co Ltd Cushioning mechanism for hydraulic striking device
JPH116383A (en) * 1997-06-19 1999-01-12 Furukawa Co Ltd Rock drill of the striking force control mechanism
US7419015B2 (en) * 2003-01-03 2008-09-02 Sandvik Mining And Construction Oy Rock drilling machine and axial bearing
JP2012509199A (en) * 2008-11-20 2012-04-19 サンドビク マイニング アンド コンストラクション オサケ ユキチュアＳａｎｄｖｉｋ Ｍｉｎｉｎｇ Ａｎｄ Ｃｏｎｓｔｒｕｃｔｉｏｎ Ｏｙ Jackhammer and axial bearing module
DE1281370B (en) 1963-09-06 1968-10-24 Krupp Gmbh Schlaggeraet back and forth movement with hydraulic piston
GB1396307A (en) * 1971-05-11 1975-06-04 Af Hydraulics Hydraulic percussive implement
ES469097A1 (en) * 1978-03-31 1980-06-16 Crespo Jose T G Hydraulic apparatus for impact
DE4027021A1 (en) * 1990-08-27 1992-03-05 Krupp Maschinentechnik , The anchor hole drilling hydraulically operated schlagdrehbohrvorrichtung particular
DE4028595C2 (en) * 1990-09-08 1993-08-05 Krupp Maschinentechnik Gmbh, 4300 Essen, De
JP3817617B2 (en) * 1999-05-10 2006-09-06 ヤマモトロックマシン株式会社 Drilling device
JP4488694B2 (en) * 2003-06-25 2010-06-23 甲南電機株式会社 Hydraulic striking device
JP2005177899A (en) 2003-12-17 2005-07-07 Konan Electric Co Ltd Hydraulic hammering device
SE527698C2 (en) * 2004-10-07 2006-05-16 Atlas Copco Rock Drills Ab Rock drilling equipment
SE528650C2 (en) * 2005-05-23 2007-01-09 Atlas Copco Rock Drills Ab Impulse generator and method for generating impulse
PL230867B1 (en) * 2007-02-01 2018-12-31 J.H. Fletcher & Co. Fail-safe striking assembly for the valveless percussive action drilling unit
SE534794C2 (en) 2010-04-01 2011-12-27 Atlas Copco Rock Drills Ab Hydraulic striking device, piston guide, and drilling rig
CN103097654A (en) * 2010-09-10 2013-05-08 澳大利亚凿岩设备制造与维护有限公司 Improved rock drill
FI123187B (en) * 2011-06-07 2012-12-14 Sandvik Mining & Constr Oy Rock-breaker impactor, method for controlling impactor
SE538675C2 (en) * 2012-02-17 2016-10-18 Construction Tools Pc Ab Spool valve, shock device and method
KR101373544B1 (en) * 2012-07-03 2014-03-25 이일재 Hitting body for hydraulic percussion apparatus
See also references of EP3100828A4 *
US10493610B2 (en) 2019-12-03
EP1559515A2 (en) 2005-08-03 Hydraulic hammer
CA2285971A1 (en) 1998-10-01 Arrangement in rock drill and method of controlling rock drilling
KR100847226B1 (en) 2008-07-17 Responsive type damper for speed and impact absorbing damper device
US4623027A (en) 1986-11-18 Unsegmented rotary rock bit structure and hydraulic fitting
FI66460B (en) 1984-06-29 Tryckmediedriven slagapparat
US8776964B2 (en) 2014-07-15 Gas cylinder actuator with overtravel safety device
US20090095585A1 (en) 2009-04-16 Vehicle damper
Ref document number: 15743909
Ref document number: 2015559827
Ref document number: 20167014347
2016-06-28 REEP Request for entry into the european phase
Ref document number: 2015743909
Ref document number: 15113664