WO2020120874A1 - Appareil hydraulique à percussions équipé d'un dispositif d'étanchéité - Google Patents
Appareil hydraulique à percussions équipé d'un dispositif d'étanchéité Download PDFInfo
- Publication number
- WO2020120874A1 WO2020120874A1 PCT/FR2019/052903 FR2019052903W WO2020120874A1 WO 2020120874 A1 WO2020120874 A1 WO 2020120874A1 FR 2019052903 W FR2019052903 W FR 2019052903W WO 2020120874 A1 WO2020120874 A1 WO 2020120874A1
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- WO
- WIPO (PCT)
- Prior art keywords
- annular
- fluid passage
- sealing
- external
- balancing channel
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/06—Means for driving the impulse member
- B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2222/00—Materials of the tool or the workpiece
- B25D2222/54—Plastics
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2222/00—Materials of the tool or the workpiece
- B25D2222/54—Plastics
- B25D2222/57—Elastomers, e.g. rubber
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/345—Use of o-rings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/365—Use of seals
Definitions
- TITLE Hydraulic percussion device fitted with a sealing device
- the present invention relates to a hydraulic percussion device.
- Hydraulic percussion devices of the rock breaker or perforator type, are generally equipped with a guide body comprising a bore, and a striking piston mounted to slide inside the bore and arranged to be driven in translation in an alternative manner by an incompressible fluid.
- the impact piston can optionally also be driven in rotation about its longitudinal axis.
- the guide body comprises an annular retaining groove, coaxial with the piston of strikes and opens into the bore, in which a sealing device is mounted.
- a first type of known sealing device consists of a one-piece sealing gasket having a U-shaped section and thus comprising a first internal sealing lip intended to cooperate with the external surface of the striking piston in order to ensure dynamic sealing. between the seal and the moving impact piston, and an external sealing lip intended to cooperate with the bottom of the annular retaining groove of the guide body in order to ensure a static seal between the seal and the guide body.
- Such a sealing device provides satisfactory sealing at low translation speed and low impact frequency of the impact piston.
- a second type of known sealing device consists of a sealing device comprising: - an internal sealing ring comprising:
- annular protection portion offset axially with respect to the internal sealing portion, the annular protection portion being delimited internally by at least one converging protection surface, the converging protection surface being annular and converging in the direction of the lip d sealing,
- annular groove opening towards the inside of the internal sealing ring, the annular groove being disposed between the sealing lip and the converging protective surface, and
- an external sealing element separate from the internal sealing ring and mounted around the internal sealing ring, the external sealing element being annular and intended to bear in leaktight manner in the bottom of the groove ring retainer.
- Such a sealing device ensures satisfactory sealing at high speed of translation and high frequency of striking of the striking piston, and low friction on the striking piston, therefore low heating by friction of the sealing lip.
- the configuration of the converging protective surface makes it possible to form, with the external surface of the striking piston, a progressive annular nozzle adapted to progressively reduce the thickness and the flow rate of the incompressible fluid flowing in the direction of the lip d sealing, and therefore to reduce the amplitude of the pressure peaks generated by very rapid reciprocating movements of the incompressible fluid controlling the movements of the striking piston.
- the presence of the annular groove between the sealing lip and the converging protective surface makes it possible to reduce the speed of arrival of the incompressible fluid on the sealing lip due to the increase in the fluid passage surface. incompressible, which further dampens residual pressure peaks.
- the configuration of the internal sealing ring of the second type of aforementioned sealing device makes it possible to greatly reduce the amplitude of the pressure peaks mentioned above, and therefore to avoid rupture of the sealing lip. Therefore, the second type of aforementioned sealing device has increased reliability.
- a problem encountered with the second type of aforementioned sealing device resides in the fact that potential radial vibrations of the striking piston are liable to generate a rise in pressure in the annular groove situated between the sealing lip and the surface. of convergent protection.
- the present invention aims to remedy all or part of these drawbacks.
- the technical problem underlying the invention therefore consists in providing a hydraulic percussion device comprising a sealing device which is simple, economical and reliable in structure.
- the present invention relates to a hydraulic percussion device, comprising:
- a guide body comprising a bore and an annular retaining groove formed on the guide body and opening into the bore
- a striking piston mounted to slide inside the bore in a direction of movement and arranged to be driven alternately by an incompressible fluid
- first fluid passage being located near a first side wall of the annular retaining groove and fluidly connecting the annular retaining groove to an incompressible fluid circuit associated with the reciprocating movement of the impact piston
- second passage of fluid fluidly connecting the annular retaining groove to a compressible fluid circuit and being located near a second side wall of the annular retaining groove which is opposite to the first side wall
- a sealing device mounted in the annular retaining groove so as to seal between the first fluid passage and the second fluid passage, the sealing device comprising:
- an internal sealing ring comprising:
- annular protection portion offset axially with respect to the internal sealing portion, the annular protection portion being delimited internally by at least one converging protection surface, the converging protection surface being annular and converging in the direction of the lip d sealing,
- annular groove opening towards the inside of the internal sealing ring, the annular groove being disposed between the sealing lip and the converging protective surface, and
- At least one balancing channel comprising a first end opening into the annular groove and a second end opening into an outer surface of the annular protective portion, the at least one balancing channel being configured to fluidly connect the annular groove at the first fluid passage when the pressure in the first fluid passage is greater than the pressure in the second fluid passage, and
- an external sealing element separate from the internal sealing ring and mounted around the internal sealing ring, the external sealing element being annular and intended to bear in leaktight manner in the bottom of the groove ring retainer.
- the presence of the at least one balancing channel allows, when the reciprocating movement of the striking piston is active and in the event of violent radial movement of the striking piston, to fluidly connect the annular groove to the first passage of fluid and therefore to the incompressible fluid circuit of the percussion hydraulic device.
- the pressure in the annular groove then remains close to the pressure of the incompressible fluid circuit which is not subjected to the radial vibrations of the striking piston.
- the presence of the at least one balancing channel makes it possible to maintain the effectiveness of the annular protection portion against pressure peaks linked to very rapid alternating movements of the incompressible fluid, and therefore maintain the reliability of the sealing device, including in the event of violent radial movement of the striking piston.
- the hydraulic percussion device may also have one or more of the following characteristics, taken alone or in combination.
- the at least one balancing channel is provided on the annular protection portion.
- the second end of the at least one balancing channel is oriented towards the first side wall of the annular retaining groove.
- the annular protection portion comprises an annular balancing groove formed on an external surface of the annular protection portion, the second end of the at least one balancing channel opening into the groove ring balancing.
- the annular balancing groove is substantially coaxial with the striking piston.
- the second end of the at least one balancing channel opens into an end surface of the internal sealing ring facing the first side wall of the annular retaining groove.
- the at least one balancing channel has a diameter of between 0.4 and 1.2 mm, and for example around 0.7 mm.
- each of the first and second fluid passages is annular.
- the compressible fluid circuit is a circuit of air lubricated under pressure configured to cool and lubricate the mechanical members of the hydraulic percussion device.
- the hydraulic percussion device is configured so that, when the pressure in the second fluid passage is greater than the pressure in the first fluid passage, that is to say say when the reciprocating movement of the striking piston is stopped, the sealing device is moved in contact with the first side wall of the annular retaining groove and the second end of the at least one balancing channel is closed by the 'external sealing element or by the first side wall.
- the internal sealing ring and the external sealing element are pushed by the pressure of the compressible fluid towards the first side wall of the annular retaining groove receiving the sealing device, and the second end of the at least one balancing channel is closed by the external sealing element or by the first side wall.
- the external sealing element exerts a radial force mainly on the annular protection portion, and the intersection of the annular groove with the annular protection portion then becomes a sealing edge, so that the annular groove located between the internal sealing portion and the annular protection portion is no longer in fluid communication with the incompressible fluid circuit. Consequently, the compressible and incompressible fluid circuits are again well separated.
- the hydraulic percussion device is configured such that, when the pressure in the first fluid passage is greater than the pressure in the second fluid passage, that is to say mainly say when the reciprocating movement of the striking piston is activated, the sealing device is moved in contact with the second side wall of the annular retaining groove and the second end of the at least one balancing channel is released from so as to fluidly connect the annular groove to the first passage of fluid via the at least one balancing channel.
- the sealing device allows a flow of incompressible fluid from the annular groove and through the at least one balancing channel and an evacuation of said incompressible fluid through the second end of the at least one balancing channel.
- the incompressible fluid When the reciprocating movement of the striking piston is activated (that is to say when the percussion of the hydraulic device is activated), the incompressible fluid is under a pressure higher than that of the compressible fluid.
- the internal sealing ring and the external sealing element are therefore pushed by the incompressible fluid in contact with the second side wall of the annular retaining groove. In this normal working position, the second end of the at least one balancing channel is released and the sealing device effectively separates the incompressible fluid from the compressible fluid.
- the sealing lip is protected, by the annular protection portion, from pressure peaks linked to very rapid reciprocating movements of the incompressible fluid, and the sealing device, and in particular the annular protection portion, is protected some pics pressures generated by the potential radial movement of the impact piston by the at least one balancing channel.
- the external sealing element is displaceable and / or deformable between a shutter configuration in which the external sealing element closes the second end of the at least one channel balancing, and a release configuration in which the external sealing element releases the second end of the at least one balancing channel.
- the annular protection portion is arranged to delimit an annular flow passage with the impact piston at least when the pressure in the first fluid passage is greater than the pressure in the second passage of fluid.
- the sealing lip projects radially inwards relative to the annular protective portion.
- the external sealing element is arranged to exert a compressive force on the internal sealing portion at least when the pressure in the first fluid passage is greater than the pressure in the second fluid passage.
- the external sealing element is arranged to exert a compressive force on the annular protective portion at least when the pressure in the second fluid passage is greater than the pressure in the first fluid passage.
- the annular groove is delimited by the sealing lip and the annular protection portion.
- the converging protective surface extends from one end of the internal sealing ring facing the first side wall of the annular retaining groove.
- the converging protective surface has an apex angle of between 10 and 40 °. As a result, the axial components of the hydraulic forces resulting from the pressure peaks remain weak on the converging protective surface.
- the annular protection portion extends longitudinally over more than half the length of the internal sealing ring. According to one embodiment of the invention, the converging protective surface extends longitudinally over at least 20% of the length of the internal sealing ring.
- the annular protective portion is internally further delimited by a divergent protective surface which is annular and which diverges in the direction of the sealing lip, the divergent protective surface being disposed between the converging protective surface and the sealing lip, and delimiting at least partially the annular groove.
- the first end of the at least one balancing channel opens into the divergent protective surface.
- the divergent protective surface has an apex angle less than 140 °, and for example less than 90 °.
- the divergent protective surface has a radial height of at least 5/10 th of a millimeter.
- the converging protection surface and / or the diverging protection surface are substantially frustoconical.
- the annular protection portion is internally further delimited by a substantially cylindrical intermediate protection surface and disposed between the converging protection surface and the annular groove.
- a substantially cylindrical intermediate protection surface and disposed between the converging protection surface and the annular groove.
- the intermediate protective surface is disposed between the converging protective surface and the divergent protective surface.
- the intermediate protective surface extends in the extension of the converging protective surface.
- the divergent protective surface extends in the extension of the intermediate protective surface.
- Such an arrangement of the divergent protective surface makes it possible to transform the purely axial component of the speed of the incompressible fluid coming from the intermediate protective surface into an axial component and a radial component, and therefore further reduce the speed of arrival of the incompressible fluid on the sealing lip.
- At least one of the convergent, intermediate and divergent protective surfaces extends substantially coaxially to the longitudinal axis of the internal sealing ring.
- the converging, intermediate and diverging protective surfaces extend substantially coaxially to the longitudinal axis of the internal sealing ring.
- the external sealing element comprises an annular bearing portion which is mounted around the internal sealing portion, and which bears in a sealed manner in the bottom of the groove of ring retainer.
- the external sealing element comprises an annular retaining portion which is mounted around the annular protective portion, and which bears in leaktight manner in the bottom of the annular retaining groove .
- the annular holding portion comes integrally with the annular bearing portion.
- the annular holding portion and the annular bearing portion are made in one piece.
- the annular holding portion is arranged to exert a compression force on the annular protective portion at least when the pressure in the second fluid passage is greater than the pressure in the first fluid passage.
- the holding portion is offset axially from the annular bearing portion.
- the annular bearing portion and the annular holding portion respectively comprise a first and a second internal bearing surface
- the internal sealing portion and the annular protective portion respectively comprise a first and a second external support surfaces arranged to cooperate respectively with the first and second internal support surfaces
- the annular balancing groove is formed on the second external bearing surface of the annular protective portion.
- the second external bearing surface formed on the annular protective portion is substantially cylindrical and extends substantially parallel to the longitudinal axis of the internal sealing ring.
- the second external bearing surface formed on the annular protection portion is concave.
- the first and second internal bearing surfaces are substantially cylindrical and extend substantially parallel to the longitudinal axis of the internal sealing ring.
- the first and second external bearing surfaces are substantially cylindrical and extend substantially parallel to the longitudinal axis of the internal sealing ring.
- the first and second external bearing surfaces extend in line with one another.
- the internal sealing ring has, at each of its ends, an annular external chamfer.
- annular that is to say the edges delimited by the side walls of the retaining groove and the inner wall of the guide body, which could affect the seal between the sealing device and the striking piston.
- each annular external chamfer extends longitudinally and radially over at least 2/10 th of a millimeter.
- each annular external chamfer has a chamfer angle of between 10 and 60 ° relative to a plane perpendicular to the longitudinal axis of the internal sealing ring.
- the external sealing element comprises, at each of its ends, an annular internal chamfer.
- each annular internal chamfer has a chamfer angle between 10 and 60 ° relative to a plane perpendicular to the longitudinal axis of the internal sealing ring.
- the at least one balancing channel is inclined relative to the longitudinal axis of the internal sealing ring.
- the at least one balancing channel extends substantially parallel to the longitudinal axis of the internal sealing ring.
- the internal sealing ring comprises a plurality of balancing channels.
- the sealing lip comprises a sealing edge intended to cooperate in sealed manner with the external surface of the striking piston.
- the intermediate protective surface comprises an internal diameter between a minimum value corresponding to the internal diameter of the sealing lip increased by 1/10 th of a millimeter and a maximum value corresponding to the external diameter of the striking piston increased by 1 millimeter.
- the internal diameter of the internal sealing ring, at the end face of the annular protective portion facing the first side wall of the annular retaining groove, is greater or equal to the diameter of the bore, at the end of the first fluid passage facing the internal sealing ring.
- the sealing device is configured to seal between the first fluid passage and the second fluid passage regardless of the operating conditions of the hydraulic percussion device, and in particularly as well when the second end of the at least balancing channel is closed as when the second end of the at least balancing channel is released, that is to say as well when the pressure in the second fluid passage is greater than the pressure in the first fluid passage than when the pressure in the first fluid passage is greater than the pressure in the second fluid passage.
- the sealing device is configured to prevent the compressible fluid coming from the second fluid passage from entering the first fluid passage when the pressure in the second fluid passage is greater than the pressure in the first fluid passage.
- the sealing device is configured to prevent the compressible fluid from the second fluid passage from flowing through the second end of the at least one balancing channel when the pressure in the second fluid passage is higher than the pressure in the first fluid passage.
- the annular protection portion comprises at least one radial notch opening into the end face of the internal sealing ring facing the first side wall of the annular retaining groove.
- the annular protection portion comprises at least one radial notch opening into the end face of the internal sealing ring facing the second side wall of the annular retaining groove.
- the at least one balancing channel opens out only at its first and second ends.
- the at least one balancing channel is integrally formed in the material of the internal sealing ring.
- the at least one balancing channel is generally tubular.
- the hydraulic percussion device is configured so that:
- the sealing device when the pressure in the second fluid passage is higher than the pressure in the first fluid passage, the sealing device is moved to the contact of the first side wall of the annular retaining groove and the external sealing element is displaced and / or deformed in the closure configuration in which the external sealing element closes the second end of the at least a balancing channel;
- the sealing device when the pressure in the first fluid passage is greater than the pressure in the second fluid passage, the sealing device is moved in contact with the second side wall of the annular retaining groove and the external sealing element is moved and / or deformed in the release configuration in which the external sealing element releases the second end of the at least one balancing channel so as to fluidly connect the annular groove to the first passage of fluid via the at least one balancing channel.
- the external sealing element is axially displaceable between the shutter configuration and the release configuration.
- the second end of the at least one balancing channel opens into an external circumferential surface of the annular protective portion.
- Figure 1 is a partial sectional view of a hydraulic percussion device according to a first embodiment of the invention and which is equipped with a sealing device shown in a percussion configuration.
- Figure 2 is a partial sectional view of the hydraulic percussion device of Figure 1 showing the sealing device in a percussion stop configuration.
- Figure 3 is a sectional view of a sealing device according to a second embodiment of the invention and which is shown in a percussion configuration.
- Figure 4 is a sectional view of the sealing device of Figure 3 in a percussion stop configuration.
- Figure 5 is a sectional view of a sealing device according to a third embodiment of the invention and which is shown in a percussion configuration.
- Figures 1 and 2 show a hydraulic percussion device 2 equipped with a guide body 3 comprising a bore 4 and an annular retaining groove 5 opening into the bore 4, and a striking piston 6 of cylindrical shape mounted sliding inside the bore 4 in a direction of movement D and arranged to be driven in translation alternately by an incompressible fluid, such as hydraulic oil.
- an incompressible fluid such as hydraulic oil.
- the hydraulic percussion device 2 further comprises a first fluid passage 7 and a second fluid passage 8 which are annular and coaxial, and which are located on either side of the annular retaining groove 5.
- Each of the first and second fluid passages 7, 8 is delimited between the guide body 3 and the striking piston 6.
- the first fluid passage 7 is located near a first side wall 9 of the annular retaining groove 5 and fluidly connects the annular retaining groove 5 to an incompressible fluid circuit associated with the reciprocating movement of the striking piston 6, while that the second fluid passage 8 fluidly connects the annular retaining groove 5 to a compressible fluid circuit and is located near a second side wall 11 of the annular retaining groove 5 which is opposite to the first side wall 9.
- the compressible fluid circuit can for example be a circuit of air lubricated under pressure configured to cool and / or lubricate mechanical members of the hydraulic percussion device 2.
- the hydraulic percussion device 2 further comprises a sealing device 12 mounted in the annular retaining groove 5 so as to seal between the first fluid passage 7 and the second fluid passage 8, and more particularly so preventing an incompressible fluid passage from the first fluid passage 7 towards the second fluid passage 8, and so as to prevent a compressible fluid passage from the second fluid passage 8 towards the first fluid passage 7.
- the sealing device 12 comprises an internal sealing ring 13.
- the internal sealing ring 13 can be made of hard plastic, for example based on PTFE, PEEK, PU.
- the internal sealing ring 13 comprises an annular internal sealing portion 14 which is provided with an annular sealing lip 15 intended to cooperate in leaktight manner with the external surface of the striking piston 6.
- the lip of sealing 15 comprises a sealing edge 16 intended to cooperate sealingly with the external surface of the striking piston 6.
- the internal sealing ring 13 further comprises an annular protective portion 17 offset axially with respect to the internal sealing portion 14.
- the internal sealing ring 13 is shaped so that the sealing lip 15 is substantially at the same level or protrudes radially inwards relative to the annular protection portion 17.
- the annular protection portion 17 is arranged to delimit an annular flow passage P with the striking piston 6 when the reciprocating movement of the striking piston 6 is activated.
- the annular protection portion 17 is delimited internally at least in part by a converging protection surface 18, an intermediate protection surface 19 and a divergent protection surface 20 which extend substantially coaxially to the longitudinal axis A of the ring d internal seal 13.
- the converging protective surface 18 extends from one end of the internal sealing ring 13, and more particularly from an end face 21 of the annular protective portion 17 opposite the portion of internal sealing 14.
- the converging protective surface 18 is advantageously frustoconical and converges in the direction of the sealing lip 15.
- the converging protective surface 18 has for example an apex angle of between 2 and 40 °.
- the converging protective surface 18 may for example further extend longitudinally over at least 20% of the length of the internal sealing ring 13.
- the intermediate protective surface 19 extends in the extension of the converging protective surface 18 in the direction of the sealing lip 15.
- the intermediate protective surface 19 is substantially cylindrical, and preferably has an internal diameter between a value minimum corresponding to the internal diameter of the sealing lip 15 increased by 1/10 th of a millimeter and a maximum value corresponding to the external diameter of the striking piston 6 increased by 1 millimeter.
- the divergent protection surface 20 extends in the extension of the intermediate protection surface 19.
- the divergent protection surface 20 is frustoconical and diverges in the direction of the sealing lip 15.
- the divergent protective surface 20 has a radial height of at least 5/10 th of a millimeter.
- the divergent protective surface 20 has an apex angle less than 140 °.
- the internal sealing ring 13 also comprises an annular groove 22 facing the striking piston 6, the annular groove 22 being delimited by the sealing lip 15 and the divergent protective surface 20.
- the annular groove 22 is advantageously substantially coaxial with the striking piston 6.
- the internal sealing ring 13 comprises, at each of its ends, an annular external chamfer 23, 24.
- Each annular external chamfer 23, 24 may for example extend longitudinally and radially over at least 2 / 10ths of a millimeter.
- each annular external chamfer 23, 24 has a chamfer angle of between 10 and 60 ° relative to a plane perpendicular to the longitudinal axis A of the internal sealing ring 13.
- the internal diameter of the internal sealing ring 13, at the end face 21 of the annular protective portion 17 opposite the internal sealing portion 14, is greater than or equal to the diameter of the bore 5, at the end of the first fluid passage 7 facing the internal sealing ring 13.
- the radial height of the internal sealing ring 13, at the end face 21 of the annular protective portion 17, is greater than or equal to the radial height of the end of the first fluid passage 7 facing the internal sealing ring 13.
- the internal sealing ring 13 also includes a balancing channel 25 or more balancing channels 25 provided on the annular protective portion 17.
- the or each balancing channel 25 comprises a first end opening into the groove annular 22, and more particularly in the divergent protective surface 20, and a second end opening into an outer surface of the annular protective portion 17.
- the second end of the or each balancing channel 25 is oriented towards the first side wall 9 of the annular retaining groove 5.
- the or each balancing channel 25 extends substantially parallel to the longitudinal axis A of the internal sealing ring 13, and the second end of the or each balancing channel 25 opens into the end face 21 of the annular protection portion 17.
- the sealing device 2 further comprises an external sealing element 26 separate from the internal sealing ring 13 and mounted around the internal sealing ring 13.
- the external sealing element 26 is annular and takes sealingly pressing in the bottom of the annular retaining groove 5.
- the external sealing element 26 can for example be made of elastomer.
- the external sealing element 26 comprises an annular bearing portion 26.1 which is mounted around the internal sealing portion 14 and which bears in a sealed manner in the bottom of the annular retaining groove 5, and an annular retaining portion 26.2 which is mounted around the annular protective portion 17 and which also bears sealingly in the bottom of the annular retaining groove 5.
- the retaining portion annular 26.2 is thus offset axially relative to the annular bearing portion 26.1.
- the annular bearing portion 26.1 is arranged to exert a compressive force on the internal sealing portion 14 at least when the pressure in the first fluid passage 7 is greater than the pressure in the second fluid passage 8
- the annular holding portion 26.2 is arranged to exert a compressive force on the annular protective portion 17 at least when the pressure in the second fluid passage 8 is greater than the pressure in the first fluid passage 7.
- the annular bearing portion 26.1 and the annular holding portion 26.2 respectively comprise a first and a second internal bearing surface 27, 28, and the internal sealing portion 14 and the annular protective portion 17 respectively comprise a first and a second external support surface 29, 31 arranged to cooperate respectively with the first and second internal support surface 27, 28.
- the first external support surface 29 formed on the internal sealing portion 14 is substantially cylindrical and extends substantially parallel to the longitudinal axis A of the internal sealing ring 13, while the second external bearing surface 31 formed on the annular protective portion 17 is concave.
- the hydraulic percussion device 2 is more particularly configured so that, when the pressure in the first fluid passage 7 is greater than the pressure in the second fluid passage 8, that is to say when the reciprocating movement of the striking piston 6 is activated, the internal sealing ring 13 and the external sealing element 26 are displaced by the pressure of the incompressible fluid in contact with the second side wall 11 of the annular retaining groove 5 and the second end of or each balancing channel 25 is released so as to fluidly connect the annular groove 22 to the first passage of fluid 7 via the or each balancing channel 25.
- the sealing device when the second end of the or each balancing channel 25 is released, the sealing device
- the sealing lip 15 is protected, by the annular protective portion 17, from pressure peaks linked to the very rapid reciprocating movements of the incompressible fluid, and the protective portion annular 17 is protected from pressure peaks generated by the potential radial movement of the striking piston 6 by the or each balancing channel 25.
- the presence of the or each balancing channel 25 makes it possible to maintain the effectiveness of the annular protective portion 17 against pressure peaks linked to very rapid alternating movements of the incompressible fluid, and therefore to maintain the reliability of the device. seal 12, including in the event of violent radial movement of the striking piston 6.
- the hydraulic percussion device 2 is further configured so that when the pressure in the second fluid passage 8 is greater than the pressure in the first fluid passage 7, i.e. mainly when the movement reciprocating of the striking piston 6 is stopped, the internal sealing ring
- annular holding portion 26.2 exerts a compressive force on the annular protective portion 17 when the pressure in the second fluid passage 8 is greater than the pressure in the first fluid passage 7, the intersection of the annular groove 22 with the intermediate protective surface 19 then becomes a sealing edge, so that the annular groove 22 is fluidly isolated from the incompressible fluid circuit, which ensures separation of the compressible and incompressible fluid circuits even in case of lifting of the sealing lip 15.
- Figures 3 and 4 show a sealing device 12 according to a second embodiment of the invention which differs from the first embodiment shown in Figures 1 and 2 essentially in that the or each balancing channel 25 is inclined relative to the longitudinal axis A of the internal sealing ring 13, and in that the external sealing element 26 is axially displaceable between a closure configuration in which the external sealing element 26 closes the second end of the or each balancing channel 25, and a release configuration in which the external sealing element 26 releases the second end of the or each balancing channel 25.
- the second end of the or each balancing channel 25 opens into an external circumferential surface of the annular protective portion 17, and more particularly into the second external bearing surface 31 of the annular protection portion 17.
- first and second external bearing surfaces 29, 31 are substantially cylindrical and extend substantially parallel to the longitudinal axis A of the internal sealing ring 13 and in line with one another.
- each annular internal chamfer 32, 33 can for example extend longitudinally and radially over at least 2/10 th of a millimeter. According to one embodiment of the invention, each annular internal chamfer 32, 33 has a chamfer angle of between 10 and 60 ° relative to a plane perpendicular to the longitudinal axis A of the internal sealing ring 13.
- annular protective portion 17 may also comprise at least one radial notch 34 opening into the end face 21 of the internal sealing ring 13 and at least one radial notch 35 opening into the end face 36 of the internal sealing ring 13 facing the second side wall 11 of the annular retaining groove 5.
- any overpressures generated in the annular groove 22 by radial movements of the striking piston 6 are evacuated via the or each balancing channel 25, so that the pressure in the annular groove 22 then remains close to the incompressible fluid circuit pressure.
- the axial pressure fluctuations originating from the first fluid passage 7 do not flow directly into the or each balancing channel 25, but flow beforehand along the end face 21 of the annular protective portion 17 and of the second external bearing surface 31 and are therefore attenuated by the end face 21 and the second external bearing surface 31.
- These pressure fluctuations axial are also attenuated due to the inclined configuration of the or each balancing channel 25.
- the compressible fluid from the second fluid passage 8 can, by leaking from the sealing lip 15, flow into the annular groove 22.
- the intermediate protective surface 19 then seals on the striking piston 6, because the external sealing element 26 presses on the second external bearing surface 31 of the annular protective portion 17 and makes it pivot towards the striking piston 6.
- the second end of the or each balancing channel 25 being obstructed by the external sealing element 26, the risk of leakage of the compressible fluid in the first fluid passage 7 is thus substantially reduced.
- the material of the internal sealing ring 13 can be very hard, the sealing at the second end of the or each balancing channel 25 is guaranteed because the external sealing element 26 is generally made of a softer material than the material of the internal sealing ring 13.
- FIG. 5 shows a sealing device 12 according to a third embodiment of the invention which differs from the second embodiment shown in Figures 3 and 4 essentially in that the annular protective portion 17 has a balancing groove annular 37 formed an outer surface of the annular protective portion 17, and in that the second end of the or each balancing channel 25 opens into the annular balancing groove 37.
- the annular balancing groove 37 is substantially coaxial with the striking piston 6, and is formed on the second external bearing surface 31 of the annular protective portion 17.
- annular balancing groove 37 facilitates the machining of the or each balancing channel 25 as well as the evacuation of the incompressible fluid in the direction of the first fluid passage 7 when the reciprocating movement of the striking piston 6 is active and in the event of a violent radial movement of the striking piston 6.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US17/294,240 US20210339371A1 (en) | 2018-12-14 | 2019-12-03 | Hydraulic percussion apparatus equipped with a sealing device |
AU2019398836A AU2019398836A1 (en) | 2018-12-14 | 2019-12-03 | Hydraulic percussion apparatus equipped with a sealing device |
CA3118204A CA3118204A1 (fr) | 2018-12-14 | 2019-12-03 | Appareil hydraulique a percussions equipe d'un dispositif d'etancheite |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1872902 | 2018-12-14 | ||
FR1872902A FR3089838B1 (fr) | 2018-12-14 | 2018-12-14 | Appareil hydraulique à percussions équipé d’un dispositif d’étanchéité |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2020120874A1 true WO2020120874A1 (fr) | 2020-06-18 |
Family
ID=66218253
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2019/052903 WO2020120874A1 (fr) | 2018-12-14 | 2019-12-03 | Appareil hydraulique à percussions équipé d'un dispositif d'étanchéité |
Country Status (5)
Country | Link |
---|---|
US (1) | US20210339371A1 (fr) |
AU (1) | AU2019398836A1 (fr) |
CA (1) | CA3118204A1 (fr) |
FR (1) | FR3089838B1 (fr) |
WO (1) | WO2020120874A1 (fr) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3118114A1 (fr) * | 2020-12-21 | 2022-06-24 | Repack-S | Elément d’étanchéité et Système d’étanchéité |
WO2022174041A1 (fr) * | 2021-02-12 | 2022-08-18 | Atlas Seals Inc. | Joint rotatif d'union à emboîtement |
EP4130520A1 (fr) * | 2021-08-04 | 2023-02-08 | Carl Freudenberg KG | Joint d'étanchéité et ensemble joint d'étanchéité comprenant un tel joint d'étanchéité |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0104504A1 (fr) * | 1982-09-10 | 1984-04-04 | Martin Merkel GmbH & Co. KG | Dispositif d'étanchéité à double racleur |
US4723782A (en) * | 1986-06-19 | 1988-02-09 | Busak + Luyken Gmbh & Co. | Arrangement for sealing a rod |
FR2996897A1 (fr) * | 2012-10-15 | 2014-04-18 | Montabert Roger | Dispositif d’etancheite pour appareil hydraulique a percussions, et appareil hydraulique a percussions comprenant un tel dispositif d’etancheite |
-
2018
- 2018-12-14 FR FR1872902A patent/FR3089838B1/fr not_active Expired - Fee Related
-
2019
- 2019-12-03 CA CA3118204A patent/CA3118204A1/fr active Pending
- 2019-12-03 AU AU2019398836A patent/AU2019398836A1/en not_active Abandoned
- 2019-12-03 WO PCT/FR2019/052903 patent/WO2020120874A1/fr active Application Filing
- 2019-12-03 US US17/294,240 patent/US20210339371A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0104504A1 (fr) * | 1982-09-10 | 1984-04-04 | Martin Merkel GmbH & Co. KG | Dispositif d'étanchéité à double racleur |
US4723782A (en) * | 1986-06-19 | 1988-02-09 | Busak + Luyken Gmbh & Co. | Arrangement for sealing a rod |
FR2996897A1 (fr) * | 2012-10-15 | 2014-04-18 | Montabert Roger | Dispositif d’etancheite pour appareil hydraulique a percussions, et appareil hydraulique a percussions comprenant un tel dispositif d’etancheite |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3118114A1 (fr) * | 2020-12-21 | 2022-06-24 | Repack-S | Elément d’étanchéité et Système d’étanchéité |
WO2022174041A1 (fr) * | 2021-02-12 | 2022-08-18 | Atlas Seals Inc. | Joint rotatif d'union à emboîtement |
EP4130520A1 (fr) * | 2021-08-04 | 2023-02-08 | Carl Freudenberg KG | Joint d'étanchéité et ensemble joint d'étanchéité comprenant un tel joint d'étanchéité |
Also Published As
Publication number | Publication date |
---|---|
US20210339371A1 (en) | 2021-11-04 |
FR3089838A1 (fr) | 2020-06-19 |
AU2019398836A1 (en) | 2021-05-27 |
FR3089838B1 (fr) | 2020-12-18 |
CA3118204A1 (fr) | 2020-06-18 |
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