Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
  • F03C1/00—Reciprocating-piston liquid engines
  • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
  • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
  • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
  • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
  • F03C1/00—Reciprocating-piston liquid engines
  • F03C1/26—Reciprocating-piston liquid engines adapted for special use or combined with apparatus driven thereby
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
  • F02N7/06—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of reciprocating-piston type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
  • F02N7/08—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of rotary type

Definitions

• Hydraulic transmission device that can constitute a compact hydraulic starter
• the present invention relates to a hydraulic transmission device for a machine comprising:
• a reciprocating hydraulic motor with radial pistons comprising a cam integral with a housing, a cylinder block and an internal fluid distributor disposed in the housing;
• a hydraulic pump comprising a drive member
• housing and the distributor are mounted relative rotation relative to a fixed support about an axis of rotation, while the cylinder block is fixed on said support.
• fixed support is meant here a support which is a non-rotating part of the device. This support is therefore intended to be fixed relative to the machine. It ensures the mechanical maintenance of the cylinder block, and more generally, the hydraulic motor, on the machine.
• the cylinder block is rigidly fixed on the support.
• the crankcase is the crankcase of the hydraulic motor; it houses in particular the cylinder block and the fluid distributor.
• Such devices are used in particular to serve as a starter for internal combustion engines, for example diesel engines.
• a known alternative is to use a hydraulic motor as a starter.
• Such an engine can indeed constitute an effective starter for an internal combustion engine, particularly when the internal combustion engine is used to drive a load having a large inertia: Indeed, the hydrostatic starter has a density (volume) of power very high, which allows it to be less bulky than an electric starter.
• the use of a hydrostatic engine to make a starter is also interesting because it is robust, and has a long life, allowing it to ensure a very large number of starts.
• the device 12 comprises an accumulator 14 of fluid under pressure, a pump 16, a hydraulic motor 18, and a tank 20 of fluid under atmospheric pressure.
• the accumulator 14 is connected via a duct 22 to the hydraulic motor 18 so that, in order to start the engine 10, the motor 18 is supplied with fluid under pressure.
• the fluid after having passed through the engine 18 is directed towards the tank 20 via an exhaust pipe 24.
• the casing 26 of the engine 18 is mounted in the end of the crankshaft of the heat engine 10.
• casing 26 is a rotating casing which is the output member of the motor 18.
• the casing 26 begins to rotate and in turn rotates the crankshaft of the motor 10, which starts the engine 10.
• a belt 28 which passes into outer grooves respectively formed on the housing 30 of the pump 16 and on the housing 26 of the motor 18, rotates the pump 16 and the motor 18. For this reason, when the crankshaft of the motor 10 rotates, the housing 26 of the motor 18 and the housing 30 of the pump 16 also rotate.
• the pump 16 is connected by a suction duct 32 to the tank 20, and by a filling duct 34 to the accumulator 14.
• the pump 16 is actuated (that is to say that its housing 30 is rotated). Also, when the motor 10 rotates, the pump 16 pumps the fluid into the reservoir 20 so as to fill the accumulator 14, via the conduits 32 and 34. The stopping of the filling of the accumulator is controlled by a valve 36 interposed between the accumulator 14 and the conduits 22 and 34.
• the operation of the device 12 is as follows:
• the engine 10 To start the engine 10, it causes the emptying of the accumulator 14 in the tank 20 via the engine 18.
• the passage of the pressurized fluid from the accumulator actuates the motor 18; the housing 26 of the engine 18 starts to rotate, which in turn rotates the crankshaft of the engine 10 and causes the engine 10 to start.
• the engine 10 is then in operation.
• the hydraulic starting system 12 complements an electric starting system.
• the device 12 is relatively bulky, which makes its implementation difficult on many equipment, including many engines such as the engine 10.
• Hydraulic motors require many hoses, the installation of a booster pump, and the drive of it by an output shaft of the engine or via an additional electric drive.
• Hydraulic motors require many hoses, the installation of a booster pump, and the drive of it by an output shaft of the engine or via an additional electric drive.
• the implementation of a hydraulic motor, and the circuit that accompanies it, as a starter of a heat engine, turns out to be a complicated operation.
• This document discloses a hydraulic starter associating a hydraulic motor with radial pistons, associated with a pump for charging an accumulator.
• the motor is of the fixed housing type, with a rotating shaft on which is fixed the cylinder block.
• the output member of the motor is a coupling piece fixed at the end of the motor shaft. The presence of this part induces additional length and additional complexity for the hydraulic starter.
• a valve device activates a hydraulic clutch interposed between the motor shaft and the drive member of the pump.
• the motor shaft then drives the pump; the rotation of the latter then makes it possible to recharge the accumulator.
• the object of the invention is therefore to provide an improved hydraulic transmission device, of the type presented in the introduction, which can constitute a relatively simple hydraulic starter and having a small footprint by being coupled to an accumulator and a fluid reservoir.
• the pump is able to discharge fluid under pressure via said coupling; consequently, it is able to be connected to an accumulator for filling it with pressurized fluid.
• the pump is rotated by the housing (directly or indirectly); it can therefore be arranged in the immediate vicinity of the motor and integrated with it.
• the housing is rotating, it is - directly or indirectly - the output member of the starter, which makes unnecessary the use of a coupling part fixed at the end of the motor output shaft, as in the previous embodiment presented previously.
• the invention provides a device that is not only compact, but also economical to produce, because of the reduced length of the connection ducts between the pump and the hydraulic motor, the reduction in the number of connection components, and a reduction in the number of connecting components. reduced number of operations for its assembly on the engines, including a reduction in the number of hydraulic connections to be made.
• the support comprises a preferably substantially cylindrical portion around which the dispenser is arranged.
• - It may have a planar distribution face (in particular perpendicular to the axis of rotation); - It can be arranged between the cylinder block and the pump, at least in terms of position relative to the axis of rotation.
• an engine exhaust duct and a pump supply duct meet at a branch in the carrier.
• these ducts are arranged compactly, and the device may comprise only three orifices or external connections.
• a conduit for supplying the pump and / or exhaust of the motor is formed in the support shaft and connects a connector arranged on an outer surface of the support shaft with an internal space of the casing.
• this conduit serves both the pump supply and the engine exhaust, when the fluid escaping from the engine is rejected in the internal space of the housing.
• the fluid sucked by the pump circulates around the drive member of the pump before entering the interior of the pump. It thus ensures the lubrication of the drive member of the pump.
• the integration of the pump in the support can in particular be carried out so as to allow the lubrication of the support thanks to the fluid present inside the housing of the hydraulic motor.
• a feed passage of the pump through which passes a fluid supplying the pump may be formed between the drive shaft and the support.
• the passage of the fluid in this passage cools and lubricates the support.
• a pump supply duct may be formed in the holder and connect an internal space of the casing to the supply passage.
• the device may then comprise a fluid supply conduit for injecting a pump supply fluid into said internal space; said inner space being further connected to said supply passage via a supply conduit for supplying the fluid supply passage; an orifice of the supply duct in the internal space of the casing and an orifice of the supply duct in the internal space being arranged axially on either side of the cylinder block.
• the fluid supply duct may for example connect a fitting arranged on an outer surface of the support to the internal space of the casing.
• This supply conduit serves in particular to introduce into the internal space the fluid supplying the pump (or a part thereof).
• a pump is chosen in which a larger transverse dimension perpendicular to the axis of rotation is smaller than the diameter of the cylinder block, for example a gear pump.
• the pump can then generally be disposed completely inside the support.
• the transmission device can in particular be used to drive in rotation a rotary drive member of a machine.
• the casing has, for coupling with the member to be driven, a flange, an external groove adapted to receive a pulley belt, or a toothing for a chain or a gear.
• the housing can thus be directly attached to one end of the crankshaft of an internal combustion engine.
• FIG. 5 is an axial section of a hydraulic device according to the invention, in a second embodiment
• FIG. 6 is a section perpendicular to its axis of the hydraulic device of Figure 5;
• FIG. 7 is an axial section of a hydraulic device according to the invention, in a third embodiment.
• connection of the hydraulic device 40 is simplified, and advantageously comprises only three ducts:
• the conduits 22 and 23 are connected to the accumulator 14 by a valve 136.
• the device 40 comprises a hydraulic motor 42 in which is integrated a hydraulic pump 44.
• the motor 42 is a retractable motor with radial pistons. He understands :
• a casing 46 composed of three parts, namely a cover 46A, a corrugated cam 46B, and a distribution casing 46C;
• the cylinder block 48 has cylinders 56 in which pistons 58 slide. These pistons 58 are arranged to be able to transmit pressure to the inner surface of the cam 46B.
• the pressures exerted by the pistons 58 allow the motor 42 to develop a driving torque.
• This engine torque is transmitted by the casing 46, which acts as an output member of the motor 42, to the equipment to which the motor 42 is coupled:
• This equipment is here the crankshaft of the internal combustion engine 110.
• the distributor 50 is rigidly connected to the timing case 46C by means not shown.
• the fluid distributor 50 is rotatable and has a planar distribution face perpendicular to the axis of rotation 51. It is disposed between the cylinder block 48 and the pump 44.
• the pistons 58 are retractable pistons. They are returned to the cylinders 56 by springs 62, when the pressure inside the cylinders 56 is less than that prevailing in the inner space 52 and the difference between the two pressures exceeds a predetermined value, which depends on the springs 62.
• the housing 46 is held in position on the support shaft 54 by ball bearings 64 and 66 disposed on either side of the cylinder block 48.
• the bearings 64 and 66 hold the housing 46 and the distributor 50 of such that they can rotate about the axis A of the support shaft 54.
• the pump 44 is a compact gear pump. In a manner known per se, it has (fig.4) two toothed wheels 68A, 68B which mesh with each other and ensure the pumping of the fluid passing through the pump 44.
• the largest transverse dimension D of the pump 44 measured perpendicularly to the axis of rotation A, is smaller than the diameter of the cylinder block and even the radius of the cylinder block, which makes it possible to integrate the pump 44 without particular difficulties in the support shaft 54.
• the pump 44 is mounted in a bore (a chamber) formed in the support shaft 54. It is held in position by its cover 45, which is screwed onto the end surface of the support shaft 54 by a screw 47.
• All of the fluid exchanges of the device 40 are via three connections 70, 72 and 74, formed in the first end 54A of the support shaft 54.
• conduits 76 and 78 are formed in the end 54A of the support shaft.
• the pump admission conduit 76 connects the connector 70 to the inlet chamber 441 of the pump 44.
• the pump discharge conduit 78 connects the delivery chamber 440 of the pump 44 to the connector 74.
• an angled feed duct 80 is formed in the support shaft 54. This duct 80 connects the connector 72 to an annular groove 75 formed on an outer circumference of the shaft. support 54, inside the dispenser 50.
• the operation of the motor 42 is as follows:
• the fluid supplying the motor 42, coming from the accumulator 14 via the conduit 22, is injected into the device 40 via the connector 72. Via the conduit 80, it is injected into the groove 75.
• the distributor 50 comprises first distribution 82. These convey fluid from the groove 75 to cylinder ducts 84 formed in the cylinder block 48, through which the fluid is injected into the cylinders 56.
• the distributor 50 which is rotated by the housing 46, successively supplies the different cylinders 56.
• the pistons 58 are in turn urged by the pressure in the cylinders 56 to exit the cylinders; the pressure they exert on the cam 46B generates a motor torque.
• the injection of pressurized fluid from the accumulator 14 makes it possible to drive the casing 46 in rotation, which consequently ensures, via the flange 60, the starting of the motor 110.
• the fluid Upon retraction of the pistons 58, the fluid is removed from the cylinders 56 by the cylinder ducts 84; it is thus driven via second distribution ducts 86 into the internal space 52 of the casing 46.
• a duct 88 passing through the support shaft 54 connects the internal space of the casing with the duct 76.
• This duct 88 joins the duct 76, which serves to supply the pump, in a branch T located in the shaft - support.
• This branch therefore divides the conduit 76 into two portions, namely an outer portion 76 ', connecting the connector 70 to the branch T, and an inner portion 76', connecting the branch T to the inlet chamber of the pump 441 (fig.4).
• the operation of the pump 44 is as follows:
• the pump has a part or drive member 90 which allows its drive.
• This part 90 forms a shaft on which is fixed the toothed wheel 68A.
• the pump is disposed in the support shaft 54 so that the axis of the part 90 coincides with the axis of rotation A of the engine.
• the device 40 comprises a drive shaft 92.
• This shaft 92 is integral in rotation with the cam 46B, via the cover 46A.
• the shaft 92 is fixed (screwed) in the cover 46A of the motor 42.
• any other method of fixing the drive shaft 92 to the cover 46A can be used, such as for example a finger. flattened drive in the form of a screwdriver blade, etc.
• the axis of the shaft 92 is also coincident with the axis of rotation A of the motor.
• An axial cylindrical bore 94 is made along the axis A in the support shaft 54 to allow the passage of the drive shaft 92 and the drive part 90.
• the drive part 90 is secured in rotation with the drive shaft 92 by means of a drive finger 96.
• the drive part 90 of the pump is thus rotated by the housing 46, via the drive shaft 92 and the drive finger.
• the drive finger 96 allows in particular a limited axial displacement, along the axis A, between the drive shaft 92 and the drive part 90. Such displacement may be necessary depending on the relative expansions. of the shaft 92 and the part 90.
• the shaft 92 makes it possible to transmit the movement imposed by the motor on the cam 46B to the drive member 90 of the pump 44.
• This result is achieved by virtue of the fact that the shaft connected to the cover 46A itself even integral with the cam 46B, connects this cover to the drive member 90 of the pump passing through the inside of the cylinder block 48.
• the pump 44 is supported by two bearings 98A and 98B, arranged axially on either side of the gears 68A, 68B.
• the pump When the pump is actuated, under the effect of the rotation of the gear formed by the wheels 68A and 68B, the fluid is sucked from the reservoir 20 via the conduit 124 and the conduit 76. It is pumped by the gears 68A and 68B and transferred from the suction chamber 441 to the delivery chamber 440. It is thus forced under pressure in the conduit 78, and thence to the accumulator 14 via the conduit 23. The pump thus ensures the filling of the accumulator 14.
• the hydraulic device 140 can be used as a hydraulic starter for an internal combustion engine, as in the first embodiment. Its integration into an engine is exactly the same as that of the device 40 presented in FIGS. 2 to 4.
• the second embodiment may be considered identical to the first embodiment.
• the identical elements or having the same function have the same numerical references in both embodiments.
• a supply duct 100 is pierced between the internal space 52 and the bore 94.
• This supply duct 100 is formed in the vicinity of the cover 46A, and preferably the most close to this one.
• the conduit 100 allows the passage of fluid from the internal space 52 to the bore 94.
• annular feed passage 102 is provided by means of a clearance provided between the support shaft 154 on the one hand, and the drive shaft 92 and the drive part 90 on the other hand. This clearance is calculated so that the section of the feed passage 102 is sufficient for feeding the pump.
• the operation of the pump is as follows: The fluid is sucked by the pump from its suction chamber 441.
• the aspirated fluid enters the support shaft 154 through the connector 70, passes through the conduits 76 'and 88, the inner space 52 of the housing, the conduit 100, the feed passage 102, the second feed passage 104, to finally reach the suction chamber 441.
• the advantage of this path is that the fluid sweeps the inner space 52 of the housing, and the annular space 102 between the passages 100 and 104. In doing so, it cools and lubricates these various elements, including all the outer faces of the block 48, the drive shaft 92 and the drive part 90.
• FIGS. 7 and 8 show a device 240 illustrating a third embodiment of the invention, very close to the first two embodiments illustrated by FIGS. 3 to 6.
• the specificity of the third embodiment with respect to the first two modes of embodiment is the arrangement of the support (254) and consequently the fluid exchange conduits of the device. Despite these differences, the operation of the device 240 is substantially identical to that of the devices 40 and 140.
• the device 240 comprises a hydraulic motor 242 which is integrated a hydraulic pump 244.
• the engine 242 is a radial piston reciprocating engine that includes:
• the cylinder block 248 of the engine 242 is fixed on the support 254.
• it has a cylindrical tubular projection 249, which extends concentrically about the axis A on the first side of the cylinder block.
• the end of this projection 249 is fixed on the support 254 by means not shown; the projection 249 thus ensures the fixing of the cylinder block on the support 254.
• the pump 244 is arranged inside the head 256 of the support 254. It is identical to the pump 44 shown above, except for the shape of its drive part 290.
• the end of the drive part 290 is arranged so as to be integral in rotation with the shaft 247, and therefore the housing 246.
• the junction between the shaft 247 and the part 290 is provided by a connecting piece 291.
• the fluid exchanges of the device 240 are as follows:
• the device 240 comprises three fluid exchange conduits, 276, 278 and 280.
• the first conduit 278 is formed partly in the head 256 of the support 254 and partly in a pump cover 279. This cover 279 is fixed on the first side of the head 256, that is to say on the opposite side to the cylinder block 248. When the pump 244 is in place in the head 256, the cover 279 serves to block it inside the head 256.
• the conduit 278 connects the discharge chamber 2440 of the pump 244 to an external connection 274 formed on an outer surface of the lid 279.
• the end of the conduit 276 which is on the side of the device 240 is divided into two branches.
• the first branch is connected to the inlet chamber 2441 of the pump 244.
• the second branch opens (not shown) in an internal space 252 arranged between the distributor 250 and the head 256, this internal space having a shape of revolution around the axis A.
• the groove 275 and the internal space 252 play the same role in the device 240 as the groove 75 and the internal space 52 in the device 40.
• the distributor 250 comprises first and second distribution ducts 282 and 286 ensuring fluid distribution in the cylinders of the cylinder block, similarly to the ducts 82 and 86 respectively.
• a pulley piece 223 is attached to the cover housing 246A.
• the outer surface of this part has a grooved groove 225 adapted to drive a belt.
• different parts similar to the piece 223 can be mounted interchangeably on the motor 242, to easily adapt the motor 242 and in particular the drive groove thereof to the type of belt (or possibly chain or other body d). drive) that the motor must drive.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Reciprocating Pumps (AREA)
• Hydraulic Motors (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=46420349

Family Applications (1)

Country Status (5)

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Citations (2)

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• 2011
  • 2011-05-27 FR FR1154634A patent/FR2975731B1/fr active Active
• 2012
  • 2012-05-22 CN CN201280025913.8A patent/CN103562541B/zh not_active Expired - Fee Related
  • 2012-05-22 EP EP12731033.2A patent/EP2715104A2/de not_active Withdrawn
  • 2012-05-22 WO PCT/FR2012/051130 patent/WO2012164199A2/fr active Application Filing
  • 2012-05-22 US US14/122,592 patent/US20140322044A1/en not_active Abandoned

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Non-Patent Citations (1)

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