Classifications

• • 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
  • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
  • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type
• • 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
  • F04C2/16—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 helical teeth, e.g. chevron-shaped, screw type
• • 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
  • F04C2240/00—Components
  • F04C2240/30—Casings or housings

Definitions

• the invention relates to a device for pressurizing a fluid, intended to be attached to a power take-off of a motor vehicle and a system comprising a power take-off and such a device for pressurizing.
• the invention particularly relates to compressors and pumps connected to a power take-off of a motor vehicle.
• the power take-offs are generally fixed on a gearbox and take their rotational movement on one of the gears of said gearbox.
• the power take-offs include an output sleeve for transmitting motion to a drive shaft and commonly a control clutch, separate from the main clutch of the vehicle, for connecting or disconnecting the gearbox to the output of the transmission. the power take-off.
• the power take-offs may further include a speed multiplication between the input speed and the output speed. The ratios of reduction or multiplication are commonly between 0.5 and 2.
• the pressurizing devices comprise at least one frame and one or two shafts, movable in rotation, carrying a member ensuring the setting under fluid pressure, pump or compressor.
• the frame of the pressurizing devices is mounted on the chassis of the vehicle and a cardan shaft, connected on the one hand to the power take-off and on the other hand to the pressurizing device, transmits the movement of the power take-off to the pressurizing device.
• the output speed of the power take-off is insufficient to drive the compression gear at the right speed.
• a multiplier is integrated into the compressor. Indeed, the speed of rotation at the output of a power take-off can reach only about 2000 rpm while the speed required for the proper operation of a screw compressor is greater than 10,000 revolutions / minute.
• the pressurizing devices comprise a safety member for limiting the torque transmitted between the power take-off and the movable member ensuring the pressurization of a fluid. Indeed, in case of blockage of the compressor or the pump, it is necessary to limit the torque transmitted to prevent the rupture of the transmission members.
• the devices of the prior art have a large size, because of the presence of a multiplier and a device for limiting the torque, so that the integration of these devices to a motor vehicle is not satisfactory.
• the installation of these devices is complex because they must be previously attached to the chassis of the vehicle, and then connected to the power take-off by the cardan shaft.
• the direction of rotation at the output of the gearboxes and therefore the output of the power take-offs can be hourly or counterclockwise.
• the devices for pressurizing a fluid are adapted in series to one or the other of the directions of rotation, or a reverser of direction of rotation is arranged between the power take-off and the device.
• the first solution requires manufacturers to provide two different references of devices while the second solution increases the size and complexity of the system.
• the invention aims to remedy these problems by proposing a device for pressurizing a fluid intended to be associated with a rotary power take-off, which is reliable and whose size and integration on the vehicle automobile are satisfactory.
• the invention provides a device for pressurizing a fluid, intended to be associated with a rotary power take-off of a motor vehicle comprising a housing and at least one multiplication stage, said device comprising a frame supporting at least a first movable rotating shaft carrying a member for the setting in motion of the fluid and dynamic coupling means of the shaft to the power take-off.
• the frame comprises support means and fixing to the casing of the power take-off and in that said coupling means are arranged to directly connect the movable shaft to the multiplication stage of the socket. of movement.
• the dynamic coupling means directly connect the movable shaft, carrying the fluid moving member, to the power take-off.
• the pressurizing device therefore does not include a multiplier because it is offset in the casing of the power take-off.
• the load related to the multiplier is close to closer to the junction between the power take-off and the gearbox so that the device, thus formed, is more compact, lighter and the system consists of the device and
• the power take-off thus becomes compatible with the allowable loadings at the junction between the power take-off and the gearbox.
• the coupling means comprises a single transmission element between the stage of multiplication and the movable tree.
• the device therefore does not include a multiplication stage, other than that of the power take-off.
• the coupling means comprise a pinion carried by the first movable shaft.
• This coupling means allows direct cooperation with the output gear of the power take-off. The drive of these gears allows a multiplication of the speed of rotation.
• the fastening means comprise a peripheral fastening flange, intended to be arranged against the casing of the power take-off.
• the fixing flange comprises a cradle-shaped portion so as to allow passage of the multiplication stage of the power take-off.
• the fixing means comprise centering and positioning means. These means make it possible to ensure precise dynamic coupling between the device and the power take-off.
• the transfer device comprises an internal lubrication circuit and means for connecting the internal circuit to the lubrication circuit of the motor vehicle.
• the rotating members of the device may require forced lubrication.
• the invention meets this need by providing a lubrication circuit capable of being connected to a lubrication circuit of the motor vehicle comprising pumping means and arranged, for example, in the casing of the power take-off.
• pumping means capable of being connected to a lubrication circuit of the motor vehicle comprising pumping means and arranged, for example, in the casing of the power take-off.
• connection means comprise a supply orifice extending in the axis of rotation C of the multiplication stage of the power take-off so as to allow a supply of the lubricant by the shaft. supporting said multiplication stage.
• the internal lubrication circuit includes a filter.
• the invention relates to a device for pressurizing a fluid, intended to be associated with a rotary power take-off of a motor vehicle comprising a housing, said device comprising a frame, a first and a second rotating shafts each carrying a member for moving the fluid, means for synchronizing the rotation of the first and second shafts arranged to drive the first shaft in a first direction of rotation and the second shaft in a second direction. direction of rotation in a suitable gear ratio; and means for dynamically coupling the first or second shaft to the power take-off.
• said coupling means comprise a removable pinion adapted to be mounted either on the first or on the second shaft, depending on the direction of rotation of said power take-off, so as to cause the first shaft in the first direction of rotation and the second shaft in the second direction of rotation and that regardless of the direction of rotation of said power take-off.
• the device according to the second aspect of the invention is adaptable to different gearboxes and market power take-off.
• this adaptation is simple and does not require an additional adapter that would increase the weight and size of the device, so that this solution is particularly interesting when the frame of the device is fixed and supported by the casing of the power take-off .
• the synchronization means advantageously have a multiplication ratio of the order of 1.2.
• the invention relates to a system comprising a rotary power take-off comprising a casing and a device for pressurizing a fluid according to the first and / or second aspect of the invention, associated with said casing.
• FIG. 1a is a perspective view of a pressurizing device according to the invention, cooperating with a transmission pinion of the movement belonging to the power take-off;
• FIG. 1b is a perspective view of a system comprising a pressurizing device and a power take-off, the housing is intended to be fixed on a gearbox;
• FIG. 2 is a detailed perspective view of the pressurizing device of FIG. 1a;
• - Figure 3 is a front view of a device according to the invention illustrating the support means and fixing to the housing;
• FIG. 4 is a perspective view of a device according to the invention comprising centering and positioning means according to a second embodiment
• FIG. 5 is a perspective view of a device according to the invention, illustrating the connection means of the internal lubrication circuit to a lubrication circuit of the motor vehicle;
• FIG. 6 is a view of the device of Figure 5, in section along the plane VI-Vl;
• FIG. 7 is a view of the device of Figure 5, in section along the plane VII-VII;
• FIG. 8 is a cross-sectional view of the device of FIG. 5;
• FIG. 9 illustrates a system according to the invention comprising a power take-off and a pressurizing device, mounted on a gearbox;
• FIG. 10 illustrates a device according to a second embodiment of the invention.
• the device for pressurizing a fluid shown in FIGS. 1 to 11 is a screw compressor 1.
• the compressor 1 is intended to be associated with a power take-off 2 of a motor vehicle, shown in Figures 1b and 10.
• the power take-off 2 comprises a housing 3 which is intended to be fixed on the box 17 of a motor vehicle, shown in Figure 10.
• the power take-off cooperates with an output shaft of the gearbox 17.
• the casing 3 comprises fixing means on the gearbox 17 of the motor vehicle.
• the PTO 2 is equipped with a torque limiting device transmitted, not shown. This device makes it possible to protect the transmission members in the event of blockage of a mobile shaft of the device 1.
• the PTO 2 comprises, at the output, a pinion 4, illustrated in Figures 1a and 2, and constituting a multiplication stage.
• the pressurizing device comprises a frame 5 which is intended to be associated with the casing 3 of the power take-off 2.
• the pressurizing device 1 comprises, in the embodiment shown, two shafts 6a, 6b rotatable on the frame 5, respectively about a first axis A and a second axis B , parallel.
• Each of the shafts 6a, 6b carries a compression screw, not shown, extending in a compression chamber of the device 1.
• the device 1 comprises a feed orifice and a fluid outlet orifice communicating with the compression chamber.
• the two screws have complementary profiles and are nested one inside the other, but do not come into contact with each other.
• One screw called female
• the other named male
• the first screw rotates in a first direction of rotation while the second screw rotates in a second direction of rotation.
• the female screw has 6 concave profiled lobes while the male screw has 5 convex profiled lobes. Due to the number of different lobes, the relative speeds are in a ratio of 5/6 or 6/5 depending on the screw taken as a reference. The rotations of the screws are synchronized.
• the shafts 6a, 6b each carry a gear wheel 11a, 11b cooperating with each other.
• the two gear wheels 11a, 11b form means for synchronizing the rotation of the shafts 6a, 6b for driving said shafts in directions of inverted rotation.
• the synchronization means will be adapted to respect the rotational speed ratios between the screws. Note that we can use any equivalent means to achieve the rotation speed synchronization function.
• one of the shafts 11a, 11b supports a pinion 7 forming a coupling means with the output gear 4 of the power take-off 2.
• the movable shafts 6a, 6b are capable of being driven at high rotational speeds of the order of 10 000 to 20 000 revolutions per minute for example.
• the pinion 7 is removable and is adapted to be mounted alternately on one end of the first 6a or the second shaft 6b.
• This embodiment makes it possible to adapt the pressurizing device 1 to the different gearboxes on the market.
• the output shafts of the gearboxes 17 of the market can indifferently be driven in rotation in the clockwise direction or in the counterclockwise direction.
• the device 1 for pressurizing adapts to the different types of gearbox 17 and existing power take-off.
• the pinion 7 will be placed on the first 6a or the second shaft 6b, depending on the direction of rotation of the power take-off 2.
• the first shaft 6a in the first direction of rotation and the second shaft 6b in the second direction of rotation.
• the axes of the two shafts 6a, 6b are placed at an equal distance from the axis of rotation C of the output pinion 4, to allow the drive of one or the other of the shafts.
• the shafts 6a, 6b have receiving ends of the pinion 7, identical and adapted to receive the bore central pinion 7.
• the central bore of the pinion 7 comprises longitudinal grooves 15 engaging in longitudinal grooves 16 of the shafts 6a, 6b.
• the shaft 6a, 6b which does not support the pinion 7 supports a removable spacer 14 of protection.
• the bores of the pinion 7 and the spacer 14 are identical.
• the spacer 14 obviously has an outside diameter smaller than the diameter of the pinion 7, so that when the device is associated with the power take-off, the spacer 14 does not come into contact with the output pinion 4 of the take-off. movement 2.
• the rotational speeds at the output of the gearboxes 17 are different, of construction.
• this difference in speed is commonly related to the direction of rotation, clockwise or anticlockwise, at the output of the gearbox 17. Therefore, in order to allow optimal operation of the device regardless of the type of gearbox. speed 17 used, it can be provided that the rotational speeds of each screw is identical, in operation and that the gear ratio between the screws is substantially identical to the rotational speed ratio between the boxes whose output is driven in the direction and the boxes whose output is drawn counterclockwise.
• the ratio of output speeds between the two types of box is of the order of 1, 15
• the gear wheels 11a, 11b thus have sizes and numbers of teeth adapted to the ratio 6/5 lobes of male and female screws.
• This ratio of 1, 2 is cleverly used in relation to ratio 1, 15 of the box types to maintain the speed of the drive motor at the most suitable speed between about 1200 rotations per minute and about 1400 rotations per minute.
• the frame 5 comprises fixing means to the casing 3 of the power take-off 2. These means are able to support and support the device 1 for putting under pressure.
• the pressurizing device 1 is fixed and supported only by means of these means and is not directly fixed by other means to the chassis of the vehicle.
• the frame 5 can therefore be considered as self-supporting.
• the support and fixing means comprise a peripheral fastening flange 8 which is adapted to cooperate with the casing 3 of the power take-off 2, via a suitable fastening flange 13 of the casing 3 for example.
• the fastening flange 8 comprises bores intended to come into contact with threaded bores formed on the casing 3.
• the bores allow the passage of fixing members 10, such as screws, cooperating with the threaded bores. of the casing 3, so as to secure the pressurizing device 1 to the casing 3.
• the fastening flange 8 has a particular shape. Indeed, the fastening flange 8 comprises a first portion along a portion of the periphery of the frame 5 and a second portion, cradle, substantially circular whose center corresponds to the center of rotation C of the output gear 4 of the power take-off 2. The second portion of the fastening flange 8 allows the output gear 4 of the power take-off 2 to pass so that the pinion 7 cooperates directly with the output pinion 4. Furthermore, the fastening flange 8 is also equipped with centering and positioning means relative to the casing 3. These centering and positioning means provide a precise dynamic coupling between the power take-off 2 and the setting device. under pressure 1.
• the centering and positioning means comprise cavities 9 for receiving pins of complementary shapes, formed on the housing 3.
• the cavities 9 can be formed in the housing 3 while the pins of complementary shapes are carried by the fastening flange 8.
• the pins must have a length and strength sufficient to allow the support of the device.
• the centering and positioning means will advantageously comprise only two cavities 9 and that the line passing through these two cavities also passes through the center C of rotation of the output pinion 4 of the power take-off 2.
• the positioning of the device 1 with respect to the power take-off 2 is ensured in a precise manner by limiting the number of cavities 9 used.
• positioning pins may be indifferently cylindrical in shape, conical or more generally any suitable shape.
• the fastening flange 8 comprises a female interlocking structure 18, or male, intended to receive a conjugate interlocking structure formed on the fastening flange 13 of the casing of the power take - off 2.
• the pressurizing device 1 comprises an internal lubrication circuit and means for connecting the internal circuit to a circuit of lubrication of the motor vehicle.
• the internal circuit of the device 1 is connected to a vehicle lubrication circuit located in the power take-off, for example, and comprising a reservoir and a pump for circulating the lubricant towards the internal circuit of the device 1.
• FIGS. 5 to 8 illustrate in detail the internal lubrication circuit.
• the lubrication circuit of the motor vehicle is here fed to the device via the output pinion support shaft 4, not shown, the inner bore forms a lubricant routing conduit.
• the end of the output pinion support shaft 4 is introduced into a supply port 19 of the device extending along the axis C of rotation of the output pinion 4.
• the positioning pins formed on the housing 3 have a length sufficient to allow the positioning of the device 1 relative to the power take-off 2 before introducing the end of the shaft into the feed port 19.
• the lubricant is then conveyed from the supply port 19 to a lubricant filter 21 by means of a first channel 20, shown in FIG. 6.
• the purified lubricant is then conveyed to the bearings 22a, 22b of the shafts 6a, 6b via a second duct 23, shown in FIGS. 7 and 8.
• the bearing armatures 23a, 23b have slots 24a, 24b of passages for the lubricant.
• the lubricant then descends by gravity to the bottom of the frame 5. Thereafter, the lubricant can be collected by means of a pumping device carried, for example, by the power take-off.
• the fluid pressure device 1 has a mass and dimensions arranged so that the forces applied by the device associated with the power take-off are less than the allowable loads at the junction of the socket. of movement on the gearbox.
• the dimensions and the thickness of the walls of the frame are optimized.
• the coupling gear 7 and / or the output gear 4 of the power take-off 2 are adapted to drive the movable shafts at speeds of the order of 10,000 to 20,000 revolutions per minute.
• Figures 10 and 11 illustrate a second embodiment of the invention.
• the device 1 comprises a frame 5, supporting two shafts 6a, 6b rotatable in opposite directions of rotation, synchronization means and a removable pinion 7 adapted to be mounted alternately on the first 6a or the second shaft 6b according to the direction of rotation of said power take-off 2.
• the device 1 comprises a device for multiplying the speed of rotation, composed of a succession of gears 26, 27, 28 whose sizes are adapted to obtain the desired multiplication ratio.
• the device comprises a splined shaft 25, shown in Figure 10, intended to be engaged in a rotary sleeve of the power take-off.
• the device comprises a fastening flange 26 intended to be fixed on the casing 3 of the power take-off 2.
• This device 1 is adaptable to different gearboxes and market power take-off. Note however that the device obtained according to the second embodiment is more bulky and heavy than that which can be obtained according to the first embodiment. Nevertheless, this embodiment may be suitable for solutions requiring low compression power, whose weight and size remain measured.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• General Details Of Gearings (AREA)
• Gear Transmission (AREA)

Applications Claiming Priority (1)

Publications (1)

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Family Applications (1)

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• 2008
  • 2008-12-19 WO PCT/FR2008/001808 patent/WO2010070211A1/fr active Application Filing
  • 2008-12-19 CA CA2740996A patent/CA2740996C/en not_active Expired - Fee Related
  • 2008-12-19 US US13/125,500 patent/US20110293444A1/en not_active Abandoned
  • 2008-12-19 CN CN200880132448.1A patent/CN102256824B/zh active Active
  • 2008-12-19 EP EP08875637A patent/EP2367701A1/de not_active Withdrawn

Non-Patent Citations (2)

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