EP3724506A1 - Scroll-type positive-displacement machine - Google Patents
Scroll-type positive-displacement machineInfo
- Publication number
- EP3724506A1 EP3724506A1 EP18819531.7A EP18819531A EP3724506A1 EP 3724506 A1 EP3724506 A1 EP 3724506A1 EP 18819531 A EP18819531 A EP 18819531A EP 3724506 A1 EP3724506 A1 EP 3724506A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spiral
- machine
- spirals
- volumetric
- machine according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0284—Details of the wrap tips
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- 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
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
Definitions
- the present invention relates to the field of volumetric machines, especially compression machines or expansion machines. These machines can be:
- volumetric machines using a change in gas volume.
- the volumetric machines can be pistons, spiro-orbital, screw, etc.
- the present invention relates more particularly to the field of volumetric spiro-orbital machines (in English "scroll”), in both forms of use, as a compressor (used for example as an air compressor or in an air conditioning cycle, refrigeration or in a heat pump (sometimes referred to as "Compressor G”) or as a relaxation machine (used for example in an organic Rankine cycle).
- a compressor used for example as an air compressor or in an air conditioning cycle, refrigeration or in a heat pump (sometimes referred to as "Compressor G) or as a relaxation machine (used for example in an organic Rankine cycle).
- Such a machine comprises a spiral-shaped moving part performing an orbital movement with respect to another fixed spiral substantially identical to the first. These two spirals are 180 ° out of phase.
- the spaces formed between the two spirals constitute chambers of geometry and evolutionary position, progressively reduce as the orbital displacement of the mobile spiral to lead to the central discharge port, and conversely in a use in relaxation machine, the rooms grow gradually to open laterally to the periphery.
- This type of volumetric machine has a reduced sound level, a great flexibility of use with a range high speeds, good performance, robustness and continuous operation at almost constant torque.
- one of the difficulties relates to obtaining a high volume ratio between the volume of the chambers just before the exhaust and the volume of the chambers just after admission, while accepting high pressures and temperatures which solicit the spirals importantly.
- fixed and orbital spiral members each having an end plate and a spiral member extending from one side of said end plate
- spiral members mutually adjusting with angular and radial offset to provide a plurality of contact lines defining at least one pair of closed fluid chambers;
- a drive mechanism comprising a drive shaft rotatably supported by said casing for causing said spiral member to perform the orbital movement by rotation of said drive shaft so as to change the volume of said drive chambers; fluids.
- the inner end of said spiral element of each of said spiral members has a surface of axial section which changes, from the root to the tip thereof, and has an extension to the transition between the root and the end plate.
- the mobile spiral has a significant thickness at its inner end leading to a partial closure of the central orifice of the fixed spiral, during the admission for an expansion machine, or during the discharge for a compressor type machine. The consequence is a degraded performance.
- the thickness of the spiral at its inner primer reduces the feed section -defined by the spacing of the spiral flanks in cooperation- from the forming chamber to the hollow of the mobile spiral (so-called "indirect" pocket ), for an expansion machine, or just reduces the discharge section of the outlet chamber in the case of a compressor.
- the consequence is also a degradation of the performances.
- the present invention relates in its most general sense to a spiral volumetric machine according to the main claim taken alone or in combination with one or more additional technical features.
- FIG. 1 shows an exploded view of an expansion machine according to the invention
- Figure 2 shows an inner and outer perspective view of the spiral cover assembly
- FIG. 4 shows a front view of the fixed and mobile spirals of the machine
- FIG. 5 represents the position of the fixed and mobile spirals during a rotation of the shaft of the machine
- Figure 6 is a partially cutaway perspective view of the movable portion of the machine
- Figure 7 shows a partially cutaway perspective view of the housing assembly of the machine
- Figure 8 shows a partially cutaway perspective view of the coupling assembly of the machine
- Figure 9 shows front views of different axial abutment surface variants
- FIG. 10 shows a schematic view of the lubrication of the machine
- FIG. 11 represents a schematic view of a Rankine cycle according to the invention.
- FIG. 12 represents a schematic view of a high temperature heat pump according to the invention.
- FIG. 13 shows schematic views of design details present on the spirals
- FIG. 14 represents three sectional views of the assembly constituting the mobile spiral and the fixed spiral at three different stages of the expansion cycle;
- Figure 16 shows a front view of a variant form of the intake port
- Figure 17 shows a sectional view of the spirals during the exhaust
- Fig. 18 is a graph showing the impact of one of the design points of the spirals.
- FIG. 19 shows a variant of the thrust washer having an annular chamber against pressure
- FIG. 20 shows a sectional view of the central zone formed by the spirals.
- the invention relates, as previously explained, spiro-orbital volumetric machines, both for applications of the type of expansion machine as for applications of the compression machine type.
- An expansion machine within the meaning of the present invention, produces a rotary mechanical movement by transforming the energy from a working fluid under pressure.
- the transformation is carried out in an expansion chamber, or several expansion chambers, forming an expansion zone, supplied with working fluid in lubricant-laden vapor form, coming from the high-pressure inlet zone and discharged by an exhaust zone.
- the pressurized fluid comprises a main component such as ethanol or cyclopentane or a refrigerant r 233zd (E) or 336mzz (Z), providing the thermodynamic cycle, charged with a liquid lubricant sprayed into the vapor phase of the main component.
- the lubricant is for example polyalkylene glycol (PAG) or polyolester (POE) miscible in the liquid phase with the other components.
- the proportion of lubricant is typically between 1 and 20% by weight.
- this working fluid may further comprise components such as water, in a proportion of between 0 and 20% by weight and optionally additives for denaturing the ethanol, by example of 1 euro-denaturant (trade name), or an alkane, or methanol, or a ketone in proportions of between 1 and 10% by weight.
- additives for denaturing the ethanol by example of 1 euro-denaturant (trade name), or an alkane, or methanol, or a ketone in proportions of between 1 and 10% by weight.
- the expansion machine operates according to the general principle of the relaxation step of a Rankine or Hirn cycle.
- a compression machine within the meaning of the present invention, compresses a gaseous working fluid by transforming the energy coming from a rotary mechanical movement.
- the transformation is carried out in a compression chamber or several compression chambers forming a compression zone, supplied with lubricant-laden gaseous working fluid from the low-pressure inlet zone and discharged through an exhaust zone. high pressure.
- the fluid comprises a main component such as a refrigerant R1336mzz (Z) or R1233zd (E), providing the thermodynamic cycle, charged with a liquid lubricant sprayed into the vapor phase of the main component.
- the lubricant is for example polyalkylene glycol (PAG) or polyolester (POE) miscible in the liquid phase with the other components.
- the compression machine operates according to the general principle of the step of compressing a refrigeration cycle.
- the volumetric spiro-orbital machines comprise two complementary structures (2, 3) with relative displacement of the orbital type.
- the first structure is a fixed structure (2) formed by a first transverse disc end plate (2001), one of whose surfaces forms a spiral bottom, surmounted by a wall defining a first spiral (2002).
- This end plate (2001) has a first central opening (407).
- the second structure (3) is movable relative to the fixed structure (2). It is formed by a second transverse disc end plate (3001) whose one of the surfaces forms a spiral bottom, surmounted by a wall defining a second spiral (3002).
- the second structure (3) moves relative to the first structure (2) in a circular translation, called orbital motion.
- the movement is characterized by a plane in which the movement takes place and an eccentricity.
- the plane is defined by the front surface of the second disc end plate (3001) on the opposite side to the second spiral (3002).
- value of the eccentricity the maximum offset between the fixed structure (2) and said movable structure (3).
- the spiral members (2002, 3002) mutually adjust with an orbital offset to provide a plurality of contact lines defining at least one pair of closed fluid chambers (411, 419, 420, 423, 424).
- the volume of these fluid chambers varies according to the relative position of one of said structures (2) relative to the other structure (3).
- the inner end of the spiral member (2002, 3002) has an upper indentation respectively (409, 313) extending from the opposite surface of the plate (2001, 3001) to an intermediate section (2003, 3003). ).
- FIGS. 1, 11 and 12 respectively represent an exploded view of a spiro-orbital volumetric machine according to an example of the invention, as well as a schematic view of a Rankine cycle and a high temperature heat pump. according to the invention.
- the spiro-orbital volumetric machine (804, 850) has an outer body formed of two complementary hollow parts:
- a housing assembly (200).
- a movable hitch (300) which will be described in more detail in the following is integrally enclosed in the volume defined by the spiral cover assembly (400) and the housing (200).
- the spiral cover assembly (400) surrounds the expansion zone when it is an expansion machine, or compression when it is a compression machine, which extends from the port (19) inlet, respectively discharge, steam to the support of the axial abutment on the part fixed (220). This is the hottest part of the machine (804, 850).
- This zone includes in particular the fixed structure, also called fixed spiral (2), with which the mobile structure, also called mobile spiral (3), comes into contact. This contact is intended to guide the mobile spiral in its orbit movement.
- the housing (200) surrounds the machine area (804, 850) extending from the axial abutment support (220) to the end of the shaft (13).
- This zone comprises in particular a shaft (13) and a coupling device (500) of said machine.
- the movable hitch (300) comprises the shaft (13) and the members attached thereto:
- the hub (320) is eccentric relative to the shaft (13), ensuring that its movement is orbital;
- an anti-rotation ring (12) ensuring that the mobile spiral (3) does not rotate about the axis of its hub (320), while allowing the circular translation of the mobile spiral (3) in the transverse plane;
- the coupling device (500) of the machine consisting in particular of a toothed wheel (10) and a freewheel (30);
- bearings for example needle bearings, ball bearings or roller bearings.
- the working fluid (808) in vapor form enters the spiral cover assembly (400) via the vapor inlet port (19) at a temperature less than 250 ° C typically between 180 ° C and 235 ° C. This vapor is charged with lubricant.
- the lubricant travels in a known manner the entire Rankine circuit, driven by the working fluid (808).
- This working fluid (808) is for example composed of a mixture of ethanol, water, denaturant and lubricant.
- the percentage of water is between 0 and 20% by weight, preferably 4.5% of the mass (azeotrope).
- a denaturant for example an alkane, an alcohol, a ketone or a euro-denaturant (standardized mixture) between 1% by mass and more (euro-denaturant 2% by volume) to which lubricant is added.
- PAG polyalkylene glycol
- the working fluid (808) in vapor form arrives via an inlet connection or a flange provided on the center of the spiral cover assembly (400) and exits, in the example described, on the side by a flange. exhaust pipe (21) provided on the spiral cover assembly (400).
- the working fluid (808) in vapor form enters the spiral cover assembly (400) via the steam inlet flange (21). This steam is loaded with lubricant.
- This working fluid (808) comprises a main component such as a refrigerant R1336mzz (Z) or R1233zd (E), providing the thermodynamic cycle, charged with a liquid lubricant sprayed into the vapor phase of the main component.
- the lubricant is for example polyalkylene glycol (PAG) or polyolester (POE) miscible in the liquid phase with the other components.
- the compressed working fluid (808) is then admitted to a condenser (854), then to an expander (855) and finally to an evaporator (853) to be readmitted to the inlet of the compression machine (850) .
- Pressure and temperature sensors (860 and 861) may be implemented respectively at the input and at the output of the compression machine (850).
- the energy required to compress the working fluid (808) is achieved through a rotary machine (851), which may be an electric motor.
- the rotation of the shaft (813) of said machine is then transmitted to the compression machine (850) via a transmission (852), which can be effected by a pulley - belt connection.
- the transmission (852) may also be arranged between a seal (70) and a rear bearing (104), in a configuration similar to that shown in FIG. 11.
- Figures 2 and 3 respectively show an inner / outer perspective view of the spiral cover assembly and a longitudinal sectional view of the machine.
- the spiral cover (4) is made of cast iron, in particular a cast iron of lamellar graphite type resistant to ethanol.
- the part is made by casting in a mold and by machining the various orifices and cavities, then it can be the subject of a surface treatment by nitriding in a bath of salts followed by an oxidation phase, or alternatively d phosphate phosphating treatment of manganese.
- the outside of the spiral cover (4) has the central intake port (19) to which an inlet connection or flange can be connected.
- the stationary scroll (2) is pierced at its center (407) so that the working fluid in the form of pressurized vapor (808) admitted through the intake port (19) can access a central chamber (411) between the fixed spiral (2) and the movable spiral (3).
- the outside of the spiral cover (4) has an orifice for a speed sensor (54).
- the velocity information is taken by means of a Hall effect sensor, detecting the passage of a moving part, preferably the anti-rotation ring (12) or the mobile spiral (3).
- the outside of the spiral cover (4) has, on a side wall, an exhaust port surrounded by the flange (21) forming an annular receiving surface for receiving a seal.
- Two threads (412 and 413) allow to receive screws for fixing a flange of an exhaust duct.
- This flange (21) is located in the lower lower half of the expansion machine (804) when it is mounted on an associated rotary machine (801). Its exact position is determined according to the machine (801), to facilitate the purging of the stagnant working fluid (808) in the stationary machine and the connection to a condenser (805) of the Rankine cycle. Also, its orientation is preferably such that its orifice is oriented in a direction opposite to the rotating component of the flow of working fluid in the form of vapor (808) at the spiral outlet, and this in order to limit the exit of the oil carried by said vapor.
- the outside of the spiral cover (4) has, in parallel with its intake circuit, a bypass valve (59) intended, once actuated, to redirect the flow steam directly to a low pressure zone (817) via a volume (418) located behind the fixed scroll (2), without passing between the spirals (2 and 3).
- This branch circuit ensures in particular the purging of the working fluid (808) stagnant in the machine at a standstill.
- the outside of the spiral cover (4) also has several cylindrical bosses (404) oriented axially, receiving a tapping for fixing the fixed spiral (2).
- the outside of the spiral cover (4) also has a plurality of ribs (405), which provide rigidity of the bottom and prevent deformations resulting from the vapor pressure.
- the outside of the spiral cover (4) has one or more bosses (53) for positioning sensors, for example temperature or pressure sensors.
- the bottom of the spiral cover (4) has a cylindrical cavity (414) ensuring the centering of the fixed spiral (2) while the indexing in rotation is made using a shoulder screw or a pin ( 102).
- the fixed spiral (2) is held by screws (100). These screws (100) also make it possible to compress the high temperature flat gasket (6), which seals at the rear of the fixed spiral (2) between the central chamber (411) and the volume of the bypass circuit (418).
- the volume (415) inside the flat gasket (6) is loaded with high pressure steam, which makes it possible to reduce the flexing of the fixed scroll (2) subjected to pressure.
- the flat gasket (6) is made of expanded polytetrafluoroethylene, which allows it to perform its sealing function at high temperatures (up to 250 ° C) and at high pressures (up to 35 bar) . Its thickness is between 1 and 4 millimeters, and its compressibility is between 10 and 70%.
- the spiral cover (4) has inclined bores (402) for harvesting the oil from the vapor (808), which collects naturally on the walls by centrifugation.
- the oil collected via the bores (402) then circulates in bores (204) associated in a housing (5).
- the spiral cover (4) has the peripheral flange (401) for bolting, centering and sealing on a housing portion (200). Sealing is provided by an O-ring (74) whose properties are detailed in the description of the housing assembly (200).
- Figure 4 shows a front view of the fixed spiral (2) on the left and the mobile spiral (3) on the right, as well as several views of details.
- Figure 5 shows the positioning of the spirals during a vapor expansion cycle for 1 revolution of the expansion machine.
- FIGS. 13 and 14 respectively represent a perspective view of the specificities of the centers of each spiral, as well as views showing the role of these specificities at several stages of the vapor expansion cycle.
- FIGS. 16, 17 and 20 respectively represent a view of a variation of steam intake port shape, views detailing the operation of the exhaust ports of the spirals, as well as a sectional view of the central zone of the spirals.
- the radial guidance between the two spirals is said to be accommodating ("compiling" in English).
- the mobile spiral (3002) is indeed still in contact radially with the fixed spiral (2002) via the sealing points (416), visible in a step 601 of FIG. 5.
- Pressurized steam (808) is admitted into the central chamber (411) via the central bore in the fixed scroll (407).
- the pressure of this central chamber (411) pushes the mobile spiral (3), increasing the volume of said central chamber.
- the volume of this chamber (411) increases to a step 606 of Figure 5, where the central chamber (411) is split into two symmetrical chambers (419 and 420). The expansion then continues in these two symmetrical chambers (419 and 420) to the exhaust.
- the spiral profile extends over three and a half turns in order to obtain the optimum volume ratio between the volume just before the exhaust and the volume just after admission for the intended type of operation.
- the Spiral geometry (2 and 3) is adjusted according to the input parameters of the expansion machine (804). These parameters can be the pressure of the working fluid (808), its flow rate, its temperature, the type of fluid used or the speed of rotation of the expansion machine (804) in particular.
- spiral sealing segments (“tip-seal” in English) (17 and 18) are mounted in grooves provided for this purpose (408 and 308).
- These segments (17 and 18) are made of polyetheretherketone (PEEK), in a grade resistant to temperatures of over 250 ° C, with a thickness typically between 1 and 4 millimeters.
- the spirals (2 and 3) each have two studs (403 and 302) in contact with the anti-rotation ring (12).
- the tangential force of the mobile spiral (3) is transmitted to the anti-rotation ring (12) by its studs (302).
- the ring is locked in rotation by the fixed spiral (2) by means of two studs (403), it follows that the induced rotation of the mobile spiral (3) relative to the fixed spiral (2) is impossible .
- the studs (403 and 302) being positioned perpendicular to each other, it follows that the movement of the mobile spiral (3) is possible on the plane of the axial abutment (220) .
- the studs (403 and 302) have at their corners chamfers (311) of low angle, typically between 1 degree and 5 degrees, visible in the detail view B of Figure 4. These chamfers are intended to create an effect hydrodynamic beneficial for the lubrication of the sliding contact between the studs (403 and 302) of spirals and the anti-rotation ring (12).
- the mobile spiral (3) also has two additional studs (306), of lower height than the guide pads of the ring (302). These studs (306) make it possible to limit moving the anti-rotation ring (12) in the axial direction.
- the movable scroll (3) has a cavity (304) and a projection (305) for returning the center of gravity of the workpiece to the axis of its hub (320). This balancing eliminates inertial torque fluctuations of up to 50% of the maximum torque delivered by the machine.
- the fixed and movable spirals (2 and 3) have cavities (303 and 406). These cavities (303 and 406) are positioned in such a way as to increase the exhaust passage section without modifying the previously described volume ratio and have the effect of reducing the work consumed by the machine during the discharge phenomenon.
- FIG. 17 shows the operation of these cavities (406) at the moment of opening of the two last symmetrical chambers (423 and 424), that is to say close to step 601 as represented in FIG. 5: the vapor flow (808) then begins to escape through its "natural" opening (422) formed by the relative movement of the two spirals (2002 and 3002), but also by its openings formed by the spiral crenels (312) and the cavities (406).
- cavities (303 and 406) are symmetrical to form the same exhaust passage section for the two symmetrical chambers (423 and 424). These cavities (303 and 406) are broken down into a plurality of portions to provide "bridges" (425) for sealing segments (17 and 18) to be held in their grooves (308 and 408).
- the fixed and movable spirals (2002 and 3002) have notches (312) machined at the groove of the segment. These notches, visible on the detail C of FIG. 4 and in FIG. 17, are positioned so as to coincide with the cavities (303 and 406) during the discharge, and thus to increase the exhaust flow rate for the same purpose as the cavities (303 and 406).
- the exhaust flow is represented by arrows in FIG. 17.
- the notches (312) are machined in several parts to maintain the sealing rings (17 and 18) correctly in their grooves (308 and 408).
- Figure 18 shows the evolution of the forces generated by the steam (808) throughout a rotation of the expansion machine (804) according to the invention.
- the curves FT1 and FRI respectively designate the tangential and radial vapor force (808) applied to the mobile spiral (3) in the presence of cavities (303 and 406) as well as notches (312).
- the curves FT2 and FR2 respectively denote the tangential and radial vapor force (808) applied to the mobile spiral (3) without the presence of the cavities and crenellations.
- FIG. 18 shows that the presence of cavities (303 and 406) as well as notches (312) makes it possible to reduce by 40% the maximum amplitude of the radial vapor force (808) applied to the mobile spiral (3). In addition, this reduction causes a decrease in the variation of the sealing force between the mobile spiral (3) and the fixed spiral (2) and allows a better control of the flanks tightness while improving the fatigue strength of the materials. .
- FIG. 18 also shows that the presence of cavities (303 and 406) as well as notches (312) make it possible to increase the average tangential vapor force (808) applied to the mobile spiral (3). This increase results in an increase in the torque delivered by the expansion machine (804) involving a gain in efficiency of up to 2% depending on the pressure ratios applied to the input and output of the machine.
- the fixed and movable spirals (2 and 3) both have a nose fillet (410 and 309) at the foot of the central end of the spiral profile (usually called the spiral "nose").
- These leaves (410 and 309) whose radius is typically between 0.2 millimeters and 0.5 millimeters, are intended to reduce the stress concentration present on the nose, this place being generally the one for which the stresses are the most important. strong.
- the profile of the base of the nose has been enlarged to reduce the constraints to an acceptable level.
- the stress level was calculated around 100 MPa, which is acceptable in service life for cast iron spirals.
- steel spirals may have a thinner nose, and therefore have a better performance.
- this type of solution increases the cost of production of the machine.
- the fixed and movable spirals (2 and 3) both have a chamfer (421 and 318) in their central zone, at the top of their nose. These chamfers are intended to avoid any interference with the nose fillet (410 and 309) of the opposite spiral during the movement of the mobile spiral (3).
- the stationary scroll (2) has a centrally located cavity (409) extending axially from an intermediate plane (2003) to the front surface opposite the transverse disc end plate (2001) at the level of his nose.
- the movable scroll (3) also has a centrally located cavity (313) extending axially from an intermediate plane (3003) to the front surface opposite the transverse disc end plate (3001). at the level of his nose. As described in more detail below, these cavities (409 and 313) are used to ensure that the two symmetrical chambers are subjected to the same vapor pressure.
- Figure 14 shows sectional views of the central zone of the fixed scroll assembly (2) and movable spiral (3) on the three different stages (604, 606 and 607) of the expansion cycle of the machine (804).
- the cavity (313) of the mobile spiral (3) opens a communication channel (319) between the two symmetrical chambers (419 and 420).
- the cavity (409) of the fixed spiral (2) also makes it possible to open a communication channel (315) between the two symmetrical chambers (419 and 420).
- These two channels (314 and 315) make it possible to reduce the pressure difference between the two symmetrical chambers (419 and 420).
- the two symmetrical chambers (419 and 420) are ideally subjected to the same vapor pressure, since it is known that a pressure difference in the two symmetrical chambers (419 and 420) causes instability of the machine (804) during its operation. This increases noise and vibration levels during operation, and tends to reduce overall life.
- cavities (409 and 313) are located axially from intermediate planes respectively (2003, 3003) to front surfaces opposite the transverse disc end plates respectively (2001, 3001) at the noses of their spiral. in order not to reduce the size of the nose near the nose pads (410 and 309), in order to guarantee the mechanical strength of the spiral noses.
- the oblong hole (407) of the fixed spiral (2) is also located at a distance from the fillet (410) in order to avoid any stress concentration which is detrimental to the mechanical strength of the fixed spiral (2).
- the central bore (407) of the fixed spiral has an oblong shape.
- This shape, its precise positioning (angle, center) and the fact that this drilling is done partially in the material of the fixed spiral (2) have been determined in such a way as to optimize the input steam flow while maximizing the volume ratio of the trigger.
- the ideal form of this piercing is a form of "bean" (426) of the type shown in FIG. 16, however this type of shape proves difficult to machine industrially.
- a simple round hole is easier to perform, but also has lower performance: lower input rate and / or lower volume ratio.
- the mobile spiral (3) has, around its surface in contact with the abutment, a low angle chamfer (310), typically between 1 degree and 5 degrees, visible in the detail view D of FIG. chamfer (310) is intended to create a beneficial hydrodynamic effect for the lubrication of the sliding contact between the mobile spiral (3) and a washer (9) of the axial abutment.
- the transition between a rear face (317) of the mobile spiral (3) and the chamfer (310) is achieved through a fillet (316).
- the fixed (2) and movable (3) spirals are made of cast iron, in particular a cast iron of spheroidal graphite type resistant to ethanol.
- the parts are made by casting in a mold and by machining spiral profiles and different holes, and can be surface treated by nitriding in a bath of salts followed by an oxidation phase or alternatively phosphate phosphating treatment of manganese.
- the parts are made of steel which is or is not subjected to a treatment of the DLC type on at least its contact surface at the level of the spirals.
- Figures 3 and 6 respectively show a longitudinal sectional view of the machine and a view in perspective of the elements constituting the moving part of the relaxation machine.
- the anti-rotation ring (12) surrounds the mobile spiral (3). It is positioned so that the axial force induced by the pressure in the mobile spiral (3) is transmitted directly to the support of the axial stop (220).
- This ring is called "female - female” because it has grooves arranged perpendicularly to each other. This configuration allows the ring to axially bring together the two forces applied to it, namely the force applied by the studs (302) of the mobile spiral (3) and the reaction force applied by the studs (403) of the fixed spiral (2). The fact that these two forces are axially close has the effect of minimizing the buckling of the ring (12) under load.
- the mobile spiral (3) has the central hub (320) in which is housed a bearing (106).
- This hub contains an insulation cup (11).
- This cup (11) makes it possible to create a static vapor volume forming a thermal insulation at the place where the temperature of the mobile spiral (3) is highest.
- the cup (11) has holes to prevent the accumulation of liquid in the volume of insulation.
- the inertial contribution of the mobile spiral (3) to the sealing force is suppressed by means of the dynamic balancing carried out with the counterweight (14). ).
- This feature makes it possible to make the sealing force independent of the speed of rotation of the expansion machine (804).
- This feature is particularly important when the expansion machine (804) is connected to an associated rotary machine (801) whose rotational speed is variable.
- the tightness between the mobile and fixed (2 and 3) scrolls at low speed is improved, and the risk of damaging the high speed spirals is reduced.
- the link between the shaft (13) and the counterweight (14) is formed by means of the bulge (26), visible in FIG. 15.
- the crown (26) is fixed on the shaft (13) by the intermediate screw (27) and can alternately be hooped in its housing.
- the crown (26) has a slightly convexly adjusted surface (260) at the contact surface with the counterweight (14).
- This convex surface (260) has a radius of curvature of the order of one meter and allows the counterweight (14) to have a straight linear connection with the shaft (13).
- the line of contact between the crown (26) and the counterweight (14) makes it possible to reduce the hyperstatism of the expansion machine (804) and thus to suppress the transmission of the moment generated by the axial forces of steam (808) to the tree (13).
- the dimensions of the crown (26) may also be adapted to modify the effective offset of the eccentric crankpin (314) vis-à-vis the shaft (13), and thus to modify the sealing force between the two spirals ( 2 and 3).
- the crown (26) may advantageously be made by an insert to facilitate its realization, particularly when this piece will require a hardness and / or surface condition more restrictive than those of the shaft (13). It will thus be possible to assemble economically a curved (26) steel treated ground with a shaft (13) cast iron or steel directly from turning or milling.
- Figures 3 and 7 respectively show a longitudinal sectional view of the machine, a perspective view of the elements constituting the housing assembly in partial section.
- Figures 9 and 19 show respectively variants in the contact surface of the washer (9) and a variant of the washer (9) having an annular chamber against pressure.
- This set (200) consists of two main parts: the housing (5) and the PTO adapter (8) (PTO is the abbreviation of the term “Power Take-Off", equivalent to the French “Auxiliary Power Take”) ). These two parts are assembled through a bolted assembly which also allows to mount the housing assembly (200) on the spiral cover (4).
- Sealing and centering of the housing assembly (200) with the spiral cover is provided by a cylindrical flange (201) and the O-ring (74) disposed in an annular groove (229).
- This is a low-pressure zone at low temperatures relative to the rest of the machine, allowing the use of inexpensive elastomeric seals rather than high temperature resistant seals.
- the seal (74) like all other static seals of the machine, is a fluoroelastomer O-ring, for example VITON (trade name) or EPDM (ethylene-propylene-diene monomer).
- the sealing and centering of the housing part (5) with the PTO adapter part (8) is provided by a cylindrical centering (217) and an O-ring (72) disposed in an annular groove (228).
- the PTO adapter part (8) has fastening means (205) allowing the mounting of the expansion machine (804) on the associated rotary machine (801), for example at a power take-off, and in particular the rear power take-off, provided on the associated rotary machine (801).
- this fixing means can be adapted according to the interface available on the casing of the associated rotary machine (801).
- this attachment is made by bolting with ears (205). Sealing is provided by an O-ring (75) disposed in an annular groove (221).
- this fastening means (205) and the compactness of this part allow the machine to be partially inside the casing of the associated rotary machine (801), thereby reducing the visible external bulk of the machine ( 804).
- the housing assembly (200) has one or more shims (23) in the form of a housing flange (417).
- the thickness of this shim is adjusted in order to adjust the axial clearance between the fixed spiral (2) and the moving spiral (3), in order to reach a nominal clearance, for example 50 microns.
- This nominal axial clearance between the spirals (2 and 3) is calculated based in particular on the temperatures and operating pressures applied to the machine (804), but also on the rigidity of the high temperature flat gasket (6).
- the control of this axial clearance is essential especially since the machine (804) is designed to operate at high temperature (up to 250 ° C).
- This housing assembly (200) comprises an axial abutment support (220) containing the axial forces generated by the steam pressure on the mobile spiral (3).
- the friction exerted on this stop during the displacement of the mobile spiral greatly affecting the overall performance of the machine (804), a surface treatment is applied to one of the surfaces of the abutment, the side of the mobile spiral (3). ) or the housing (5), or both, to reduce the friction losses due to this contact.
- this treatment was not performed directly on the parts, but on a steel washer coated with a composite metal-polymer (9) (for example provided by the company Daido Metal, trade name DAIDYNE DDK05 ) or any other similar surface coating made in particular by a layer of PTFE (polytetrafluoroethylene) or any other Young's modulus material less than or equal to 5 GPa, of minimum thickness 50 ⁇ m deposited on a metal substrate allowing the mechanical attachment of soft material (PTFE or other) and the dissipation of heat.
- the washer (9) attached was attached to the abutment support (220) to reduce friction with the moving spiral (3). Alternatively, it may be fixed on the mobile spiral (3), or may not be fixed at all.
- the washer (9) greatly simplifies the process of making the surface treatment, which is difficult and expensive to perform on large parts.
- the washer (9) was fixed by means of rivets (105), but could be fixed by any other means (screws or pins for example) without this modifies its principle of use.
- the washer may be centered on its inside or outside diameter and stopped in rotation by a lug or a pin.
- a washer (9) having a thickness of flexible material (Young's modulus less than 5 GPa) and thickness of the order of 50 to 250 microns allows accommodation of the surface and facilitates the formation of a "wedge of oil" on the inner edge of the surface (211).
- the layer of flexible material also allows a certain accommodation over its entire flat surface, it may advantageously be used raw, without the need for rework or rectification that would have been necessary to achieve an acceptable level of flatness if the piece had been made of metal or coated with a thin deposit.
- the washer (9) abutment may have on its face subject to friction several depressed areas (222) distributed substantially homogeneously.
- these areas in depression - or pockets - (222) are substantially circular and have a small depth in front of their diameter, typically 30 to 100 ym deep.
- the pockets (222) have a radius preferably less than the eccentricity of the orbital trajectory of the mobile spiral (3) which promotes the renewal of the oil in the cavity and on the opposite face thanks to the kinematics of the spiral mobile (3).
- the minimum distance between adjacent pockets (222) may be substantially less than or equal to an orbit diameter, and chosen to ensure a ratio (pocket area / stop surface) of between 20% and 50%.
- the pockets (222) are made on the face of the abutment equipped with the washer (9) reported in polymer, and their depth is less than or equal to the thickness of the polymer layer, which makes their realization more economical and especially ensures a connection between pockets and non-aggressive flat part for the opposing part.
- the pockets (222) can be interconnected by communication channels (214) of small width in order to promote the renewal of the oil they trap, and thus prevent the heating of the interface, in particular on machines having to operate at high rotational speeds and / or having a radially extended axial abutment (for example when the abutment width is greater than six times the eccentricity of the orbital motion of the movable spiral).
- the channels (214) connecting the adjacent pockets will be arranged to allow, step by step, a circulation of the oil between the inner diameter and the outer diameter of the thrust washer (9); advantageously the channels (214) will be arranged in the tangential direction, in the favorable direction vis-à-vis the movement of the mobile spiral (3).
- Said tangential direction is oriented so that the channels (214) are perpendicular to the direction of instantaneous displacement of the mobile spiral (3) at the point where the axial stop is the most loaded.
- Said channel orientation (214) and the direction of movement of the movable scroll (3) are shown in Fig. 9.
- Radial grooves (212) may also be made on the surface of the thrust washer (9), to facilitate the supply of the oil contact and reduce the power dissipated by shearing the oil film.
- the depth of these striations is comparable to the previously presented pouches (222).
- the number of striations, their orientation and their width can be adapted according to various parameters, such as the type of fluid used or the type of oil used.
- An annular groove (223) may be provided on the active face of the metal-polymer washer (9) in the thickness of the polymer, defining one or more annular chambers (223) between the rear face of the mobile spiral (3) and the thrust washer (9) as shown in Fig. 19.
- This annular chamber (223) is supplied with working fluid (808) at a higher pressure than the ambient pressure of the abutment by one or more holes (225) opening in the bottom of the mobile spiral (3), and thus applies a selected pressure - by the position of the bore - to compensate for a part of the effort axial to which is subjected the mobile spiral (3) due to the pressure distribution in the spirals (2 and 3).
- This pocket (223) is dynamically sealed on its edges (226) thanks to the accommodation capacity of the polymer, the seal being further improved by the presence of the oil in the working fluid (808).
- the seal obtained is all the more effective as the axial pressure force is important, because of a crushing of the more pronounced polymer.
- the assembly achieves a reduction in the net axial force passing between the mobile spiral (3) and the abutment support (220) via the polymer abutment washer (9), in order to reduce the local heat dissipation of it and improve the performance of the machine (804).
- the metal-polymer washer (9) can be installed on the fixed support (220), in this case the chamber (223) comprises at least locally an extension (224) of dimension substantially close to the orbit diameter, in order to be fed continuously by the bore (225) arranged in the mobile spiral (3).
- several holes (225) in the mobile scroll can feed several extensions (224), allowing said extensions to have a more limited dimension, in particular less than an orbit diameter, without interruption of the pressure supply of the room (223).
- the washer (9) By its implantation in the fixed support, the washer (9) will be subjected to a lower temperature and will be cooled by conduction to the fixed support (220).
- the metal-polymer washer (9) can be installed at the rear of the mobile spiral (3), the annular chamber can thus have a limited and constant radial extent, which is favorable vis-à-vis the length the escape path between the chamber (223) and the pressure of the surrounding chamber (817).
- the axial abutment support (220) is formed on an annular ring-shaped ring (210).
- the diameter of this tee (210) and its thickness has been calculated so that the bending of the abutment support (220) in the axial direction conforms to the bending of the mobile spiral (3) when the spirals (2 and 3) are under pressure.
- This allows the contact pressure on the thrust washer (9) to remain homogeneous and to avoid any stress peak on its inner circumference (in the case where said annular ring is too rigid) or external (in the case where said spiral is too rigid).
- the surface of the thrust washer (9) is flat, in order to minimize the contact pressures.
- the inner edge of this surface (211), as well as the edges of the mobile spiral end stop surface (3), visible in FIG. 4, have a chamfer (310) with a very small angle, typically between 1 degree and 5 degrees. This chamfer allows the oil to be distributed on the surface, and creates a beneficial hydrodynamic effect for the lubrication of the contact between the moving spiral (3) and the axial abutment washer (9).
- the transition between the flat rear portion (317) of the abutment and this chamfer (310) mobile spiral side (3) is achieved through a fillet (316).
- the bottom of the casing (5) also has a central shaft outlet whose inner tubular surface is machined to receive the bearing (103), the shaft end seal (71) and possibly the second end seal. tree (70).
- An annulus (202) between the shaft end seals (70, 71) provides a vent chamber (202) to prevent contamination by the working fluid contained in the associated rotary machine ( 801) on which the expansion machine (804) is mounted.
- This chamber (202) is pierced by a vent (203) opening outwards, in the lower part of said annular chamber (202), when the machine is mounted on a motor, to allow the evacuation of any leaks from fluid (Work fluid (808), or possibly fluid present in the associated rotary machine (801).
- the seals (70, 71) are annular lip seals, the lips being oriented in opposite directions to the chamber (202) to promote sealing of the machine (804) relative to the working fluid (808) of a part and sealing against the fluids present in the associated rotary machine (801) on the other hand.
- the chamber (202) forms a fluid recovery volume to evacuate to the outside, and prevent contamination between the two machines (804 and 801).
- These lip seals could be replaced by any other dynamic sealing device (seals with mechanical seal for example) without this modifying the principle of the invention.
- the seal (71) is made of polytetrafluoroethylene (PTFE), for example a lip seal marketed under the reference BEKA 804 or BEKA 806 by the company FranceJoint (trade names).
- PTFE polytetrafluoroethylene
- Figures 3, 8 and 11 respectively show a longitudinal sectional view of the machine, a perspective view of the elements constituting the coupling assembly in partial section and a schematic view of a Rankine cycle according to the invention. .
- a Rankine cycle recovers waste heat from an associated rotary machine (801), which may be an internal combustion engine or an electric machine. This heat can be recovered in several places: on the cooling circuit, on the cooling of the compressed air upstream of the engine, on the cooling of the exhaust gases. recirculated in the rotary machine or on the exhaust gas (802) as shown in FIG. 11.
- a heat exchanger (807) is inserted in bypass on the exhaust line after the pollution control system (803).
- a bypass valve (827) proportionally distributes the flow rates between the heat exchanger (807) and the normal exhaust.
- the exchanger (807) is an evaporator for evaporating the working fluid (808) of the Rankine cycle.
- the working fluid (808) is drawn by the pump (806) from a pressure expansion tank (828) controlled by an electric valve (829).
- the proportional electric valve (829) regulates the air pressure in the expansion vessel (828) either by connecting the expansion tank to a source of compressed air (821) or by connecting the expansion tank ( 828) to the atmosphere.
- the temperature and pressure of the working fluid (808) upstream of the pump (806) and downstream of the evaporator (807) are measured by sensors.
- the Rankine cycle calculator receives these signals to control the actuators of the system and a temperature of the vapor in the expansion machine (804) measured either in the expansion zone (816) or in the exhaust zone ( 817).
- the vapor produced in the evaporator (807) flows to the expansion machine (804).
- the expansion machine (804) comprises three zones: an inlet zone (814) of the high-pressure steam which is connected to the expansion zone (816), itself connected to the exhaust zone (817). ) at low pressure.
- the bypass valve (59) opens and closes a bypass channel connecting the intake zone (814) and the exhaust zone (817).
- the bypass valve (59) is advantageously pneumatic and is connected to the source of compressed air (821).
- An electric valve (820) controls the admission of air into the bypass valve (59) either by connecting the bypass valve to the source of compressed air (821) or by connecting the bypass valve (59) to the atmosphere.
- the bypass channel or bypass valve (59) further comprises a restriction, typically of the order of 20 mm 2 in order to limit the volume flow through the bypass channel and to cause a rise in pressure of the zone upstream of the the restriction.
- the condenser (805) is cooled either by a fluid of the associated rotary machine (801) or by ambient air. For example, one or more of the cooling circuits of the associated rotary machine (801) may be used.
- the condensed working fluid then returns to the expansion vessel (828).
- a coupling area (99), including the coupling assembly (500) and the rear bearing (104), is isolated from the working fluid (808) via the end seal (71). 'tree.
- This particular arrangement allows the elements located in the coupling zone (99) to have a lubricating means independent of the lubrication system of the volumetric machine (804). This arrangement also limits the area containing the working fluid (808) and ensures maximum compactness of the machine (804).
- the expansion machine (804) is connected to a rotating shaft (813) of the associated rotary machine (801).
- the coupling assembly (500) makes it possible to connect the shaft (13) of the expansion machine (804) to the shaft (813) of the associated rotary machine (801).
- the coupling assembly (500) is not limited to the example shown and may be constituted by other coupling means, for example a combination of the following elements: free wheel, clutch of any type, shock absorber vibration, gear, pulley, belt.
- This assembly (500) is located in the PTO adapter (8), but is isolated from the ethanol vapor by the seal (71) of tree end.
- the positioning inside the casing of the associated rotary machine (801) allows this assembly to benefit from a means of lubrication independent of the working fluid (808).
- This assembly (500) is to be adapted according to the associated rotary machine (801) on which the machine (804) is mounted.
- the geometry of the toothed wheel (10), in particular, must be modified according to the machine (801) used.
- This assembly (500) consists in particular of a toothed wheel (10) disposed around the central shaft (13), for transmitting the mechanical power generated by the machine (804) to the associated rotary machine (801).
- the speed ratio between the machine (804) and the associated machine (801) is fixed and is typically between 1 and 6.
- This assembly (500) consists in particular of a freewheel (30).
- the freewheel (30) is cams, but it can indifferently be designed according to another technology (free wheel roller for example).
- This freewheel is, in the example described, implemented between the shaft (13) and the inside of the toothed wheel (10).
- This freewheel (30) acts as a clutch for the machine (804). Indeed, when the steam pressure is not sufficient to cause rotation of the shaft (13), the freewheel allows the associated rotary machine (801) to rotate without driving the machine (804) (free wheel bandwidth).
- This assembly (500) is constituted in particular by one or more bearings (31 and 32), making it possible to take up the axial and radial forces induced by the toothed wheel (10).
- bearings (31 and 32) are constituted in particular by one or more bearings (31 and 32), making it possible to take up the axial and radial forces induced by the toothed wheel (10).
- FIGS. 3, 6, 10 and 15 respectively represent a longitudinal sectional view of the machine, a view of the partially cutaway moving part, a longitudinal sectional view of the machine with arrows indicating the direction of the oil flows, and a view of the rotating parts of the machine
- the expansion machine (804) uses at least two lubrication sources.
- the first source of lubrication comes from the oil contained in the working fluid in the form of steam, this oil can be used to lubricate in particular the contacts of the anti-rotation ring (12), the axial thrust washer (9), the shaft end seal (71), the crown (26) and the bearings (103 and 106). Since a part of the machine is mounted directly inside the casing of the associated rotary machine (801), the elements situated in the coupling zone (99) have an independent lubrication means, which can come from the oil used in the casing of the associated rotary machine (801). In this case, the oil flows associated with these two sources of lubrication are represented by black arrows in FIG. 10 for the flow of oil from the working fluid (808), and by gray and black arrows for the oil flow from the casing of the associated rotary machine (801).
- the elements located in the coupling zone (99) may also have a lubricating means independent of the associated rotary machine (804), for example by a permanent lubrication.
- the working fluid in vapor form (808) at the spiral outlet is charged with oil and circulates with a rotating component. This circulation leads to a centrifugal force tending to drive the oil particles towards the inner wall of the spiral cover (4).
- Slide links the anti-rotation ring (12) and a part of the axial stop (220) are supplied with oil by this direct flow.
- the oil is then sensed by the inclined holes (402), then passes through inclined holes in the housing (204) to the annular volume (207), allowing the oil to lubricate the shaft end seal (71). ) and the bearing (103).
- the oil-laden working fluid (808) When the oil-laden working fluid (808) is in the inner volume (141) of the counterweight, it is driven by a rotational movement which projects the oil, heavier than the working fluid, against the walls. (142) of said counterweight (14) by centrifugation. The oil adheres to the walls (142) by capillarity and is then driven by the rotational movement of the counterweight (14) into cavities (140). These cavities have a tangential ramp (143) to facilitate entry and a wedge (144) for oil to accumulate in the cavities (140). The progressive filling of the cavities (140) pushes the oil axially until it is projected on the rear face (317) of the mobile spiral (3).
- the counterweight acts as an oil separator of the working fluid (808) which is then discharged from the interior (141) of the counterweight to the volume (208) and thereafter through radial bores (209).
- the shaft end bearing (104) and the elements constituting the coupling assembly (500) are implemented in the coupling zone (99), which can be implemented inside the machine housing. associated rotator (801).
- the lubricating means of the elements of this zone (99) being independent of the working fluid (808), they can therefore be lubricated by the oil mist present in the casing of the rotary machine (801), the flow being moreover forced by the rotation of the toothed wheel (10).
- the elements of said zone (99) can be lubricated by a permanent lubrication.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1762225A FR3075251B1 (en) | 2017-12-15 | 2017-12-15 | VOLUMETRIC MACHINE WITH SPIRALS |
PCT/FR2018/052855 WO2019115897A1 (en) | 2017-12-15 | 2018-11-15 | Scroll-type positive-displacement machine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3724506A1 true EP3724506A1 (en) | 2020-10-21 |
Family
ID=61132727
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18819531.7A Withdrawn EP3724506A1 (en) | 2017-12-15 | 2018-11-15 | Scroll-type positive-displacement machine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3724506A1 (en) |
FR (1) | FR3075251B1 (en) |
WO (1) | WO2019115897A1 (en) |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59185885A (en) * | 1983-04-06 | 1984-10-22 | Nippon Soken Inc | Scroll type hydraulic machine |
US5944500A (en) * | 1996-06-20 | 1999-08-31 | Sanden Corporation | Scroll-type fluid displacement apparatus having a strengthened inner terminal end portion of the spiral element |
JP2003049785A (en) * | 2001-08-06 | 2003-02-21 | Mitsubishi Heavy Ind Ltd | Scroll type fluid machine |
JP3919631B2 (en) * | 2002-08-13 | 2007-05-30 | 株式会社ケーヒン | Scroll compressor |
-
2017
- 2017-12-15 FR FR1762225A patent/FR3075251B1/en not_active Expired - Fee Related
-
2018
- 2018-11-15 WO PCT/FR2018/052855 patent/WO2019115897A1/en unknown
- 2018-11-15 EP EP18819531.7A patent/EP3724506A1/en not_active Withdrawn
Also Published As
Publication number | Publication date |
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FR3075251A1 (en) | 2019-06-21 |
WO2019115897A1 (en) | 2019-06-20 |
FR3075251B1 (en) | 2019-11-08 |
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