EP2806164B1 - Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale - Google Patents

Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale Download PDF

Info

Publication number
EP2806164B1
EP2806164B1 EP13168729.5A EP13168729A EP2806164B1 EP 2806164 B1 EP2806164 B1 EP 2806164B1 EP 13168729 A EP13168729 A EP 13168729A EP 2806164 B1 EP2806164 B1 EP 2806164B1
Authority
EP
European Patent Office
Prior art keywords
spiral
scroll compressor
displacement
compressor according
counter
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.)
Active
Application number
EP13168729.5A
Other languages
German (de)
English (en)
Other versions
EP2806164A1 (fr
Inventor
Frank Obrist
Oliver Obrist
Christian SCHMÄLZLE
Christian Busch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Obrist Engineering GmbH
Original Assignee
Obrist Engineering GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Obrist Engineering GmbH filed Critical Obrist Engineering GmbH
Priority to EP13168729.5A priority Critical patent/EP2806164B1/fr
Priority to US14/282,509 priority patent/US9512840B2/en
Priority to JP2014104948A priority patent/JP6425417B2/ja
Priority to CN201410216902.9A priority patent/CN104179682B/zh
Publication of EP2806164A1 publication Critical patent/EP2806164A1/fr
Application granted granted Critical
Publication of EP2806164B1 publication Critical patent/EP2806164B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • 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
    • 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
    • F04C18/0253—Details concerning the base
    • 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
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)
    • 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

Definitions

  • the invention relates to a scroll compressor for a CO 2 vehicle air conditioning system, and a CO 2 vehicle air conditioning system with such a scroll compressor.
  • Non-combustible refrigerants are used for the air conditioning of motor vehicles in order to avoid the risk of explosion inside the vehicle in the event of an accident.
  • the refrigerants used so far are either already banned or at least classified as problematic because of their high global warming potential.
  • CO 2 non-combustible refrigerant
  • CO 2 air conditioners operate with high operating pressures, which make special demands on the strength and tightness of the system components. The advantage associated with the high operating pressure is that the higher density of CO 2 requires a smaller volume flow to provide a relatively high refrigeration capacity.
  • a scroll compressor for a CO 2 vehicle air conditioner is off JP 2006/144635 A known.
  • a scroll compressor with the features of the preamble of claim 1 is made US 2009/0098001 A1 known.
  • Such scroll compressors have variable speed electric drives to control the cooling capacity of the compressor.
  • US 6,273,692 B1 a scroll compressor with a mechanical drive, which is connectable by an electromagnetic clutch to the compressor unit.
  • US 2002/0081224 A1 discloses a variable low-pressure scroll compressor which can be switched on and off by a radial movement of one of the two scroll spirals. In this case, the eccentricity between the two scroll spirals is released, which thus get out of engagement in the radial direction.
  • the invention has for its object to provide a scroll compressor for a CO 2 vehicle air conditioner, which is simple and improved in view of the tightness.
  • the invention is also based on the object of specifying a CO 2 vehicle air conditioning system with such a scroll compressor.
  • the object is achieved by a scroll compressor for a CO 2 vehicle air conditioner with the features of claim 1.
  • the object is achieved by the subject matter of claim 11.
  • the invention is suitable for variable speed or digitally controlled scroll compressors.
  • the invention has the advantage that tilting moments which act on the displacement spiral are reduced, thereby achieving a uniform contact pressure of the displacement spiral.
  • the uniform pressure leads to the fact that at each contact point between the two spirals substantially the same tightness prevails.
  • the invention provides that the eccentric bearing is arranged in the displacement between the positive displacement spiral and the counter-spiral and has a bearing bush, which is integrally formed with the positive displacement spiral and whose bottom is aligned with the end face of the turns of the positive displacement spiral.
  • the eccentric bearing is recessed in the VerdrDeutscherspirale in the direction of the pressure chamber, wherein the eccentric bearing is at least partially equal to the turns of the counter-spiral.
  • the eccentric bearing so at least partially immersed in the counter-spiral. That in the known low-pressure scroll compressors used for final compression innermost volume between the displacement spiral and the counter-spiral is at least partially used to accommodate the eccentric bearing. As a result, lever lengths and tilting moments are effectively reduced, because the immersion depth of the eccentric bearing is particularly large.
  • the invention also has the advantage that the suction side is securely separated from the high pressure side, because the bearing bush is formed integrally with the positive displacement spiral. Thus, no seals between the eccentric and the positive spiral are required.
  • the bushing participates in the compression, because this one hand is in the displacement and on the other hand, the bottom of which is aligned with the end face of the turns of the positive displacement spiral.
  • the bearing bush in the circumferential direction cooperates with the turns of the counter-spiral and in the axial direction with a sealing surface of the counter-spiral.
  • any tilting moments are further reduced if the displacement spiral has a central recess in which at least partially a counterweight is accommodated, which is connected to the eccentric bearing.
  • the surface of the eccentric bearing is smaller than the central area within the innermost turn of the counter-spiral such that at least one gas ejection opening formed in the region of the central area is accessible for fluid communication with the pressure chamber. This avoids that the gas ejection opening is covered by the recessed eccentric bearing.
  • a further improvement of the tightness is achieved when the turns of the positive displacement spiral and the counter-spiral each have lubricating bevels.
  • Lubricants can accumulate in the lubricating surfaces, which improves the sliding properties and reduces local resistance forces, so that there is a uniform contact pressure and thus a good seal between the two spirals. If the lubricating bevels are formed at both outer edges of each of the turns of the positive displacement spiral and the counter-spiral, good lubrication in both directions takes place in the reciprocal movement of the positive displacement spiral.
  • the lubricating chamfers and / or a radius are formed in the corners between the turns and a sealing surface of the displacement spiral.
  • the lubricating chamfers and / or a radius may be formed in the corners between the turns and a sealing surface of the counter-spiral.
  • the gullies or radii in the corners preferably cooperate with the gullies on both outer edges of each of the turns of the positive displacement spiral and the counter-spiral. As a result, the sealing effect in the region of the respective gas chamber or gas pocket is improved, which is formed by the radial contact between the displacement spiral and the counter-spiral.
  • the tightness can be improved if a closed to the suction side receiving space for the eccentric bearing fluidly connected to the pressure chamber and a rear wall of the positive displacement spiral can be acted upon by a contact pressure.
  • the distance between the center of the counter-spiral and the center of the displacement spiral maximally 1.5 mm, in particular at most 1.2 mm, in particular at most 1.0 mm, in particular maximally 0.8 mm, in particular maximally 0.6 mm, in particular maximally 0.4 mm, in particular not more than 0.2 mm.
  • the lower limit can be 0.1 mm.
  • the counter-spiral has a winding angle of 660 ° to 720 °, in particular from 680 ° to 700 °, whereby a sufficient compression of the refrigerant is achieved.
  • the volume of the pressure chamber by a factor of 5-7, in particular by a factor of 6, greater than the suction volume per revolution of the displacement spiral, whereby gas pulsations are effectively reduced.
  • the scroll compressor described in detail below is designed for use in a CO 2 vehicle air conditioning system which typically includes a gas cooler, an internal heat exchanger, a throttle, an evaporator, and a compressor. Such systems are designed for maximum pressures over 100 bar.
  • the compressor is a scroll compressor, also referred to as a scroll compressor.
  • the scroll compressor has a mechanical drive 10 in the form of a pulley.
  • the pulley may be connected in use to an electric motor or an internal combustion engine.
  • the scroll compressor further includes a housing 30 having a housing cover 31 which closes the high pressure side of the compressor and is bolted to the housing 30.
  • a housing intermediate wall 32 is arranged, which limits a suction chamber 33.
  • a passage opening is formed, through which a drive shaft 11 extends.
  • the outside of the Housing 30 arranged shaft end is rotatably connected to a driver 35 which engages in the rotatably mounted on the housing 30 pulley, so that a torque can be transmitted to the drive shaft 11 of the pulley.
  • the drive shaft 11 is rotatably mounted on the one hand in the housing bottom 34 and on the other hand in the housing intermediate wall 32.
  • the sealing of the drive shaft 11 against the housing bottom 34 is effected by a first shaft seal 36 and against the housing intermediate wall 32 by a second shaft seal 37.
  • the drive shaft 11 transmits the torque to a compressor unit, which is constructed as follows.
  • the compressor unit comprises a movable displacement spiral 13 and a counter-spiral 14.
  • the displacement spiral 13 and the counter-spiral 14 engage each other.
  • the counter-spiral 14 is fixed in the circumferential direction and in the radial direction.
  • the coupled with the drive shaft 11 movable displacement spiral 13 describes a circular path, so that in a conventional manner by this movement several gas pockets or gas chambers are generated, which migrate radially between the displacement spiral 13 and the counter-spiral 14.
  • refrigerant vapor is sucked into the open outer gas chamber and compressed with the further spiral movement and the concomitant reduction of the gas chamber.
  • the refrigerant vapor is increasingly compressed linearly from radially outward to radially inward direction and expelled in the center of the counter-spiral 14 into a pressure chamber 15.
  • an eccentric bearing 12 is provided, which is connected to the drive shaft by an eccentric pin 38 (s. FIG. 2 ).
  • the eccentric bearing 12 and the displacement spiral 13 are arranged eccentrically with respect to the counter-spiral 14.
  • the gas chambers are separated from each other pressure-tight by conditioning the Verdrticianerspirale 13 on the counter-spiral 14.
  • the radial contact pressure between the displacement spiral 13 and the counter-spiral 14 is adjusted by the eccentricity.
  • the eccentricity results from the distance x between the center of the counter-spiral and the center of the displacement spiral (s. FIG. 6 ).
  • the distance x may preferably be in a range from 0.1 mm to 1.5 mm, in particular from 0.1 mm to 1.0 mm, in particular from 0.1 mm to 0.8 mm, in particular from 0.1 mm to 0.6 mm, in particular from 0.1 mm to 0.4 mm, in particular from 0.1 mm to 0.2 mm.
  • a rotational movement of the displacement spiral is avoided by a plurality of guide pins 39, which, as in FIG. 2 shown, are mounted in the intermediate wall 32.
  • the guide pins 39 engage in corresponding guide bores 40 which are formed in the displacement spiral 13.
  • a counterweight 28 is connected, preferably in one piece, to the eccentric bearing 12 to compensate for the imbalance caused by the orbital motion of the displacer coil 13.
  • the eccentric bearing 12 is recessed in the positive displacement spiral 13 in the direction of the pressure chamber 15.
  • the eccentric bearing 12 is thus at least partially equal to the turns of the counter-spiral 14.
  • the eccentric bearing 12 is disposed in the displacement between the displacement spiral 13 and the counter-spiral 14.
  • the eccentric bearing 12 has a pin 58 which is rotatably arranged in a bearing bush 26.
  • the bearing bush 26 is designed in one piece or in one piece with the displacement spiral 13.
  • the bushing 26 and the pin 58 may be made of the same material, for example. From bronze.
  • the bearing bush 26 and thus also the pin 58 are arranged at the same height as the turns of the two spirals 13, 14 and thus dive into the counter-spiral 14.
  • the outer wall of the bearing bush 26 forms part of the winding of the displacement spiral 13 and cooperates with the counter-spiral 14 for compressing the gas.
  • the axial sealing takes place through the bottom 58 of the bearing bush 26, which is aligned with the end face of the turns.
  • the end face and the bottom 58 are aligned parallel to the sealing surface 59 of the counter-spiral 14 and seal against them in the axial direction (s. Fig. 4 ).
  • the structure of the eccentric bearing 12 is in cross section in FIG. 6 shown.
  • the winding of the displacement spiral 13 widens towards the center.
  • the widened inner part of the displacement spiral 13 receives the pin 58 and integrally forms the bearing bush 26 in which the pin 58 rotatably seated.
  • the surface of the eccentric bearing 12 is smaller than the central surface 55 within the innermost turn of the counter-spiral 14.
  • the surface of the eccentric bearing 12 corresponds to the surface of the bottom 54 of the bearing bush 26. This ensures that formed in the region of the central surface 55 gas ejection port (not shown) for the fluid connection with the pressure chamber 15 is accessible.
  • lubricating lands 56 are formed complementary to the lubrication lands 56 at the outer edges of the turns.
  • the complementary lubricating bevels 56 may have the same angle. It is also possible that the lubricating bevels 56 in the corners have a shallower angle than the lubricating bevels 56 at the outer edges.
  • the corners may have radii 57 which are so large that they accommodate the associated lubricating bevels 56 at the outer edges (see FIG. Fig. 9 ).
  • FIGS. 1 . 2 shown scroll compressor is clutchless.
  • the scroll compressor is switched on and off (digital circuit).
  • the counter-spiral 14 in the axial direction ie in a direction parallel to the drive shaft 11 is alternately movable.
  • the displacement spiral 13 is fixed in the axial direction.
  • the counter-spiral 14 can be lifted from the displacement spiral 13 in the axial direction, as in the FIGS. 1 to 3 shown.
  • a pressure equalizing gap 41 is created between the displacement spiral 13 and the counter-spiral 14, which connects the gas chambers, which are separated from each other in the radial direction, between the displacement spiral 13 and the counter-spiral 14.
  • the sliding surface 42 is machined and seals against the counter-spiral 14.
  • the rear wall 21 of the counter-spiral 14 forms the bottom of the pressure chamber 15.
  • the counter-spiral 14 therefore closes directly with the pressure chamber 15.
  • the rear wall 21 also has a flange 22, in particular an annular flange 22, which rests against the sliding surface 42 of the pressure chamber 15.
  • the flange 22 serves as an axial guide of the counter-spiral 14 in the pressure chamber 15.
  • On the outer circumference of the flange 22, a groove with a sealing means, for example a sealing ring 43 is formed.
  • the pressure chamber 15 is bounded by a peripheral wall 44 which forms a stop 45 and limits the axial movement of the counter-spiral 14.
  • the pressure chamber 15 is provided in the housing cover 31. As a result, the assembly of the axially movable counter-spiral 14 is simplified. In addition, it has a rotationally symmetrical cross section.
  • axial force For the alternating movement of the counter-spiral 14 between the open position ( FIG. 3 ) and the closed position ( FIG. 4 ) opposite axial forces are required.
  • the spring 16 may be formed, for example, as a plate spring.
  • the spring 16 is in the closed position according to FIG. 4 biased and urges the counter-spiral 14 and the displacement spiral 13 apart.
  • the spring 16 is disposed opposite to the pressure chamber 15.
  • a central recess 46 is provided in the counter-spiral 14, in which the spring 16 is arranged.
  • the spring 16 is supported on the displacement spiral 13.
  • the bearing bush 26 of the eccentric bearing 12 is recessed in the VerdrDeutscherspirale 13.
  • the bearing bush 26 dips into the counter-spiral 14 and protrudes into the counter-spiral 14.
  • the bottom of the bearing bush 26, on which the spring 16 is supported is at the same height as the inner edges of the turns of the displacer spiral 13. This is well in FIG. 3 to recognize (open position). In the closed position according to FIG. 4 Therefore, the bottom of the bearing bush 26 abuts against the counter-spiral 14 and seals the innermost gas chamber between the displacement spiral 13 and the counter-spiral 14.
  • a piston 17, in particular an annular piston 17 is provided which is coaxial with the longitudinal axis of the counter-coil 14 slidably.
  • annular piston 17 a plurality of arranged on the circumference of the counter-spiral 14 cylindrical piston can be provided.
  • the annular piston 17 engages the rear wall 21 of the counter-spiral 14 and acts on it with a closing force which operates against the spring force of the spring 16.
  • the piston 17 engages, as in the FIGS. 1 to 4 to recognize, in addition to the pressure chamber 15 to the counter-coil 14 at.
  • the piston 17 is thus arranged outside the pressure chamber 15 or generally eccentrically.
  • a simple outlet opening may be formed in the counter-spiral 14 (not shown).
  • the annular piston 17 has a pressure ring 47, which is connected to a bottom 48 of the piston.
  • the piston head 48 is axially displaceable and pressure-tight in an axial guide 18.
  • the axial guide 18 is formed as an annular chamber.
  • the annular chamber with a Supply terminal 20c connected.
  • the supply port 20c is connected to a 2/3-way valve, which in turn is connected to a high pressure port 20a and a suction pressure port 20b, so that the annular chamber can be acted upon alternately with high pressure or suction pressure.
  • the counter-spiral 14 can be alternately moved back and forth between the open position or the closed position.
  • the annular piston 17 operates substantially only against the spring force of the spring 16, because the pressure prevailing in the pressure chamber 15 and acting on the counter-spiral 14 pressure is at least partially compensated by the pressure acting between the counter-spiral 14 and the displacement spiral 13 during compression.
  • only relatively small strokes are required to adjust the pressure equalizing gap 41. For example, stroke ranges of about 0.3 to 0.7 mm, in particular a stroke of about 0.5 mm.
  • the power control takes place in the scroll compressor by switching on or off the compressor power, specifically by changing the frequency of the cyclic or alternating movement of the counter-spiral 14th
  • the compressed gas collected in the pressure chamber 15 flows through an outlet 49 from the pressure chamber 15 into an oil separator 29, which in the present case is designed as a cyclone separator.
  • the compressed gas flows through the oil separator 29 and a check valve 19 in the circuit of the air conditioner.
  • the check valve 19, which prevents the compressed gas from flowing back into the scroll compressor which is switched off, is designed, for example, for pressure differences of 0.5 to 1 bar.
  • a receiving space 24 also referred to as a backpressure space ( FIG. 1 ), in which a part of the counterweight 28 and the eccentric bearing 12 are arranged, fluidly connected to the high pressure side.
  • the receiving space 24 is bounded by the rear wall 25 of the compressor spiral 13 and the housing intermediate wall 32.
  • the receiving space 24 is fluid-tightly separated from the suction space 33 by the second shaft seal 37 described above.
  • a sealing and sliding ring 52 is disposed between the displacement spiral 13 and the housing intermediate wall 32 and seals the receiving space 24 against the high pressure side.
  • the sealing and sliding ring 52 is seated in an annular groove in the housing intermediate wall 32. Between the housing intermediate wall 32 and the displacement spiral 13, a gap is formed (not shown).
  • the displacement spiral 13 is therefore not supported in the axial direction directly on the housing intermediate wall 32 but on the sealing and sliding ring 52 and slides on this.
  • the sealing and sliding ring 52 protrudes from the annular groove and seals the gap.
  • the gap can be about 0.2 mm to 0.5 mm wide.
  • a line 50 connects the oil separator 29 with the receiving space 24. This extends through the housing cover 31, the counter-spiral 14 and the intermediate wall 32. Between the oil separator 29 and the receiving space 24, specifically between the counter-spiral 14 and the Housing cover 31, a pressure reducer 53 is arranged, which ensures that between the high pressure side and the receiving space 24, a pressure difference of about 10% -20% prevails. This ensures that in the closed position of the axial contact pressure between the displacement spiral 13 and the counter-spiral 14 and thus the axial tightness is increased.
  • the pressure chamber 15 is encapsulated (s. FIG. 4 ).
  • the pressure chamber 15 is free of installation.
  • the pressure chamber may have an inner shell 51, in particular made of stainless steel or stainless steel.
  • the inner shell 51 has a lower thermal conductivity than aluminum.
  • the thermal insulation of the oil separator 29 reduces the heating of the refrigerant vapor on the suction side.
  • the thermal insulation is carried out by an encapsulation, for example by an inner shell of stainless steel or stainless steel, which surrounds the cyclone.
  • the pressure reducer 53 is isolated by encapsulation with an inner shell of stainless steel or stainless steel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (11)

  1. Compresseur à spirale pour une installation de climatisation de véhicule à CO2 avec une spirale de déplacement mobile (13) qui est reliée pouvant tourner avec un palier excentrique (12) et vient en prise dans une contre-spirale (14) de telle manière qu'entre les spires de la spirale de déplacement (13) et la contre-spirale (14) il se forme des chambres se déplaçant radialement pour comprimer le frigorigène et l'éjecter dans une chambre de compression (15),
    la spirale de déplacement (13) étant disposée sur le côté aspiration et la contre-spirale (14) sur le côté haute pression,
    pour lequel le palier excentrique (12) dans le compartiment de déplacement est disposé entre la spirale de déplacement (13) et la contre-spirale (14) et comporte une bague de palier (26) constituée en une seule pièce avec la spirale de déplacement (13),
    caractérisé en ce que
    le fond (54) de celle-ci est aligné avec la face avant des spires de la spirale de déplacement (13).
  2. Compresseur à spirale selon la revendication 1,
    caractérisé en ce que
    la spirale de déplacement (13) comporte un évidement central (27), dans lequel est logé au moins en partie un contre-poids (28) qui est relié avec le palier excentrique (12).
  3. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la surface du palier excentrique (12) est inférieure à la surface centrale (55) à l'intérieur de la spire la plus interne de la contre-spirale (14) de telle sorte qu'au moins une ouverture d'éjection de gaz constituée dans la zone de la surface centrale (55) est accessible pour le raccord en fluide avec la chambre de compression (15).
  4. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les spires de la spirale de déplacement (13) et de la contre-spirale (14) comporte respectivement des chanfreins de lubrification (56) qui sont constitués respectivement sur les deux bords extérieurs des spires de la spirale de déplacement (13) et de la contre-spirale (14).
  5. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    d'autres chanfreins de lubrification (56) et/ou un rayon (57) dans les angles sont constitués entre les spires et une surface étanche (59) de la spirale de déplacement (13).
  6. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    d'autres chanfreins de lubrification (56) et/ou un rayon (57) dans les angles sont constitués entre les spires et une surface étanche (59) de la contre-spirale (14).
  7. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    un espace de réception (24) fermé du côté aspiration pour le palier excentrique (12) est en raccord de fluide avec la chambre de compression (15) et une paroi arrière (25) de la spirale de déplacement (13) peut être sollicitée avec une pression d'appui.
  8. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'espace entre le centre de la contre-spirale (14) et le centre de la spirale de déplacement (13) est au maximum de 1,5 mm, en particulier au maximum de 1,2 mm, en particulier au maximum de 1,0 mm, en particulier au maximum de 0,8 mm, en particulier au maximum de 0,6 mm, en particulier au maximum de 0,4 mm, en particulier au maximum de 0,2 mm.
  9. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que la contre-spirale (14) présente un angle d'enroulement de 660° à 720°, en particulier de 680° à 700°.
  10. Compresseur à spirale selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le volume de la chambre de compression (15) est supérieur du facteur de 5-7, en particulier du facteur de 6, au volume d'aspiration par révolution de la spirale de déplacement (13) et/ou la chambre de compression (15) est thermiquement isolée.
  11. Installation de climatisation qui contient du CO2 en tant que frigorigène avec un compresseur à spirale selon la revendication 1.
EP13168729.5A 2013-05-22 2013-05-22 Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale Active EP2806164B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13168729.5A EP2806164B1 (fr) 2013-05-22 2013-05-22 Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
US14/282,509 US9512840B2 (en) 2013-05-22 2014-05-20 Scroll-type compressor and CO2 vehicle air conditioning system having a scroll-type compressor
JP2014104948A JP6425417B2 (ja) 2013-05-22 2014-05-21 スクロール型圧縮機およびスクロール型圧縮機を有するｃｏ２車両空調システム
CN201410216902.9A CN104179682B (zh) 2013-05-22 2014-05-21 涡旋式压缩机以及具有涡旋式压缩机的co2车辆空调系统

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13168729.5A EP2806164B1 (fr) 2013-05-22 2013-05-22 Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale

Publications (2)

Publication Number Publication Date
EP2806164A1 EP2806164A1 (fr) 2014-11-26
EP2806164B1 true EP2806164B1 (fr) 2015-09-09

Family

ID=48569935

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13168729.5A Active EP2806164B1 (fr) 2013-05-22 2013-05-22 Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale

Country Status (4)

Country Link
US (1) US9512840B2 (fr)
EP (1) EP2806164B1 (fr)
JP (1) JP6425417B2 (fr)
CN (1) CN104179682B (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10350966B2 (en) 2015-08-11 2019-07-16 Ford Global Technologies, Llc Dynamically controlled vehicle cooling and heating system operable in multi-compression cycles
DE102015120151A1 (de) * 2015-11-20 2017-05-24 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug
DE102016105302B4 (de) * 2016-03-22 2018-06-14 Hanon Systems Steuerstromregelventil, insbesondere für Spiralverdichter in Fahrzeugklimaanlagen oder Wärmepumpen
DE102017105175B3 (de) 2017-03-10 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Verdrängerspirale, Fahrzeugklimaanlage und Fahrzeug
DE102017110913B3 (de) 2017-05-19 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug
DE102018217911A1 (de) * 2018-10-19 2020-04-23 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Verdichtermodul sowie elektromotorischer Kältemittelverdichter
GB2583373A (en) * 2019-04-26 2020-10-28 Edwards Ltd Scroll pump crank sleeve
WO2021040360A1 (fr) * 2019-08-27 2021-03-04 Samsung Electronics Co., Ltd. Compresseur à spirale
DE102020110097A1 (de) * 2020-04-09 2021-10-14 OET GmbH Verdrängermaschine, Verfahren, Fahrzeugklimaanlage und Fahrzeug

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1482910A (fr) 1966-03-23 1967-06-02 Pompe volumétrique
US3817664A (en) 1972-12-11 1974-06-18 J Bennett Rotary fluid pump or motor with intermeshed spiral walls
US3874827A (en) 1973-10-23 1975-04-01 Niels O Young Positive displacement scroll apparatus with axially radially compliant scroll member
JPS581278B2 (ja) 1980-04-05 1983-01-10 サンデン株式会社 スクロ−ル型圧縮機
US4610610A (en) 1984-08-16 1986-09-09 Sundstrand Corporation Unloading of scroll compressors
JPS6263189A (ja) 1985-09-17 1987-03-19 Nippon Soken Inc スクロ−ル型圧縮機
US4927339A (en) 1988-10-14 1990-05-22 American Standard Inc. Rotating scroll apparatus with axially biased scroll members
JPH05187371A (ja) * 1992-01-13 1993-07-27 Hitachi Ltd スクロール圧縮機とスクロールラップ加工用エンドミル
US5199280A (en) 1991-11-25 1993-04-06 American Standard Inc. Co-rotational scroll compressor supercharger device
JP3170111B2 (ja) * 1993-09-24 2001-05-28 株式会社日立製作所 スクロール圧縮機
US6273692B1 (en) 1999-06-29 2001-08-14 Sanden Corporation Scroll-type compressor
US6213731B1 (en) 1999-09-21 2001-04-10 Copeland Corporation Compressor pulse width modulation
JP2002161875A (ja) * 2000-11-27 2002-06-07 Matsushita Electric Works Ltd スクロールポンプ
JP4597358B2 (ja) 2000-12-22 2010-12-15 株式会社日本自動車部品総合研究所 スクロール型圧縮機
JP2003227476A (ja) * 2002-02-05 2003-08-15 Matsushita Electric Ind Co Ltd 空気供給装置
TWI221502B (en) * 2002-04-11 2004-10-01 Shimao Ni Scroll type fluid displacement apparatus with fully compliant floating scrolls
US6758659B2 (en) * 2002-04-11 2004-07-06 Shimao Ni Scroll type fluid displacement apparatus with fully compliant floating scrolls
US7265080B2 (en) * 2002-06-12 2007-09-04 Nsk Ltd. Rolling bearing, rolling bearing for fuel cell, compressor for fuel cell system and fuel cell system
JP2005023817A (ja) * 2003-07-01 2005-01-27 Matsushita Electric Ind Co Ltd スクロール圧縮機およびスクロールラップの加工方法
JP2006144635A (ja) 2004-11-18 2006-06-08 Denso Corp スクロール型圧縮機
EP2865895B1 (fr) * 2006-03-03 2017-07-19 Daikin Industries, Ltd. Compresseur et son procédé de fabrication
JP2008121490A (ja) * 2006-11-10 2008-05-29 Daikin Ind Ltd 回転式圧縮機
DE102008013784B4 (de) * 2007-03-15 2017-03-23 Denso Corporation Kompressor
US7611344B2 (en) * 2007-10-15 2009-11-03 Scroll Laboratories, Inc. Sealing tabs on orbiting scroll
JP2012026310A (ja) * 2010-07-21 2012-02-09 Panasonic Corp インバータ一体型電動圧縮機
JP5581440B2 (ja) * 2011-04-22 2014-08-27 株式会社日立製作所 スクロール圧縮機
JP2012237251A (ja) * 2011-05-12 2012-12-06 Mitsubishi Heavy Ind Ltd スクロール型流体機械

Also Published As

Publication number Publication date
CN104179682A (zh) 2014-12-03
CN104179682B (zh) 2018-03-02
US9512840B2 (en) 2016-12-06
EP2806164A1 (fr) 2014-11-26
JP2014228002A (ja) 2014-12-08
JP6425417B2 (ja) 2018-11-21
US20140348681A1 (en) 2014-11-27

Similar Documents

Publication Publication Date Title
EP2806164B1 (fr) Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
EP2806165B1 (fr) Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
EP3545195B1 (fr) Machine à déplacement positif selon le principe de la spirale, procédé de fonctionnement d'une machine à déplacement positif, spirale à déplacement positif, installation de climatisation de véhicule et véhicule
DE60116684T2 (de) Linearkompressor
WO2018197458A1 (fr) Compresseur
DE60309247T2 (de) Spiralverdichter
DE602005000066T2 (de) Verdichter
DE102016122028A1 (de) Taumelscheibenkompressor mit variabler Fördermenge
DE19633533C2 (de) Taumelscheibenkompressor
DE19650108A1 (de) Taumelscheiben-Kompressor
DE112005000201B4 (de) Kältemittelverdichter
DE3142230A1 (de) Mehrzylinder-kompressor
DE102004040476B4 (de) Kapazitäts-Steuerventil
EP1297256B1 (fr) Dispositif de securite pour compresseur de conditionnement d'air
DE102016203587A1 (de) Taumelscheibenverdichter mit veränderlicher Verdrängung
DE112011104568B4 (de) Kompressor mit einem Regelventil einer Öffnung in einer Ansaugpassage
DE102017102645B4 (de) Kältemittel-Scrollverdichter für die Verwendung innerhalb einer Wärmepumpe
DE102008008860B4 (de) Verdichter
DE102016219311A1 (de) Fluidverdichter
DE102016217358A1 (de) Scrollverdichter
DE102019208680A1 (de) Verdrängermaschine nach dem Spiralprinzip, insbesondere Scrollverdichter für eine Fahrzeugklimaanlage
DE19919141A1 (de) Elektromotorisch angetriebener Kompressor
DE102020210453B4 (de) Scrollverdichter eines elektrischen Kältemittelantriebs
DE102020203491B4 (de) Scroll-Verdichter
DE3401064A1 (de) Stroemungsmittelpumpe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20131126

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 18/02 20060101AFI20150209BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150320

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 748361

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150915

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013001118

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151210

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160109

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160111

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 4

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013001118

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20160610

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160531

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160522

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160531

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160531

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160522

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130522

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 748361

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180522

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20200528

Year of fee payment: 8

Ref country code: TR

Payment date: 20200511

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20200528

Year of fee payment: 8

Ref country code: IT

Payment date: 20200522

Year of fee payment: 8

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200522

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230530

Year of fee payment: 11