EP4336043B1 - Machine à spirales et système frigorifique - Google Patents

Machine à spirales et système frigorifique

Info

Publication number
EP4336043B1
EP4336043B1 EP23181521.8A EP23181521A EP4336043B1 EP 4336043 B1 EP4336043 B1 EP 4336043B1 EP 23181521 A EP23181521 A EP 23181521A EP 4336043 B1 EP4336043 B1 EP 4336043B1
Authority
EP
European Patent Office
Prior art keywords
unit
scroll
machine
spiral
bearing
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
EP23181521.8A
Other languages
German (de)
English (en)
Other versions
EP4336043A2 (fr
EP4336043A3 (fr
Inventor
Markus Hauser
Christian Scharer
Thomas Varga
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP4336043A2 publication Critical patent/EP4336043A2/fr
Publication of EP4336043A3 publication Critical patent/EP4336043A3/fr
Application granted granted Critical
Publication of EP4336043B1 publication Critical patent/EP4336043B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • 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
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2240/50—Bearings
    • 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
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the present invention relates to a scroll machine, in particular a spiral compressor for a medium, in particular a refrigerant, and to a refrigeration system with such a scroll machine.
  • Scroll machines are fluid energy machines and are known in various designs from the prior art. Examples of scroll machines include scroll compressors, scroll compressors or spiral compressors, and scroll expanders.
  • Known scroll machines typically feature two cooperating spiral units, each with at least one spiral rib forming at least one spiral channel.
  • the spiral ribs of the spiral units interlock to form pressure chambers, with the spiral ribs sealingly abutting the spiral channel floor of the other spiral unit.
  • Both the spiral channel and the spiral rib forming the spiral channel are shaped like a circular involute, with the two spiral units being movable relative to each other.
  • a common design of scroll machines features a stationary spiral unit and a movable spiral unit, the first movable spiral unit moving along an orbital path relative to a second spiral unit.
  • a medium for example a refrigerant
  • a medium is compressed in a compressor by the relative movement of two spiral units.
  • the medium in pressure chambers along the spiral channels from an outer end region to an inner end region, whereby the medium in the respective pressure chamber undergoes a change in volume.
  • a scroll machine of this type is known that can be used in a refrigeration system with a refrigerant circuit.
  • refrigeration systems can be used in a variety of ways, such as cooling a secondary fluid like air or cooling components or equipment.
  • the cooling or heating load of refrigeration systems can vary considerably depending on ambient conditions, occupancy levels, and other load requirements.
  • the printed materials US 2009/162222 A1 and US 2004/057859 A1 reveal scroll machines with a bearing unit and a spiral unit that enclose a space.
  • the object of the present invention is to propose a scrolling machine and a refrigeration system of the type described above, which incorporates features known from the prior art. Disadvantages are eliminated in a practical manner.
  • a scrolling machine and a refrigeration system are to be provided, which are cooled and lubricated effectively in a simple manner.
  • the scrolling machine according to the invention comprising the features of claim 1 for a medium, in particular a refrigerant, has a machine housing with a longitudinal axis, an inlet, and an outlet for the medium. Furthermore, in the scrolling machine according to the invention, a drive unit, a drive shaft, a first spiral unit, and a second spiral unit are arranged along the longitudinal axis.
  • the drive shaft is supported on the machine housing by a first bearing unit and a second bearing unit, the axis of rotation of the drive shaft preferably determining the position and orientation of the longitudinal axis.
  • the first bearing unit and the second bearing unit are preferably arranged in opposite end sections of the drive shaft.
  • the second bearing unit is located in the end section adjacent to the first spiral unit, and the first bearing unit is located in the opposite end section.
  • the first spiral unit has a first spiral channel formed by a first spiral rib, which extends from an inner end region to an outer end region.
  • the second spiral unit has a second spiral channel formed by a second spiral rib, extending from an inner end region to an outer end region.
  • the inlet of the scroll machine is in fluid communication with the outer end regions of the first and second spiral units, the outer end regions being referred to as the intake region in connection with this invention.
  • the outlet is in fluid communication with the inner end regions, whereby the medium is guided through the inlet and through the machine housing along several flow paths to the outer end regions and from the inner end regions to the outlet.
  • the first spiral unit can be moved by means of the drive shaft through the drive unit along an orbital path relative to the second spiral unit, and the first spiral unit and the second spiral unit interlock to form pressure chambers, with the spiral ribs sealingly abutting a spiral channel floor of the other spiral unit.
  • the drive shaft has a hollow shaft section, wherein one of the flow paths is guided through the hollow shaft section.
  • the hollow shaft section is preferably arranged coaxially to the axis of rotation of the drive shaft and can partially or completely penetrate the drive shaft.
  • the drive shaft can simultaneously be used as a conduit for the medium, resulting in a space-saving and low-pressure-loss design.
  • the proposed solution allows for the medium to be guided within the machine housing, while simultaneously enabling cooling of the drive shaft and, in particular, the components of the scroll machine connected to the drive shaft, such as the drive shaft bearings. This results in a particularly compact scroll machine with integrated cooling and efficient bearing lubrication.
  • the medium is preferably a refrigerant, wherein the refrigerant comprises a lubricant which can be carried along by the refrigerant.
  • the hollow shaft section is formed by a blind hole.
  • the blind hole preferably extends from an end face of the drive shaft in the first end section towards the second end section.
  • the drive shaft can have at least one radial bore that opens into the hollow shaft section and connects the hollow shaft section to an outer surface of the drive shaft.
  • the medium can be guided along a flow path through the at least one radial bore.
  • the at least one radial bore makes it possible to direct the medium along the longitudinal axis from the drive shaft to individual components, thereby enabling cooling and/or lubrication of these components by the lubricant carried along with the medium.
  • a rotor of the drive unit can be arranged between the first bearing unit and the second bearing unit, wherein the drive shaft between the first bearing unit and the rotor and/or the drive shaft between the second bearing unit and the rotor has at least one radial bore.
  • at least one radial bore is arranged both between the first bearing unit and the rotor and between the second bearing unit and the rotor.
  • the at least one radial bore between the first bearing unit and the rotor and/or between the second bearing unit and the rotor can contribute to improved cooling of the rotor of the drive unit, wherein preferably the drive shaft has several radial bores around its circumference, which, according to a further preferred embodiment, are arranged circumferentially symmetrically.
  • the drive unit or preferably an electric drive, has at least one axial opening and/or at least one axial groove around the drive unit, and if the at least one axial opening and/or the at least one axial groove defines a flow path for the medium.
  • the drive unit has several axial openings and/or several axial grooves around its circumference, which are preferably arranged circumferentially symmetrically.
  • the at least one axial opening and/or the at least one axial groove connects opposite end faces of the drive unit or the drive, and extensive cooling of the rotor and/or the stator of the drive can be achieved.
  • the at least one axial opening can, for example, be formed by a motor gap, and/or the at least one axial groove can be formed by a channel-shaped free space between The stator and the housing are formed.
  • the at least one axial groove and/or axial opening can be formed in the housing and/or the drive unit.
  • the first bearing unit comprises a secondary bearing body, preferably a rolling bearing not sealed by seals, through which the other flow path is preferably guided.
  • the inlet in the machine housing can be located directly in front of the free end of the drive shaft, preferably being arranged approximately coaxially with the drive shaft along its longitudinal axis.
  • the medium coming from the inlet is split into two parallel flow paths, one through which the medium flows into the first bearing unit and the other through the hollow shaft section of the drive shaft. This allows, in particular, the secondary bearing body of the first bearing unit to be cooled, and the lubricant carried along with the medium can also lubricate the secondary bearing body.
  • the second bearing unit and the first spiral unit enclose a space, wherein at least one of the flow paths is led into the space through the second bearing unit.
  • the second bearing unit can comprise a main bearing body and a main bearing housing. At least one of the flow paths can be routed through the main bearing housing and/or through the main bearing body. In other words, the flow paths into the space through the second bearing unit can be routed exclusively through the main bearing housing or the main bearing body, or they can be connected in parallel through the main bearing housing and the main bearing body.
  • At least one flow path is guided through the main bearing body to cool the main bearing body and to lubricate it with the lubricant carried along by the medium.
  • the main bearing body can be an unsealed rolling bearing.
  • the second bearing unit divides the machine housing into a drive section and an intake section.
  • the drive unit is located in the drive section, and the outer end regions of the first and second spiral units are located in the intake section.
  • the inlet opens into an intake section, with the first bearing unit positioned between the intake section and the drive section.
  • the medium is guided along the flow paths from the inlet section through the drive section and through the second bearing unit to the intake section and the outer end regions of the first and second spiral units, respectively.
  • the drive shaft projects into the space through the second bearing unit, wherein a balancing mass firmly connected to the drive shaft and/or An eccentric drive is arranged for the first spiral unit.
  • An eccentric drive preferably comprises an eccentric section formed as a driver on the drive shaft, which is coupled to the first spiral unit via an eccentric bearing body. Both the counterweight and the eccentric drive can move together with the drive shaft within the space, thereby “stirring” or “swirling” the medium present in the space and allowing a significant amount of the lubricant carried along with the medium to be separated.
  • the second bearing unit can be cup- or bell-shaped, with the main bearing body and an axial bearing for the first spiral unit being provided on opposite sides of the second bearing unit along its longitudinal axis.
  • the main bearing body is preferably arranged in the region of a vertex of the bell-shaped second bearing unit, and the axial bearing on the opposite end face.
  • At least two parallel flow paths lead from the inlet into the chamber, one flow path being guided through the main bearing body and the other flow path being guided through at least one inlet opening formed as a perforation in the main bearing housing.
  • the two parallel flow paths reduce pressure loss while simultaneously ensuring sufficient lubrication and/or cooling of the main bearing body.
  • the main bearing housing has several inlet openings, which are more preferably arranged symmetrically around its circumference.
  • the inlet openings are preferably located in a cylindrical surface of the main bearing housing and, even more preferably, approximately centered along the longitudinal axis between the opposite sides of the second bearing unit.
  • the invention provides that the space has at least one outlet opening, and that the outlet opening defines a flow path that connects the space with the outer end regions of the first spiral unit and the second spiral unit or the intake area.
  • the at least one outlet opening comprises a first bore section and a second bore section, and if the first bore section and the second bore section are arranged in an L- or T-shape.
  • the first bore section and the second bore section are each formed along a straight line that intersects at a common point.
  • the first bore section is oriented radially with respect to the longitudinal axis, and the second bore section is oriented axially.
  • the first bore section is preferably designed as a through bore and connects an outer surface of the main bearing housing to the space.
  • the second bore section can, for example, be formed by a blind bore.
  • at least one of the two bore sections can be formed in the main bearing housing by a forming or machining process.
  • an outlet opening can be arranged such that lubricant can drain from the chamber through the outlet opening.
  • an outlet opening is particularly well-placed in the underside of the second bearing unit. Separated lubricant can accumulate in the area of the underside and can then be carried away by the flow through the outlet opening or flow off.
  • the at least one outlet opening can be formed by an axial recess extending from the radial outside to the radial inside, interrupting the axial bearing surface.
  • the at least one axial recess is traversed, thereby providing continuous lubrication and cooling of the axial bearing.
  • the transition between the surface of the axial bearing and the at least one radially oriented axial recess can be provided with transition radii.
  • an axial bearing element is arranged between the second bearing unit and the first spiral unit, preferably on axial recesses that extend from the radial outside to the radial inside and interrupt the axial bearing surface.
  • the axial bearing element can preferably be an axial bearing plate.
  • the at least one outlet opening is formed by a conduit in the second bearing unit, wherein the conduit preferably comprises a first bore section and a second bore section arranged in an L-shape.
  • the first bore section is arranged radially oriented and The second bore section is arranged axially.
  • the first bore section and the second bore section can preferably be machined into the second bearing unit or the main bearing housing, wherein the first bore section preferably penetrates the second bearing unit completely, while the second bore section can be designed as a blind hole.
  • the first bore section thus extends from the space to an outer surface of the second bearing unit or the main bearing housing and is preferably closed there by the machine housing or a section of the machine housing.
  • the second bore section intersects the first bore section and opens into the outer end regions of the first spiral unit and the second spiral unit, or into the intake region of the two spiral units.
  • the at least one outlet opening is arranged circumferentially offset from the at least one inlet opening with respect to the longitudinal axis of the space. This offset arrangement of the inlet openings relative to the outlet opening allows the residence time of the medium in the space to be extended, thereby increasing the separation rate of the lubricant carried in the medium.
  • a preferred embodiment of the present invention provides that the at least one outlet opening on the side of the second bearing unit facing the first spiral unit is arranged partially or completely within an area that is traversed by the first spiral unit during a complete movement along its orbital path.
  • the at least one outlet opening is thus, during movement along the orbital path of the first spiral unit, at least once partially or completely traversed, thereby lubricating the axial bearing located between the second bearing unit and the first spiral unit.
  • the first spiral unit has a recess on the side facing the at least one outlet opening, which is located within a surface that the at least one outlet opening passes over during a complete movement of the first spiral unit along its orbital path. This recess prevents the first spiral unit from coming into direct contact with the at least one outlet opening, thereby preventing damage to the outlet opening and/or to a surface of the axial bearing of the first spiral unit.
  • a further development of the present invention provides that at least one ring-pin coupling is provided which prevents a complete rotation of the first spiral unit about the longitudinal axis.
  • a ring-pin coupling comprises at least one pair of ring-pin couplings, preferably several pairs of ring-pin couplings, each with a pin that engages in an abutment. The pin can move within the annular abutment in a manner corresponding to the orbital path.
  • one of the flow paths is guided through the ring-pin coupling, wherein the respective abutment is more preferably formed in the second bearing unit and either completely penetrates the second bearing unit or has a connecting bore that penetrates the second bearing unit so that the flow path coming from the inlet
  • the lubricant carried along by the refrigerant can be deposited in the ring-pin coupling for lubrication.
  • the at least one connecting bore can guide a flow path from the inlet through the second bearing unit to the intake area.
  • the connecting bore does not necessarily have to pass through a ring-pin coupling pair or its abutment as previously described, but can also pass through the second bearing unit beyond the ring-pin coupling pair.
  • the at least one ring-pin coupling pair is arranged in the scroll machine during its intended use such that lubricant can drain from the drive section through the ring-pin coupling towards the intake area.
  • a ring-pin coupling is specifically arranged in the area of a lower surface of the second bearing unit.
  • the second spiral unit is stationary.
  • the second spiral unit preferably does not move relative to the first spiral unit and the machine housing during the intended operation of the scroll machine.
  • a high-pressure chamber can be arranged in the housing.
  • the inner end regions of the first spiral unit and the second spiral unit are connected to the high-pressure chamber via a passage, and the medium can leave the machine housing from the high-pressure chamber through the outlet.
  • the high-pressure chamber can be connected to an outlet via a pressure port.
  • the pressure port can be arranged in a plane transverse to the longitudinal axis relative to the outlet and can preferably be located in the pressure chamber along the longitudinal axis on the side opposite the outlet. This offset arrangement between the outlet and the pressure port is intended to ensure that pressure pulsations are reduced and that the medium coming from the outlet cannot flow directly out of the scroll machine through the pressure port.
  • the high-pressure chamber can incorporate a backflow region that forces an S-shaped flow path from the inlet to the outlet. This backflow region promotes pulsation damping and reduces pressure fluctuations in the medium discharged through the outlet.
  • an intermediate floor can be provided between the high-pressure chamber and the second spiral unit, with the intermediate floor, together with the machine housing, enclosing the high-pressure chamber.
  • the intermediate floor absorbs a large part of the pressure load of the high-pressure chamber, thereby subjecting the second spiral unit to lower loads.
  • the backflow area is formed by a recess in the intermediate floor on the side facing the high-pressure chamber and the pressure nozzle, with the pressure nozzle projecting into the high-pressure chamber oriented towards the recess.
  • the pressure nozzle is in contact with the intermediate floor in an area towards the The formation of the flow area is in effective contact, and the contact area is arranged on an imaginary connecting line in a plane perpendicular to the longitudinal axis between the pressure nozzle and the passage.
  • a check valve can be provided, which is arranged between the high-pressure chamber and the outlet.
  • the check valve can be located either in the outlet or in the pressure port, with the check valve being particularly preferably inserted into the pressure port in the form of a bushing. This results in a particularly compact and simple design.
  • Another aspect of the present invention relates to a refrigeration system with a scroll machine described above.
  • Figure 1 shows a preferred embodiment of a refrigeration system 1 with a scroll compressor 2.
  • the refrigeration system 1 comprises the scroll compressor 2, a condenser 3, an expansion element 4, and an evaporator 5.
  • a medium preferably a refrigerant, flows through the refrigeration system 1 in the direction indicated by arrows, first from an outlet 12 of the scroll compressor 2, then to the condenser 3, the expansion element 4, the evaporator 5, and finally back through an inlet 11 into the scroll compressor 2.
  • Figure 1 The scrolling machine 2 shown is described.
  • FIG 2 is a simplified cross-sectional view of the scrolling machine 2 according to Figure 1
  • the scroll machine 2 has a machine housing 10, referred to as a whole, which is oriented along a longitudinal axis X.
  • the machine housing 10 can have several housing parts, wherein in the In the present embodiment, the machine housing 10 has a first housing part 10' and a second housing part 10''.
  • a drive unit 400 In the machine housing 10, along the longitudinal axis X, according to Figure 2 From right to left the inlet 11, a drive unit 400, a drive shaft 420, a first spiral unit 100, a second spiral unit 200, an intermediate floor 50, a high pressure chamber 30 and the outlet 12 are arranged.
  • the first spiral unit 100 is coupled to the drive unit 400 via an eccentric drive 150 and the drive shaft 420.
  • the drive unit 400 preferably comprises an electric drive with a rotor 410 and a stator 415, wherein the rotor 410 is rigidly coupled to the drive shaft 420.
  • the drive shaft 420 is aligned along the longitudinal axis X, and in the illustrated embodiment, the axis of rotation of the drive shaft 420 defines the longitudinal axis X.
  • the drive shaft 420 has a first end section and a second end section on opposite sides along the longitudinal axis X.
  • the drive shaft 420 is supported on the machine housing 10 by a first bearing unit 450, and in the second end section by a second bearing unit 300.
  • the rotor 410 of the drive unit 400 is arranged between the first bearing unit 450 and the second bearing unit 300.
  • the drive shaft 420 has a hollow shaft section 424 oriented along the longitudinal axis X.
  • the hollow shaft section 424 can be configured as a blind bore and extends from a free end face of the drive shaft 420 in the first end section towards the second end section.
  • the drive shaft 420 also includes several radial bores 428 that penetrate the drive shaft 420 and connect the hollow shaft section 424 with an outer cylindrical surface of the drive shaft 420.
  • the drive shaft 420 can have at least one radial bore 428 between the first bearing unit 450 and the rotor 410 and/or between the second bearing unit 300 and the rotor 410.
  • the drive shaft 420 has two radial bores 428 between the first bearing unit 450 and the rotor 410 and between the second bearing unit 300 and the rotor 410, which are arranged circumferentially symmetrically to the drive shaft 420.
  • the first bearing unit 450 comprises a bearing receptacle 452 and a secondary bearing body 455.
  • the bearing receptacle 452 can be formed by the machine housing 10.
  • the secondary bearing body 455 can be designed as a rolling bearing, which is preferably not sealed.
  • the first bearing unit 450 divides the interior of the machine housing 10 into an inlet section and a drive section, with the inlet 11 opening into the inlet section.
  • the inlet 11 is preferably arranged on an end face of the machine housing 10, wherein the inlet 11 is even more preferably arranged in line with the drive shaft 420 - preferably directly in front of the free end face of the drive shaft 420.
  • the second bearing unit 300 comprises a main bearing housing 302 and a main bearing body 305.
  • the main bearing body 305 can be designed as a rolling bearing, preferably unsealed.
  • the second bearing unit 300 further divides the interior of the machine housing 10 into the drive section and an intake area 320.
  • the second bearing unit 300 has a first side and a second side, the first side facing the drive unit 400 and the second side facing the first spiral unit 100.
  • the main bearing body 305 is arranged on the first side and an end face on the second side forms an axial bearing 190 for the first spiral unit 100.
  • the second bearing unit 300 or the main bearing housing 302 can be bell- or pot-shaped and enclose a space 380 together with the first spiral unit 100.
  • the chamber 380 has several inlet openings 370, which are formed in the second bearing unit 300 and in the main bearing housing 302, respectively.
  • the inlet openings 370 penetrate the main bearing housing 302 and open into the chamber 380.
  • the second bearing unit 300 can have four inlet openings 370, as shown in Figure 5 As shown, they can be arranged circumferentially symmetrically on a lateral surface, preferably approximately midway between the first side and the second side.
  • the space 380 can have several outlet openings 390, which are preferably formed in the second bearing unit 300 or the main bearing housing 302.
  • Figure 3 shows an enlarged detail view according to Figure 2 which shows that the outlet opening 390 can be formed from a first bore section 392 and a second bore section 394 in the main bearing housing 302.
  • the first bore section 392 is essentially radially oriented and extends from the space 380. For manufacturing reasons, it may be advantageous if the first bore section 392 completely penetrates the main bearing housing 302.
  • the second bore section 394 is essentially axially oriented and connects the second side of the second bearing unit 300 or the main bearing housing 302 with the first bore section 392.
  • the second bearing unit 300 can have four outlet openings 390, which are preferably arranged circumferentially symmetrically. Furthermore, the outlet openings 390 can be oriented relative to the inlet openings 370 – as in Figure 5 indicated - arranged offset in the circumferential direction.
  • the drive shaft 420 projects into space 380 through the second bearing unit 300 or through the main bearing body 305.
  • a counterweight 430 is located in space 380 and is arranged on the drive shaft 420.
  • the eccentric drive 150 is arranged in space 380, comprising an eccentric shaft section 152 and an eccentric bearing body 155 arranged on the eccentric shaft section 152.
  • the eccentric shaft section 152 can be formed by the drive shaft 420.
  • the first spiral unit 100 according to Figure 2
  • the device has a first side 101 and a second side 102 opposite the first side 101 along the longitudinal axis X.
  • the first spiral unit 100 is mounted on the second bearing unit 300 by means of the axial bearing 190.
  • the eccentric drive 150 is coupled to the first spiral unit 100 on the first side 101, and on the second side 102, a first spiral rib 110 is arranged, which projects along the longitudinal axis X and forms a first spiral channel 120.
  • a ring-pin coupling 350 is provided, which connects several ring-pin coupling pairs 351 (see Figures 4 or 5
  • the ring-pin coupling pairs form the ring-pin coupling 350, which prevents a complete rotation of the first spiral unit 100 about the longitudinal axis X.
  • the ring-pin coupling 350 couples the first spiral unit 100 to the second bearing unit 300 and comprises a pin 356 and an abutment, which can be formed by a recess 352 and a sleeve 354 arranged in the recess 352.
  • the pin 356 can move within the abutment in a manner corresponding to its orbital path.
  • the abutment can be formed in the second bearing unit 300, and the pins 356 project from the first side 101 of the first spiral unit 100 and engage in the abutments of the second bearing unit 300.
  • a ring-pin coupling pair 351 can have a connecting bore. 360, which breaks through the second bearing unit 300 or the main bearing housing 302.
  • the first spiral rib 110 on the second side 102 of the first spiral unit 100 forms the spiral channel 120 with a spiral channel base.
  • the spiral rib 110 has a first spiral rib tip at its end face, which may either have a seal or be designed as a flat tip.
  • the first spiral channel 120 may also have an inner end region 125 and/or an outer end region 126.
  • the first spiral rib 110 is involute in shape and extends from the inner end region 125 to the outer end region 126.
  • the inner end region 125 is located radially inside with respect to the longitudinal axis X
  • the outer end region 126 is located radially outside with respect to the longitudinal axis X.
  • the at least one spiral channel 120 is U-shaped and is bounded in the radial directions by the spiral rib 110 or a spiral wall of the spiral rib 110 and the spiral channel floor.

Landscapes

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

Claims (21)

  1. Machine (2) à spirales, en particulier compresseur à spirale, pour un milieu, en particulier pour un fluide réfrigérant, comportant une enveloppe (10) de machine, ayant un axe (X) longitudinal et une entrée et une sortie pour le milieu, dans laquelle, dans l'enveloppe (10) de la machine, le long de l'axe (X) longitudinal, est montée une unité (400) d'entraînement ayant un arbre (420) d'entraînement, qui est monté par une première unité (450) de palier et par une deuxième unité (300) de palier sur l'enveloppe (10) de la machine,
    une première unité (100) à spirale comprenant un canal (120) à spirale formé par une première nervure (110) de spirale et ayant une partie (125) intérieure d'extrémité et une partie (126) extérieure d'extrémité,
    il est prévu une deuxième unité (200) à spirale, comprenant un canal (220) à spirale, formé par une deuxième nervure (210) de spirale et ayant une première partie (225) intérieure d'extrémité et une deuxième partie (226) extérieure d'extrémité, et
    dans laquelle, la première unité (100) à spirale et la deuxième unité (200) à spirale s'interpénètrent pour la formation de chambres sous pression,
    dans laquelle la première unité (100) à spirale peut, au moyen de l'arbre (420) d'entraînement, par l'unité (400) d'entraînement, être déplacée suivant une trajectoire orbitale par rapport à la deuxième unité (200) à spirale,
    dans laquelle l'entrée (11) est en communication fluidique avec les parties (126, 226) extérieures d'extrémité et la sortie (12) est en communication fluidique avec les parties (125, 225) intérieures d'extrémité,
    caractérisée en ce que
    le milieu peut dans l'enveloppe (10) de la machine s'écouler suivant plusieurs chemins d'écoulement de l'entrée (11) aux parties (126, 226) extérieures d'extrémité,
    dans laquelle la deuxième unité (300) de palier et la première unité (100) de palier entourent un espace (380) et en ce qu'au moins l'un des chemins d'écoulement passe par l'espace (380),
    dans laquelle l'arbre (420) d'entraînement pénètre par la deuxième unité (300) de palier dans l'espace (380) et sur l'arbre (420) d'entraînement dans l'espace (380) sont respectivement ou est disposés une masselotte de compensation assemblée fixement à l'arbre (420) et/ou un entraînement (150) à excentrique de la première unité (100) à spirale,
    dans laquelle l'espace (380) a au moins une ouverture (390) de sortie et en ce que l'ouverture (390) de sortie prescript un chemin d'écoulement, qui met l'espace (380) en communication avec les parties (126, 226) extérieures d'extrémité.
  2. Machine (2) à spirales suivant la revendication 1, caractérisée en ce que
    l'arbre (420) d'entraînement a un tronçon (424) d'arbre creux, dans laquelle passe l'un des chemins d'écoulement.
  3. Machine (2) à spirales suivant la revendication 2, caractérisée en ce que
    le tronçon (424) d'arbre creux est constitué par un trou borgne, en ce que l'arbre (420) d'entraînement a au moins un alésage (428) radial traversant l'arbre (420) d'entraînement par le tronçon (424) d'arbre creux.
  4. Machine (2) à spirales suivant l'une des revendications 2 ou 3,
    caractérisée en ce qu'
    un rotor (410) de l'unité (400) d'entraînement est monté entre la première unité (450) de palier et la deuxième unité (300) de palier et en ce que l'arbre (420) d'entraînement a au moins un alésage (428) radial entre la première unité (450) de palier et le rotor (410) et/ou entre la deuxième unité (300) de palier et le rotor (410).
  5. Machine (2) à spirales suivant la revendication 4, caractérisée en ce que
    l'unité (400) d'entraînement a au moins un ajour (414) axial et/ou au moins une rainure (418) axiale et en ce que le au moins un ajour (414) axial et/ou la au moins une rainure (418) axiale prescrivent l'un des chemins d'écoulement.
  6. Machine (2) à spirales suivant l'une des revendications 2 à 5,
    caractérisée en ce qu'
    entre l'entrée (11) et l'arbre (420) d'entraînement, un chemin d'écoulement bifurque en deux chemins d'écoulement en parallèle, dans laquelle l'un des chemins d'écoulement passe dans le tronçon (424) d'arbre creux et l'autre des chemins d'écoulement passe dans la première unité (450) de palier.
  7. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce que
    la deuxième unité (300) de palier comprend une boîte (302) principale de palier et un corps (305) principal de palier, et au moins l'un des chemins d'écoulement passe par la boîte (302) principale de palier et/ou le corps (305) principal de palier.
  8. Machine (2) à spirales suivant l'une des revendications 6 ou 7,
    caractérisée en ce qu'
    au moins deux chemins d'écoulement vont, en passant par la deuxième unité (300) de palier, de l'entrée (11) à l'espace (380), dans laquelle l'un des chemins d'écoulement passe par le corps (305) principal de palier et l'autre des chemins d'écoulement passe dans au moins une ouverture (370) d'entrée constituée comme ajour dans la boîte (302) principale de palier.
  9. Machine (2) à spirales suivant la revendication 8, caractérisée en ce que
    plusieurs ouvertures (370) d'entrée sont disposées sur le pourtour, de préférence symétriquement.
  10. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    au moins une ouverture (390) de sortie est constituée sous la forme d'un évidement axial orienté radialement du côté tourné vers la première unité (100) à spirale.
  11. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    au moins une ouverture (390) de sortie a une première partie (392) d'alésage, orientée radialement, et une deuxième partie (394) d'alésage, orientée axialement.
  12. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    au moins une ouverture (390) de sortie est disposée de manière décalée dans la direction du pourtour par rapport à au moins une ouverture (370) d'entrée.
  13. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    au moins une ouverture (390) de sortie débouche, du côté tourné vers la première unité (100) à spirale, en tout ou partie à l'intérieur d'une surface qui est parcourue, lors du déplacement complet suivant la trajectoire orbitale, par la première unité (100) à spirale.
  14. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce que
    la première unité (100) à spirale présente, du côté tourné vers au moins une ouverture (390) de sortie, un retour (290), qui est disposé à l'intérieur d'une surface, qu'au moins une ouverture (390) de sortie franchit lors d'un déplacement complet suivant la trajectoire orbitale.
  15. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    il est prévu un accouplement (350) ring pin et en ce que l'un des chemins d'écoulement passe par l'accouplement (350) ring pin.
  16. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce que
    la deuxième unité (200) à spirale est fixe.
  17. Machine (2) à spirales suivant l'une des revendications précédentes,
    caractérisée en ce qu'
    une chambre (30) sous haute pression est disposée dans l'enveloppe de la machine, en ce que les parties (125, 225) intérieures d'extrémité communiquent avec la chambre (30) sous haute pression par un passage (260) et avec la sortie (12) par la chambre (30) sous haute pression et en ce qu'il est prévu, dans la chambre (30) sous haute pression, une partie (45) d'écoulement en retour, qui oblige à avoir un chemin d'écoulement en forme de S dans la chambre (30) sous haute pression.
  18. Machine (2) à spirales suivant la revendication 17, caractérisée en ce qu'
    un fond (50) intermédiaire est prévu entre la chambre (30) sous haute pression et la deuxième unité (200) à spirale et en ce que la partie (45) d'écoulement en retour est formée par un évidement (59), constitué dans le fond (50) intermédiaire du côté tourné vers la chambre (30) sous haute pression, et une tubulure (40) tenant la pression en saillie par rapport à l'évidement (59).
  19. Machine (2) à spirales suivant la revendication 17 ou 18,
    caractérisée en ce que
    la tubulure (40) tenant la pression est, pour la formation de la partie (45) d'écoulement en retour en contact d'action avec le fond (50) intermédiaire dans une partie (46) de contact et en ce que la partie (46) de contact est disposée entre la tubulure (40) tenant la pression et le passage (260) sur une ligne de liaison imaginaire dans un plan perpendiculaire à l'axe (X) longitudinal.
  20. Machine (2) à spirales suivant l'une des revendications 17 à 19,
    caractérisée en ce que
    la tubulure (40) tenant la pression comprend une douille (49) ayant un clapet anti-retour.
  21. Installation (1) frigorifique comprenant une machine (2) à spirales suivant l'une des revendications précédentes.
EP23181521.8A 2022-08-16 2023-06-26 Machine à spirales et système frigorifique Active EP4336043B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102022120679.3A DE102022120679A1 (de) 2022-08-16 2022-08-16 Scrollmaschine und Kälteanlage

Publications (3)

Publication Number Publication Date
EP4336043A2 EP4336043A2 (fr) 2024-03-13
EP4336043A3 EP4336043A3 (fr) 2024-04-03
EP4336043B1 true EP4336043B1 (fr) 2026-03-18

Family

ID=87047571

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23181521.8A Active EP4336043B1 (fr) 2022-08-16 2023-06-26 Machine à spirales et système frigorifique

Country Status (4)

Country Link
US (2) US12331743B2 (fr)
EP (1) EP4336043B1 (fr)
CN (1) CN117588410A (fr)
DE (1) DE102022120679A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022120679A1 (de) * 2022-08-16 2024-02-22 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine und Kälteanlage

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU613949B2 (en) * 1987-09-08 1991-08-15 Sanden Corporation Hermetic scroll type compressor
JP3870642B2 (ja) * 1999-12-21 2007-01-24 株式会社デンソー 電動圧縮機
KR100427399B1 (ko) * 2000-12-28 2004-04-17 라필찬 고, 저압부가 일체로 장착된 스크롤 유체기계
US6887050B2 (en) * 2002-09-23 2005-05-03 Tecumseh Products Company Compressor having bearing support
US7914268B2 (en) * 2007-09-11 2011-03-29 Emerson Climate Technologies, Inc. Compressor having shell with alignment features
JP2009150234A (ja) * 2007-12-18 2009-07-09 Toyota Industries Corp 電動圧縮機
JP5285988B2 (ja) * 2008-07-25 2013-09-11 日立アプライアンス株式会社 横型スクロール圧縮機
WO2014002970A1 (fr) * 2012-06-27 2014-01-03 株式会社豊田自動織機 Compresseur à spirale
JP2014070582A (ja) * 2012-09-28 2014-04-21 Toyota Industries Corp 電動圧縮機及び空調装置
JP6147605B2 (ja) * 2013-08-02 2017-06-14 三菱重工業株式会社 圧縮機
EP3491245B1 (fr) 2016-07-27 2024-03-27 BITZER Kühlmaschinenbau GmbH Compresseur
US10801495B2 (en) * 2016-09-08 2020-10-13 Emerson Climate Technologies, Inc. Oil flow through the bearings of a scroll compressor
US11111921B2 (en) * 2017-02-06 2021-09-07 Emerson Climate Technologies, Inc. Co-rotating compressor
KR102087141B1 (ko) * 2018-09-06 2020-03-10 엘지전자 주식회사 전동식 압축기
US20230258186A1 (en) * 2020-06-23 2023-08-17 Emerson Climate Technologies (Suzhou) Co., Ltd. Scroll compression mechanism and scroll compressor
JP7439690B2 (ja) * 2020-08-05 2024-02-28 株式会社デンソー 圧縮機、圧縮機の製造方法
DE102022120679A1 (de) * 2022-08-16 2024-02-22 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine und Kälteanlage

Also Published As

Publication number Publication date
US20250283467A1 (en) 2025-09-11
US20240060491A1 (en) 2024-02-22
CN117588410A (zh) 2024-02-23
EP4336043A2 (fr) 2024-03-13
EP4336043A3 (fr) 2024-04-03
DE102022120679A1 (de) 2024-02-22
US12331743B2 (en) 2025-06-17

Similar Documents

Publication Publication Date Title
DE112015004113B4 (de) Kompressor mit Ölrückführeinheit
DE112014002604B4 (de) Antriebswelle für Scroll-Verdichter und Scroll-Verdichter
DE2735663A1 (de) Spiralartige einrichtung mit einem hydrodynamischen axiallager
DE19622718A1 (de) Kolbenkompressor mit integriertem Schmierölseparator
DE102016121241B4 (de) Hydraulischer Antrieb, hydraulischer Motor und integrierte Pumpe mit dem hydraulischen Antrieb
EP1307657B1 (fr) Pompe a vide a deux arbres
DE3127323A1 (de) Schraubenkompressor mit geschlossenem druckgassystem mit oelnebelschmierung
DE102020210453B4 (de) Scrollverdichter eines elektrischen Kältemittelantriebs
EP4336043B1 (fr) Machine à spirales et système frigorifique
EP4264053B1 (fr) Compresseur à spirale pour la production d'air comprimé sans huile
DE69003012T2 (de) Axialdichtungseinrichtung für Spiralverdichter.
DE69631485T2 (de) Spiralverdichter mit einem plattenförmigen axialgleitlage
DE3826548C2 (de) Flügelzellenverdichter mit variabler Förderleistung
EP4325055B1 (fr) Machine à spirales à injection et système frigorifique
DE2332411B2 (de) Rotationskolbenverdichter
DE102020207510A1 (de) Verdichtermodul sowie elektromotorischer Kältemittelverdichter
DE19949730B4 (de) Wassergekühlte Gaszuführvorrichtung
DE102012100720A1 (de) Ölleitsystem für einen Verdichter
EP4062067B1 (fr) Compresseur à spirales
EP4325056B1 (fr) Machine à spirales et système frigorifique
DE4221720B4 (de) Hydraulische Druckvorrichtung
DE102020109556B4 (de) Vorrichtungen zum Verdichten eines gasförmigen Fluids und Verfahren zum Betreiben der Vorrichtungen
EP4692550A1 (fr) Pompe à engrenages avec plusieurs trains d'engrenages à axes internes
EP4088030A1 (fr) Compresseur à spirale
DE102012025755B3 (de) Kältemittelscrollverdichter für Kraftfahrzeugklimaanlagen

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

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

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

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 ME MK MT NL NO PL PT RO RS SE SI SK SM TR

AK Designated contracting states

Kind code of ref document: A3

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 ME MK MT NL NO PL PT RO RS SE SI SK SM TR

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 29/12 20060101ALI20240228BHEP

Ipc: F04C 29/02 20060101ALI20240228BHEP

Ipc: F04C 23/00 20060101ALI20240228BHEP

Ipc: F04C 18/02 20060101AFI20240228BHEP

RIN1 Information on inventor provided before grant (corrected)

Inventor name: VARGA, THOMAS

Inventor name: SCHARER, CHRISTIAN

Inventor name: HAUSER, MARKUS

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20241001

RBV Designated contracting states (corrected)

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 ME MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20251031

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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 ME MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: F10

Free format text: ST27 STATUS EVENT CODE: U-0-0-F10-F00 (AS PROVIDED BY THE NATIONAL OFFICE)

Effective date: 20260318

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

P01 Opt-out of the competence of the unified patent court (upc) registered

Free format text: CASE NUMBER: UPC_APP_0006804_4336043/2026

Effective date: 20260225

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502023003396

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN