EP3568571A1 - Scroll-type machine - Google Patents
Scroll-type machineInfo
- Publication number
- EP3568571A1 EP3568571A1 EP18701983.1A EP18701983A EP3568571A1 EP 3568571 A1 EP3568571 A1 EP 3568571A1 EP 18701983 A EP18701983 A EP 18701983A EP 3568571 A1 EP3568571 A1 EP 3568571A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- scroll
- drive
- orbiting
- type displacement
- drive shaft
- 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.)
- Granted
Links
- 238000006073 displacement reaction Methods 0.000 claims abstract description 34
- 239000000314 lubricant Substances 0.000 claims description 35
- 239000012530 fluid Substances 0.000 claims description 25
- 230000009471 action Effects 0.000 claims description 15
- 230000008878 coupling Effects 0.000 claims description 12
- 238000010168 coupling process Methods 0.000 claims description 12
- 238000005859 coupling reaction Methods 0.000 claims description 12
- 230000003068 static effect Effects 0.000 claims description 6
- 238000005461 lubrication Methods 0.000 claims description 2
- 101150034459 Parpbp gene Proteins 0.000 claims 1
- 230000007246 mechanism Effects 0.000 abstract description 7
- 230000002265 prevention Effects 0.000 abstract 1
- 238000013461 design Methods 0.000 description 20
- 238000004519 manufacturing process Methods 0.000 description 12
- 230000006835 compression Effects 0.000 description 9
- 238000007906 compression Methods 0.000 description 9
- 238000012546 transfer Methods 0.000 description 9
- 239000007789 gas Substances 0.000 description 7
- 230000008859 change Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 239000007787 solid Substances 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 238000005304 joining Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 230000006870 function Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 238000009826 distribution Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000013011 mating Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000001052 transient effect Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000000356 contaminant Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000009740 moulding (composite fabrication) Methods 0.000 description 1
- 230000003134 recirculating effect Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 239000000565 sealant Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 239000013598 vector Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
- F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
-
- 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
- F04C18/023—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 both members are 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
Definitions
- the present invention generally relates to scroll-type displacement machines adapted as a compressor, expander (pneumatic motor), liquid pump, or hydraulic motor. More particularly, according to one aspect, the present invention relates to a so-called high-side machine, where the compressor mechanism within the casing is surrounded by high-pressure working fluid. According to another aspect, the present invention relates to a unique arrangement of the internal drive system which simplifies the manufacture of the scroll- type machine and which allows for easy adaptation to various motor types (ie. compressor or pump) or various power transfer devices (ie. expander or motor). According to a further aspect, the present invention relates to such a machine which uses an Oldham coupling (or ring) to prevent rotation of the orbiting scroll relative to the fixed scroll. According to yet another aspect, the present invention relates to hermetic or semi-hermetic compressors where the motor and compressor are sealed within an enclosure which contains the working fluid to be compressed.
- Scroll- type displacement machines are commonly employed as a compressor for various gases, including air and refrigerants. However, they are readily adapted for use as a compressed vapor expander (e.g. pneumatic motor), a liquid pump, or a hydraulic motor. In normal operation, scroll-type machines have high pressure in the center region of the scroll pair and low pressure around the outside periphery. Fluid flows from the outside to the inside for compressors and pumps and from the inside to the outside for expanders and motors.
- means are provided to isolate the high pressure fluid passing through the high pressure port in the fixed scroll, sometimes through a simple discharge tube attached to the fixed scroll and more commonly through a high pressure manifold or pulse volume integrated into the external housing and further communicating externally through a high- pressure tube or fitting.
- the low-pressure flow is connected directly to the scroll pair at the periphery and the high-pressure flow exits at the center of the scroll pair and passes through an external housing which contains the pressurized flow.
- the high pressure flow serves to cool the bearings and any other heat- generating components such as motors or sliding mechanisms.
- the orbiting scroll typically has a drive bearing located at the center of the scroll on the opposite side from the spiral vanes.
- the high pressure port is typically located at the center of the fixed scroll, on the opposite side of the scroll set from the drive bearing.
- the high- pressure port in the fixed scroll communicates directly with the interior of the external housing.
- an aspect of the invention is directed towards improvements over the state of the art as it relates to routing high pressure fluid in a high- side machine to avoid the disadvantages associated with conducting high pressure working fluid between a fixed scroll high pressure port and the external compressor housing.
- a drive shaft used either to input or to extract mechanical power, is provided with support bearing means to support radial loads and to allow free rotation of the drive shaft.
- an eccentric drive bearing which may take the form of an eccentric bearing, a so-called slider block, or an eccentric bushing, all serving to provide an eccentric drive to connect between the drive shaft and the orbiting scroll and to drive the orbiting scroll in a circular path, ie., a circular non-rotating orbit.
- the eccentric drive bearing may take the form of a bearing rigidly attached to the drive shaft and which drives the orbiting scroll through a fixed orbital radius or it may take the form of a so-called radially compliant drive where the radial position of the orbiting scroll relative to the drive shaft center is permitted to vary in response to rnisalignment and tolerance variations so as to maintain positive contact at all times between the vane walls of the orbiting scroll and the fixed scroll
- a counterweight arrangement is provided to achieve a dynamic balance among the various orbiting, rotating, and translating masses within the machine.
- a primary counterweight nearest the orbiting scroll provides a static balance for the machine.
- the axial spacing between the planes of unbalance of the moving components and the plane of action of the primary counterweight results in an overturning moment which tends to impose a wobbling- type load onto the shaft and consequently onto compressor frame which results in undesirable vibration
- a secondary counterweight is provided toward the end of the shaft opposite the orbiting scroll (on the other side of said primary counterweight) to create a counteracting overturning moment.
- An equivalent mass unbalance may also be added to the primary counterweight to maintain static balance.
- the scroll- type machine maybe said to have three counterweights: one larger counterweight to provide a static balance and two smaller counterweights of identical unbalance phased 180 degrees from each other and axially separated to provide a dynamic balance with one of the smaller counterweights at the same location as the larger
- the primary counterweight may thus consist of the combination of the larger counterweight and one of the smaller counterweights while the secondary counterweight is simply the other smaEer counterweight.
- the offset between the drive shaft center and the center of said eccentric drive bearing defines an angular reference which rotationaUy orients the drive shaft.
- the moving masses within the machine may all be defined by their axial position along the axis of the drive shaft and by their angular orientation relative to the eccentric drive bearing angular reference.
- the locations of the primary counterweight and the secondary counterweight are also defined by axial positions along the drive shaft axis and their angular positions relative to the eccentric drive bearing angular reference. The mass unbalances of these counterweights are chosen to counter the mass unbalances of all the moving masses.
- the drive means, the primary counterweight, and the secondary counterweight are all separate components located at separate axial locations along the drive shaft.
- the primary counterweight is interposed between the support bearing and the drive means and said secondary counterweight is placed at the opposite end of the drive shaft.
- locating means must be provided to position these counterweights property both axially and angularly onto the drive shaft.
- Such locating means may consist of locating features between the counterweights and the drive shaft, they may consist of external ftxturing, or they may consist of a combination of locating features and fjxturing. This construction requires fabrication, alignment, and assembly of a number of components during manufacture of the scroll machine, all of which adds to the cost of manufacture.
- the drive shaft and primary counterweight maybe combined into a single component but with the same general overall layout.
- the support bearing means typically includes two bearings supporting the main drive shaft which are in turn supported by a structure, frame or shell
- a motor for compressors or pumps
- a power transfer device e.g. a generator for expanders or hydraulic motors
- the motor or power transfer device is supported by the structure or frame and is located between the two bearings or just outboard of the two bearings.
- the rotor component of the motor or power transfer device is affixed onto the drive-shaft.
- both scrolls are adapted to rotate together on offset axes (as opposed to the conventional fixed- orbiting arrangement) but they both rotate at the same speed and the angular phasing between the two scrolls remains the same, which is to say they do not rotate relative to one another.
- a typical Oldham ring comprises a solid body, more or less ring-shaped.
- the body may be an oblong or irregular shape to fit around other features in the machine but it will generally follow the pattern of a closed ring.
- Axial or radial projections from the Oldham ring body are provided with axialfy extending surfaces or keyways which engage matching surfaces on the respective scrolls to complete the coupling assembly and to prevent relative rotation between the scrolls while permitting orbiting action.
- the ring-shaped portion of the Oldham ring is typically flat and of a more or less uniform thickness, being generally distributed about a radial plane at all points around the ring.
- a radial plane which passes through the centroid of the Oldham ring will divide the Oldham ring into two continuous ring-shaped portions.
- This dedicated space adds to the overall height (Le. axial length) of the scroll- type machine and thereby increases the size and weight of the scroll machine.
- an aspect of this invention is directed towards improvements over the state of the art as it relates to the design of an Oldham coupling to avoid the need for a dedicated axial space for the coupling and thereby to reduce the overall size of the displacement machine.
- the compressor and drive motor are contained within a sealed housing which isolates the working fluid from the outside environment.
- the vapor flows around the compressor and motor and provides cooling, especially for the motor.
- the drive motor typically an electric motor
- the motor stator is integrated into the compressor frame and the motor rotor is mounted directly onto the compressor shaft, which also incorporates the compressor drive means (e.g. eccentric bearing) and counterweights which may be placed on both sides of the motor or even attached directly to the rotor.
- This arrangement provides acceptable economy and simplicity by mininiizing the number of separate components that make up the motor and compressor combination
- a given compressor is then dedicated to a particular motor size and design
- Physical changes to the motor often require extensive changes to the compressor frame and drive shaft to accommodate the new motor.
- the motor lineup is typically standardized with common motor sizes and configurations found across a relatively limited selection of motor suppliers. There is seldom a need to change to a different size motor and the compressor design can be relatively stable with regard to motor selection.
- So another aspect of this invention is directed towards a general compressor design which allows use of a range of prepackaged motors of various sizes with minimal if any changes to the compressor or to the motor.
- the high-pressure port in a high- side scroll- type machine at the center of the orbiting scroll.
- the inlet or low pressure port may then be located in a radially outer portion of the fixed scroll which may have a solid baseplate thus avoiding any need to provide means for fluid communication between the fixed scroll and the compressor housing (which is at high pressure).
- high-pressure fluid passes directly from the center of the orbiting scroll over the drive bearing means that engages the orbiting scroll and thus through a path directly between the high pressure port and the interior of the compressor housing.
- Lubricant which is entrained in the vapor flow serves to lubricate the drive bearing means and other mechanical components in the displacement machine.
- This arrangement is well- suited to systems where the fluid flow is contained within a closed loop and a fixed quantity of recirculating lubricant is present.
- this may be easily adapted to open- cycle systems, where the fluid passes through the displacement machine once and does not recirculate, by providing means to inject lubricant into the inlet flow and optionally to extract it from the outlet flow.
- the high- side scroll machine is simpler, more compact, and easier to manufacture than an equivalent high side machine with the high pressure port at the center of the fixed scroll.
- the scroll machine combines the eccentric drive bearing means, the primary counterweight, and the secondary counterweight into a single component or module (referred to in the description as a widget) which may be affixed to the end of the drive shaft adjacent the orbiting scroll.
- This module is designed as a single, unitary piece suitable for casting, molding, forming, or machining operations so that the necessary counterweight sizes and locations relative to said eccentric drive bearing means are integral to the as-formed part and no subassembly, alignment operations, or alignment features are required. Since all angular relationships are built into the drive module there is no need for angular alignment of the drive module with the drive shaft.
- the module or widget is preferably designed to be fitted on to the end of a drive shaft although the module could also be formed integrally with the drive shaft.
- the drive module may be standardized in terms of the interface with the motor or the power transfer device so that a wide variety of motors or power transfer devices may be readily adapted to a particular scroll machine model.
- the drive shaft and shaft support bearing means may be packaged as part of the motor or power transfer device assembly. This allows ready access to a wide range of commercially produced motors or other drive devices with no significant design change required to integrate a variety of different devices into a scroll-type machine. Only details of device attachment, alignment, and the attachment of the drive module to the drive shaft need be considered. The rated bearing life of said device when applied to the scroll machine would simply be one of the product specifications along with other performance specifications.
- a still iurther aspect of the present invention is to improve the Oldham coupling for the scroll machine.
- the main body of the Oldham ring may be considered as being divided into four arc-shaped segments.
- a first pair of diametrically opposed segments bridges between and slidingry engages with the
- the first segment pair occupies around the same level, ie. the same axial position, as the orbiting scroll baseplate but not extending beyond the orbiting scroll floor surface.
- the space between the ends of the segment pairs is occupied by the Oldham key tabs on the orbiting scroll
- the first segment pair occupies otherwise unused space in the machine.
- the second pair of diametrically opposed segments (oriented generally at 90 degrees to the first pair) bridges between and slidingly engages with the corresponding Oldham coupling surfaces on the fixed scroll.
- the second segment pair occupies a level starting at around the floor of the orbiting scroll baseplate (also the fixed scroll tip surface) and extends away from the orbiting scroll floor but does not extend across the plane defined by the orbiting scroll floor. This makes the coupling arrangement more compact.
- the symmetry of the Oldham ring of this design eliminates any polarity or handedness, so that it is impossible to install improperly.
- the ends of the segment pairs can favorably be extended so that they overlap some reasonable distance in a common radial or lateral plane. With the segment pairs fused together at the overlap zones, the Oldham ring becomes a single solid object which may be fabricated by a number of methods.
- a still further aspect of the present invention is to design the scroll machine to permit incorporation of a prepackaged motor unit including stator, rotor, housing, bearings, and shaft, as is typical of commercially available motors.
- the motor unit can be attached to the compressor frame and a drive module may then be attached to the end of the motor shaft.
- the motor shaft and bearings serve as the main compressor shaft and bearings. Design changes, if any, accompanying a motor change are limited to details of the motor unit attachment to the compressor frame, and of the drive module attachment to the motor shaft.
- FIG. 1 is an exploded isometric view of a scroE-type machine, here a compressor according to one embodiment of this invention, viewed from the scroll end.
- Figure 2 is an exploded isometric view of the same compressor viewed from the motor end.
- Figure 3 depicts a cross- sectional isometric view of the same compressor.
- Figure 4 depicts a cross- sectional orthographic view of the same compressor.
- Figure 5 is an isometric view of a fixed scroll according to the present invention
- Figure 6 is an orthographic plan view of the same fixed scroll
- Figure 7 is an isometric view of an orbiting scroll seen from the front or vane side according to the present invention.
- Figure 8 is an isometric view of the orbiting scroE seen from the back or opposite of the vane side according to the present invention.
- Figure 9 is a cross-sectional orthographic side view of the same orbiting scroll.
- Figure 10 is an isometric view of an Oldham ring as used in the present invention.
- Figure 11 is an isometric view of an Oldham ring divided into sections showing a dividing plane.
- Figure 12 is a cross- sectional orthographic side view of the drive housing.
- Figure 13 is an orthographic representation of a motor as used in the present invention.
- Figure 14 is an isometric view of the drive widget as used in the present invention.
- Figure 15 is an orthographic plan view of the drive widget.
- Figure 16 is a cross- sectional orthographic side view of the drive widget.
- Figure 17 is a schematic representation of the drive system including the drive bearing and orbiting scroll drive hub.
- Figure 18 is a cross- sectional orthographic side view of the motor-compressor module.
- Figure 19 is a cross- sectional isometric view of the compressor housing.
- the scroE compressor 10 of this embodiment includes a motor- compressor module 1 1 with a drive gaEery 12.
- a motor chamber 14 is defined between the module 11 and a main compressor housing 80.
- the scroll pair is here shown as a fixed scroll 20 and a mating orbiting scroll 30, wherein the fixed scroll has an inlet (low-pressure) port 21 located on a radially outward portion, a fixed scroll spiral vane 22 having a tip suriace 23.
- the fixed scroll 20 also has a flat face 24, shoulder 25, pilot floor 26, with an outside diameter 27 and pilot diameter 28.
- At the center of the scroll vane is a blind recess or mirror port 29, which will be explained later.
- the orbiting scroll 30, which has a defined orbiting path 31 relative to the fixed scroll 20 has a scroll vane 32, a number of anti-thrust pads 33, a plurality of flat faces 34, a drive hub 35 on the side opposite the vane 32, with the drive hub having an inside diameter 36 defining a drive bearing contact point 37, a drive hub center 38 and a discharge port 39 that penetrates the scroll 30 more- or- less at the axis or center.
- a drive widget 40 for achieving the orbital motion of the scroll 30 is comprised of a shaft bore 41 , an eccentric crankpin 42 having a crankpin center 43, and a drive bearing 45 that has a predetermined drive bearing outside diameter 46.
- the shaft bore 41 has a shaft bore center 47 located at the main drive axis for the compressor.
- the drive widget 40 also includes a primary counterweight 48 and a secondary counterweight 49.
- an Oldham ring 50 here shown in the form of four arcuate segments, and whose shape defines key surfaces 54 that slidably engage the flat faces 24 and 34 of the fixed and orbiting scrolls 20 and 30, with the ring comprising a lateral dividing plane 56, a first segment pair 57 and a second segment pair 58.
- a drive housing 60 that houses the aforementioned components is shown with a back- flange surface 61, a flat motor- engaging surface 62, and a pilot bore 63; a flat face 66 for engaging the fixed scroll pilot floor 26, and having an outside diameter 68.
- An outlet port 69 permits the compressed working fluid vapor to pass through.
- Motive power for the orbiting scroll is provided here by an electric motor 70, having a motor shaft 71 with a shaft center or axis 77, a flat surface 72, and having pilot diameter 73.
- a set of motor bolts 74 or similar fasteners are provided to attach the motor to the drive housing.
- the compressor housing 80 is shown with a flat surface or flange 81 , an O-ring seal 83 and an annular O-ring groove 84, a retaining ring 85 and annular retaining ring groove 86, a bore 87, electrical feedthrough passage 88, and a discharge passage 89.
- scroE compressor 10 includes fixed scroll 20 and orbiting scroll 30.
- Fixed scroll 20 and orbiting scroll 30 comprise a
- scroll pair each having involute shaped vanes 22 and 32 respectively which interfit to form pairs of moveable sealed crescent-shaped pockets.
- the scroll- type principle is well-known in the art and may be employed to transport, compress, or expand various fluids and gases.
- the orbiting scroll 30 is driven through a circular path by means of drive widget 40 which includes eccentric crankpin 42 and drive bearing 45 which together urge orbiting scroll 30 into contact with fixed scroll 20.
- Orbiting scroll 30 and fixed scroll 20 contact each other through orbiting scroll vane 32 and fixed scroll vane 22.
- Drive widget 40 including drive bearing 45 further urges orbiting scroll 30 to move in a circular path which is defined by the geometry of orbiting scroll vane 32 and fixed scroll vane 22.
- the orbiting scroll 30 is constrained to move in a lateral plane without rotation by means of Oldham ring 50.
- Four of eight key surfaces 54 of Oldham ring 50 sEdingry engage fixed scroll 20 through a set of four flat faces 24 and the other four key surfaces 54 of Oldham ring 50 slidingy engage orbiting scroll 30 through a set of four flat faces 34.
- the Oldham ring is typically keyed between the scrolls as in the present invention or between the orbiting scroll and a fixed structure within the compressor such as a crankcase or bearing housing (e.g. drive housing 60). Keying to a fixed structure requires the additional step of angularly aligning the fixed scroll to the structure to provide the proper angular orientation between the orbiting scroll and the fixed scroll. Keying to a fixed structure offers the option to aEow the Oldham ring to fit behind the orbiting scroll, i.e.
- the body of the ring is typically a sold ring of a generally constant thickness evenly distributed about a lateral plane.
- Posts which extend axialfy from the body of the ring engage key-slots or flat laces on the two scroll components.
- the body of the ring maybe located between the two scrolls with posts extending from both sides of the body of the Oldham ring, or the body may be located beneath the orbiting scroll with posts extending from one side of the body of the Oldham ring and with some features keying directly into the adjacent orbiting scroll and some features extending beyond the orbiting scroll to key into the fixed scroll. In both cases, a specific axial space must be set aside for the body of the ring, all at a single leveL
- Oldham ring 50 is a single, solid component, it is conceptually made up of four segments placed at two different axial locations.
- Segment pair 57 extends between the four flat surfaces 34 or 24 of orbiting scroll 30 or fixed scroll 20, respectively, and segment pair 58 extends between the four flat surfaces 24 or 34 of the other scroll, i.e. fixed scroll 20 or orbiting scroll 30, respectively.
- Segment pairs 57 and 58 are joined together at their ends at a single plane of symmetry 56. As a general rule, portions of segment pair 57 do not cross over the plane into the side occupied by segment pair 58 and likewise portions of segment pair 8 do not cross over the plane into the side occupied by segment pair 57.
- Oldham ring 50 does not require a dedicated axial space to be set aside for it. Instead each segment pair extends only between their respective set of flat surfaces 24 or 34 and occupies axial space which would otherwise be unused within the compressor. If desired, segment pairs 57 and 58 may be even further removed from plane 56 with axialry extending segments joining the segment pairs 57 and 58 at the four pairs of segment ends. Oldham ring 50 has been designed to be fully symmetric in that segment pair 57 is identi-cal to segment pair 58 and Oldham ring 50 may be instaEed in any of four possible orientations in the compressor, ie. it is not possible to mis-assemble it.
- segment pair 57 or segment pair 58 may also be non- symmetric, in that segment pair 57 may comprise two different shaped segments or segment pair 58 may comprise two different shaped segments. But whether the ring is designed symmetrically or non-symmetrical y there will still be two segments operating on one side of a lateral plane 56 and two segments operating on the other side of plane 56.
- drive housing 60 nests within fixed scroll 20.
- Flat face 66 engages fixed scroll pilot floor 26 to establish axial position and perpendicularity between drive housing 60 and fixed scroll 20.
- Outside diameter 68 engages fixed scroll pilot diameter 28 to establish centerline concentricity between drive housing 60 and fixed scroll 20.
- the components are self-aKgning through this
- some or aE of this alignment between the fixed scroll 20 and drive housing 60 may be provided through external fkturing for some or aE alignment attributes with means provided to maintain alignment after the fixturing is removed.
- motor 70 is attached to drive housing 60 and motor shaft 71 extends into the scroE side of the drive housing.
- motor 70 is secured to drive housing 60 by three bolts 74 although other attachment means may be used.
- Motor 70 is aEgned axially and perpendicularly to drive housing 60 through flat surface 72 which engages flat surface 62 of drive housing 60.
- Motor 70 is aligned concentricaEy with drive housing 60 through pilot diameter 73 which engages pilot bore 63 of drive housing 60.
- motor 60 is an electric motor but it is understood that motor 60 could be a hydrauEc motor, pneumatic motor, or any other prime mover which provides a rotary output.
- drive widget 40 is attached to motor shaft 71. In this example the drive widget 40 is pressed onto the shaft 71 through an interference fit between shaft bore 41 and shaft 71 but it is understood that any of a wide variety of attachment methods maybe used, including combining drive widget 40 and shaft 71 into a single component.
- Drive widget 40 is aligned to the shaft 71 concentrically and perpendicularly through the press fit on the shaft 71.
- the axial position of drive widget 40 with respect to motor 70 may be determined by physical features in or adjacent the shaft bore 41 and motor shaft 71 or by external fkturing during manufacture or assembly.
- Drive bearing 45 is fitted over eccentric crankpin 42.
- drive bearing 45 is a baE bearing pressed on to the crankpin 42; however a number of other bearing types may be used including a solid disk with a smooth bore running directly against the eccentric crankpin 42.
- Drive bearing 45 is aligned to the drive widget 40 through the fit between drive bearing 45 and crankpin 42 and through axial locating features such as a mechanical stop or through external fkturing.
- Orbiting scroll 30 is interposed between fixed scroll 20 and drive bearing 45.
- the orbiting scroll 30 is not rigidly constrained to be in any one particular position or orientation relative to any other compressor components.
- Orbiting scroll 30 may freely move laterally or radially within the limits of the geometry of fixed and orbiting scroll vanes 22 and 32 and also within the limits of the radial clearance space between drive bearing 45 and drive hub inside diameter 36.
- Orbiting scroll 30 is free to move axially inside the clearance allowed within the space defined between the fixed scroll tip surface 23 and the flat face 66 of drive housing 60. In this way, when the compressor is not in operation, orbiting scroll 30 may be said to be "rattling loose" in the assembly with no particular position or orientation imposed upon it.
- drive bearing 45 is positioned within the orbiting scroll drive hub inside diameter 36 and, when driven by motor 70 through the drive widget 40, drive bearing outside diameter 46 acts against the drive hub inside diameter 36 at contact point 37 to urge the orbiting scroll vane 32 against the fixed scroll vane 22 in the lateral or radial plane and to follow a circular orbit path as defined by the resulting contact between fixed scroll vane 22 and orbiting scroll vane 32.
- Figure 17 shows a schematic representation of the drive bearing 45 with an outside diameter 46 and a drive bearing center 43 situated inside the drive hub 35 which has an inside diameter 36 and a center 38.
- Motor shaft center 77 is coincident with the center of fixed scroll 20 and defines the center of rotation for drive widget 40.
- the orbiting scroll is constrained through pressure and inertial loads to move in a circular orbit path 31 which is centered on fixed scroll 20 and which is defined by the respective geometries of fixed scroll vane 22 and orbiting scroll vane 32.
- the motor shaft 71 and thus also the drive widget 40 are rotating in a clockwise direction and drive bearing center 43 is also moving in a clockwise direction in a circular path centered on shaft center 77.
- Drive bearing outside diameter 46 contacts the drive hub inside diameter 36 at contact point 37 and the instantaneous direction of motion of the orbiting scroll 30 is to the right as indicated in Figure 17 even though drive bearing center 43 is moving down and to the right as also indicated in Figure 17. Assuming there is no slippage between drive bearing outside diameter 46 and drive hub inside diameter 36 at contact point 37 the difference in velocity vectors between the orbiting scroll center 38 and drive bearing center 43 results in a rolling action between drive bearing 40 and drive hub inside diameter 36. As a result of the rolling action, drive bearing outside diameter 46 will rotate in a counterclockwise direction as viewed in Figure 17 even though the drive system is rotating in a clockwise direction.
- the total rotational speed of drive bearing 45 relative to crankpin 42 will be the sum of the rotation induced by this reverse rolling action plus the rotational speed of the motor shaft 71.
- drive bearing 45 it is necessary to design drive bearing 45 to run at a somewhat higher rotational speed than that of the motor shaft 71.
- the contact force Fc between drive bearing outside diameter 46 and drive hub inside diameter 36 is applied at contact point 37 and is directed normal to the two surfaces 46 and 36 at the point of contact.
- This contact force Fc will have a component Ft which acts in the instantaneous direction of motion of the orbiting scroll 30. This force balances a gas compression force generated within the scroll pair which resists the action of drive bearing 45 and represents the force against which the work of compression is accomplished.
- the drive bearing center 43 is positioned so that the line of action of the contact force Fc acts at an angle a to the instantaneous direction of orbiting scroll motion.
- contact force Fc in addition to contact force Fc generating a tangential force component Ft in the direction of orbiting scroll motion to accomplish the work of compression, contact force Fc also generates a radial force component Fr which acts to push the orbiting scroll 30 radially outward to increase the loading between the orbiting scroll vane 32 and the fixed scroll vane 22. This may be done to counteract a radially inward-acting gas force generated by the scroll set which tends to separate the orbiting and fixed scroll vanes 32 and 22.
- the drive bearing center 43 may be repositioned to reduce or eliminate the outward- acting radial force component Fr of the contact force Fc or even to reverse the radial force component Fr to act radially inward against the centrifugal inertial action of the orbiting scroll 30 and thus to reduce the load between orbiting and fixed scroll vanes 32 and 22.
- drive widget 40 In addition to providing the function of the eccentric crankpin 42 and drive bearing 45, drive widget 40 also provides two counterweights, primary counterweight 48 and secondary counterweight 49.
- the size, location, and orientation of the two counterweights 48 and 49 are selected and calibrated so that the entire rotodynamic system defined by drive widget 40 including drive bearing 45, orbiting scroll 30, and Oldham ring 50 is in both static and dynamic balance.
- the three functions of the drive system Le. the mechanical drive, primary counterweight, and secondary counterweight, are normally carried out by separate components distributed at separate locations along a drive- shaft which also includes an integrated motor.
- the present invention decouples the mechanical drive function from the motor 70 and aEows either the drive system (drive widget 40 and orbiting scroll drive hub 35) or the motor 70 to be modified with little if any impact on the other. Additionally, the specific geometric relationships between the eccentric crankpin 42 and the two counterweights 48 and 49 are "locked in” to a single component instead of requiring assembly and alignment of various components in various operations. Any prime mover, whether electrical, hydraulic, pneumatic, or otherwise need only meet requirements of shaft output, radial shaft loading, and mechanical interface in order to be applied to this compressor. No significant redesign or retooling is needed to change from one motor type or design to another.
- Motor- compressor module 11 (including drive bearing 45), Oldham ring 50, drive housing 60, and motor 70 together form an integrated motor-compressor module 1 1 which maybe packaged and applied in a number of different ways.
- Motor- compressor module 11 is illustrated in Figure 18.
- motor- compressor module 1 1 is mounted within a semi-hermetic compressor housing 80.
- compressor housing 80 is illustrated in detail in Figure 19.
- the back- flange surface 61 of drive housing 60 seats against flat surface 81 of compressor housing 80 which establishes the axial position of motor- compressor module 11 within compressor housing 80.
- the fixed scroll outside diameter 27 matches the compressor housing bore 87 closely enough for a snug fit, which establishes the radial position (concentricity) of the fixed scroll 20 and thus the concentricity of the motor- compressor module 1 1 within compressor housing 80.
- a sealing element 83 fits within seal groove 84 in the side wall of bore 87 and seals against fixed scroll outside diameter 27.
- Beveled retaining ring 85 fits within retaining ring groove 86 of compressor housing 80 and seats against fixed scroll shoulder 25. The bevel-spring action of the retaining ring 85 loads and clamps drive module 1 1 within compressor housing 80. In this manner the motor- compressor module 1 1 is located and sealingly secured within compressor housing 80.
- Electrical feed- through 88 is/are provided to conduct motor power leads into the sealed space within compressor housing 80, and a discharge passage 89 is provided for compressed vapor to exit the compressor housing.
- This design concept may be easily converted to a hermetic- type compressor by eliminating the retaining ring 85 and joining the compressor housing 80 to the fixed scroll outside diameter 27 with some sort of vapor- tight seal such as welding, swaging, brazing, soldering, roll forming, crimping, bonding, or other suitable joining process.
- a ring type seal 83 or an applied sealant may optionally be used in addition to the joining process to assure gas-tightness of the joint.
- Suitable hermetic power terminals and piping connections would replace the corresponding threaded and gasketed components in this design example.
- the high- ressure discharge port 39 through the orbiting scroll floor directs the full discharge flow into the drive bearing system, which is unusual if not unique in current scroll practice.
- the normal arrangement has the discharge flowing through the fixed scroll 20 (with an open, through port in place of blind mirror port recess 29) with the space behind orbiting scroll 30 reserved for bearing, drive, and lubrication systems which are intentionally kept separate from the direct flow through the compressor.
- Mist- lubricated compressors including scroll- types as well as others, are also well- known in the art. They are most commonly applied in automotive air conditioning
- any and all lubricant and vapor passing through compressor 10 will be discharged through port 39, through and around drive bearing 45, and into drive gallery 12.
- the compressed vapor exits drive gallery 12 through outlet port 69 along with whatever lubricant remains entrained in the vapor flow.
- port 69 is at the top of drive gallery 12 in an effort to allow gravity to collect lubricant on the opposite side at the bottom of drive gaEery 12.
- Other means, such as baffles or deflectors within drive gallery 12 or around port 69 may be added to further separate the lubricant flow and to tend to retain lubricant within drive gallery 12. In this way drive gallery 12 tends to act as a lubricant sump, but one which is not managed. There are no means for lubricant pumping or distribution.
- Any lubricant delivery from the bottom of drive gallery 12 will be through splashing action of the moving parts and the turbulent vortex flow driven by the rotating drive widget 40.
- lubricant is returning from the system to compressor 10 through the suction flow there is no need for a lubricant reserve in drive gallery 12.
- This also provides a lubricant reserve for critical moving parts in the event of a transient loss of lubricant return.
- the discharge pressure acting on the drive hub side of orbiting scroll 30 serves to load it against the fixed scroll 20 in opposition to the internally pressure- generated axial force which tends to separate the scrolls. In this way the scrolls are pressure- loaded together for effective contact sealing between tip and floor surfaces.
- the compressor 10 will generate enough flow to create back pressure against the system restriction or load until enough pressure is developed to overcome the axial separating gas force and to axially load the orbiting scroll 30 against the fixed scroll 20. In this way the compressor "bootstraps" itself up from a balanced- pressure start.
- discharge passage 89 is placed at the bottom of motor chamber 14 to avoid creating "traps" or pockets where lubricant could collect away from the main vapor flow. Any carryover lubricant in the discharge vapor flow will be carried along by the flow and the force of gravity to discharge passage 89 and flows back to the system to be returned again to the compressor the next time around.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201762444962P | 2017-01-11 | 2017-01-11 | |
PCT/US2018/012872 WO2018132344A1 (en) | 2017-01-11 | 2018-01-09 | Scroll-type machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3568571A1 true EP3568571A1 (en) | 2019-11-20 |
EP3568571B1 EP3568571B1 (en) | 2021-11-03 |
Family
ID=61074565
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18701983.1A Active EP3568571B1 (en) | 2017-01-11 | 2018-01-09 | Scroll-type machine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3568571B1 (en) |
ES (1) | ES2905687T3 (en) |
WO (1) | WO2018132344A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20200085559A (en) * | 2019-01-07 | 2020-07-15 | 엘지전자 주식회사 | Motor operated compressor |
DE102022111379A1 (en) * | 2022-05-06 | 2023-11-09 | OET GmbH | Displacement machine based on the spiral principle |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2777415B2 (en) * | 1989-08-10 | 1998-07-16 | 三洋電機株式会社 | Scroll compressor |
US5152682A (en) * | 1990-03-29 | 1992-10-06 | Kabushiki Kaisha Toshiba | Scroll type fluid machine with passageway for innermost working chamber |
JP3509299B2 (en) * | 1995-06-20 | 2004-03-22 | 株式会社日立製作所 | Scroll compressor |
JP3274814B2 (en) * | 1996-12-27 | 2002-04-15 | サンデン株式会社 | Scroll fluid machine |
JP4310960B2 (en) * | 2002-03-13 | 2009-08-12 | ダイキン工業株式会社 | Scroll type fluid machinery |
KR101462941B1 (en) * | 2012-03-07 | 2014-11-19 | 엘지전자 주식회사 | Horizontal type scroll compressor |
-
2018
- 2018-01-09 WO PCT/US2018/012872 patent/WO2018132344A1/en unknown
- 2018-01-09 EP EP18701983.1A patent/EP3568571B1/en active Active
- 2018-01-09 ES ES18701983T patent/ES2905687T3/en active Active
Also Published As
Publication number | Publication date |
---|---|
EP3568571B1 (en) | 2021-11-03 |
ES2905687T3 (en) | 2022-04-11 |
WO2018132344A1 (en) | 2018-07-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8590324B2 (en) | Compressor and oil-cooling system | |
EP0078148B1 (en) | Biased drive mechanism for an orbiting fluid displacement member | |
JP2840716B2 (en) | Scroll machine | |
CN101297117B (en) | Scroll compressor | |
US10774833B2 (en) | Scroll-type machine | |
EP3568571B1 (en) | Scroll-type machine | |
US4934910A (en) | Scroll-type fluid apparatus with radially compliant driving means | |
US4854831A (en) | Scroll compressor with plural discharge flow paths | |
US6352418B1 (en) | Displacement type fluid machine | |
US5588819A (en) | Compliant drive for scroll machine | |
JPH0557438B2 (en) | ||
US20060133944A1 (en) | Scroll machine with brushless permanent magnet motor | |
US4811471A (en) | Method of assembling scroll compressors | |
US10941661B2 (en) | Scroll compressor having oldham coupling with key portions projecting from horizontal surfaces into key grooves | |
WO2016189801A1 (en) | Cylinder-rotation-type compressor | |
US7766633B2 (en) | Scroll compressor having a slider with a flat surface slidable and fitted in a notch part of a main shaft | |
US10815992B2 (en) | Scroll compressor having Oldham coupling with key portions and different width key gaps | |
US6179593B1 (en) | Displacement fluid machine | |
JP7439690B2 (en) | Compressor, compressor manufacturing method | |
JP3545826B2 (en) | Scroll compressor | |
CN113544360B (en) | Oldham coupling for co-rotating scroll compressor | |
US20060233654A1 (en) | Compressor with radial compliance mechanism | |
WO2018212076A1 (en) | Scroll compressor | |
KR19980079773A (en) | Scroll Compressor | |
JP2004003525A (en) | Scroll compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: UNKNOWN |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
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: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20190808 |
|
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 |
|
DAV | Request for validation of the european patent (deleted) | ||
DAX | Request for extension of the european patent (deleted) | ||
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: 20210517 |
|
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 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 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1444113 Country of ref document: AT Kind code of ref document: T Effective date: 20211115 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602018026044 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20211103 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1444113 Country of ref document: AT Kind code of ref document: T Effective date: 20211103 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2905687 Country of ref document: ES Kind code of ref document: T3 Effective date: 20220411 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20211103 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: 20211103 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: 20211103 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: 20220203 Ref country code: AT 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: 20211103 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20220120 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20220303 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: 20220303 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: 20211103 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: 20220203 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: 20211103 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: 20211103 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: 20211103 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: 20220204 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20220128 Year of fee payment: 5 Ref country code: ES Payment date: 20220201 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20211103 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: 20211103 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: 20211103 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: 20211103 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: 20211103 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: 20211103 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602018026044 Country of ref document: DE |
|
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: 20211103 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
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: 20220804 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20220109 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: 20211103 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20211103 |
|
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: 20220131 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220131 |
|
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: 20220109 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230124 Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230125 Year of fee payment: 6 Ref country code: DE Payment date: 20230124 Year of fee payment: 6 Ref country code: BE Payment date: 20230131 Year of fee payment: 6 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20230109 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20230110 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230109 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20240229 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230110 |