EP2198125B1 - Screw compressor pulsation damper - Google Patents

Screw compressor pulsation damper Download PDF

Info

Publication number
EP2198125B1
EP2198125B1 EP07839131.5A EP07839131A EP2198125B1 EP 2198125 B1 EP2198125 B1 EP 2198125B1 EP 07839131 A EP07839131 A EP 07839131A EP 2198125 B1 EP2198125 B1 EP 2198125B1
Authority
EP
European Patent Office
Prior art keywords
slide
screw compressor
screw
pocket
discharge
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.)
Revoked
Application number
EP07839131.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2198125A4 (en
EP2198125A1 (en
Inventor
Paul J. Flanigan
Bruce A. Fraser
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.)
Carrier Corp
Original Assignee
Carrier Corp
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40526475&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2198125(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2198125A1 publication Critical patent/EP2198125A1/en
Publication of EP2198125A4 publication Critical patent/EP2198125A4/en
Application granted granted Critical
Publication of EP2198125B1 publication Critical patent/EP2198125B1/en
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • 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
    • F04C29/06—Silencing
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/14—Pulsations

Definitions

  • Screw compressors typically comprise a pair of counter-rotating, mating male and female screws that have an intermeshing plurality of lands and channels, respectively, that narrow from an inlet end to a discharge end such that an effluent working fluid or gas, or some other such working matter, is reduced in volume as it is pushed through the screws.
  • the discharged working matter is released in pulses as each mating land and channel pushes a volume of the working matter out of the compressor.
  • Each pulse comprises a burst of wave energy that propagates through the working matter and the screw compressor as the working matter leaves the screws.
  • the screw compressors are typically turned by motors operating at speeds such that the wave pulsations are discharged at a high frequency.
  • the pulsations not only produce vibration of the screw compressor, but also produce noise that is amplified by the working matter and the compressor. Such vibration is undesirable as it wears components of the compressor and produces additional noise as the compressor vibrates. Noise from the discharging working matter and vibrating compressor is undesirable as it results in loud operating environments.
  • Previous attempts to counteract these problems have involved mufflers, padded mounts and clamps that are mounted external to the screw compressor. These solutions do not address the underlying source of the noise and vibration and only provide after-the-fact countermeasures. In addition to adding cost and weight, such solutions provide only limited noise reduction and do not prevent wear on internal screw compressor components.
  • Other solutions have proposed acoustic barriers that prevent pulsation damage to screw compressor components, but do not attenuate screw compressor noise or vibration. There is, therefore, a need for screw compressors having reduced effects from discharge pulsations.
  • US 3,146,720 discloses a positive displacement pump with sound attenuating means, and the features in the preamble to claim 1 are disclosed in US 2006/0165543 .
  • the present invention provides a screw compressor in accordance with claim 1.
  • Exemplary embodiments of the invention include a screw compressor comprising a housing, a slide valve assembly and a pulsation damper.
  • the housing receives a supply of working matter from a pair of intermeshing screw rotors, and comprises a slide recess, a pressure pocket, and a piston cylinder.
  • the slide valve assembly regulates the capacity of the screw compressor, and comprises a slide valve axially movable within the slide recess and the pressure pocket, a piston head axially movable within the piston cylinder, and a piston shaft connecting the slide valve with the piston head.
  • the pulsation damper comprises a flange for separating the pressure pocket from the piston cylinder, a bore for receiving the piston rod, and a damping channel extending through the flange for damping pressure pulsations in the working matter discharged from the pair of intermeshing screw rotors.
  • FIG. 1 shows a partially cutaway perspective view of screw compressor 10, which compresses a working fluid or gas such as a refrigerant that is typically used in refrigeration or air conditioning systems.
  • Screw compressor 10 includes rotor case 12, outlet case 14, slide case 16, male screw rotor 18, female screw rotor 20, drive motor 22 and slide valve assembly 23.
  • Male screw rotor 18 and female screw rotor 20 are disposed within rotor case 12 and include shafting and bearings such that they can be rotationally driven by drive motor 22.
  • male screw rotor 18 includes shaft 24A (which extends axially through rotor case 12 and into motor 22 and rests on bearing 26A), and shaft 24B (which extends axially into outlet case 14 and rests in bearing 26B).
  • Refrigerant is introduced into rotor case 12 at suction port 28, directed around motor 22 and into suction pocket 30 at the inlet of screw rotors 18 and 20.
  • Male screw rotor 18 and female screw rotor 20 include meshing grooves and lands that form helical flow paths having decreasing cross sectional areas as the grooves and lands extend from suction pocket 30.
  • the refrigerant is reduced in volume and pressurized as the refrigerant is directed into discharge pocket 32 by screw rotors 18 and 20, before being discharged at pressure port 34 and released to, for example, a condenser or evaporator of a cooling system.
  • Slide valve assembly 23 which includes slide valve 36, piston rod 38, piston head 40 and spring assist 42, regulates the discharge capacity of screw compressor 10.
  • piston head 38, piston rod 40 and spring assist 42 through a control system, translate slide valve 36 axially between rotors 18 and 20 to vary the volume of refrigerant compressed in the helical flow paths.
  • motor 22 drives screw rotors 18 and 20
  • the multiple sets of meshing grooves and lands comprising the helical flow paths discharge the refrigerant into pressure pocket 32 in a series of high frequency pulsations, which effectuates undesirable noise and vibration.
  • Outlet case 14 includes a pulsation damper that mitigates the pulsation effects of the discharged refrigerant.
  • screw compressor 10 comprises a two-screw compressor.
  • the present invention is readily applicable to compressors having three, four our more screw rotors that employ a reciprocating slide valve system.
  • FIG. 2 shows a schematic diagram of screw compressor 10 of FIG. 1 , having pulsation damping means of the present invention.
  • outlet case 14 includes damping channels 46A and 46B that attenuate the pulsation effects of refrigerant R within screw compressor 10.
  • Screw compressor 10 also includes rotor case 12, slide case 16, female screw rotor 20, drive motor 22, slide valve assembly 23 (including slide valve 36, piston rod 38, piston head 40 and spring assist 42) and control system 48.
  • Rotor case 12 includes slide recess 51, slide stop 52 and recirculation passage 53.
  • Slide case 16 includes piston cylinder 54, and outlet case 14 includes rod flange 58.
  • rotor case 12, outlet case 14 and slide case 16 comprise a sealed flow path for directing refrigerant R through screw compressor 10.
  • Refrigerant R is directed into rotor case 12 at suction port 28, and routed around motor 22 to suction pocket 30.
  • Refrigerant R from suction pocket 30 is compressed by male screw rotor 18 (not shown) and female screw rotor 20 and discharged into pressure pocket 32.
  • Female screw rotor 20 includes screw channels, or grooves, 50A - 50D that mesh with mating lands or lobes on male screw rotor 18 to form a sealed, decreasing-volume flow path. The sealed flow path decreases in volume such that refrigerant R is pushed and compressed as it moves from suction pocket 30 to discharge pocket 32.
  • refrigerant R enters, for example, screw channel 50A at suction pocket 30 having pressure P 1 and is discharged from the same screw channel 50A at discharge pocket 32 having elevated pressure P 2 .
  • each screw channel delivers a small volume of refrigerant R to discharge pocket 32.
  • Outlet case 14 includes damping channels 46A and 46B, which act as pulsation dampers to reduce the noise and vibration effects of refrigerant R as it is discharged from screw rotors 18 and 20.
  • Outlet case 14 which includes discharge pocket 32, is disposed between rotor case 12 and slide case 16 such that it receives the high pressure side of screw rotors 18 and 20 at a first end, and piston rod 38 of slide assembly 23 at a second end.
  • Slide valve 36 of slide assembly 23 is positioned within slide recess 51 of rotor case 12 such that it is disposed between male screw rotor 18 and female screw rotor 20.
  • Slide valve 36 is connected with piston rod 38 and piston head 40 such that slide valve 36 can be axially withdrawn from slide recess 51 and extended into pressure pocket 32 to control the amount of pressurized refrigerant R entrained within screw channels 50A - 50D.
  • slide valve 36 can be extended to the fully-loaded position (to the left in FIG.
  • screw compressor 10 is maximized by maximizing the amount of refrigerant R compressed in the lands and grooves of screw rotors 18 and 20. From the fully-loaded position, slide valve 36 is moved toward discharge pocket 32 (to the right in FIG. 1 ) to open recirculation passage 53, decreasing the discharge capacity of screw compressor 10.
  • Piston rod 38 extends through rod flange 58 to connect slide valve 36 within rotor case 12 to piston head 40 disposed within piston cylinder 54 of slide case 16.
  • Piston head 40 includes first pressure side 56A, which is exposed to refrigerant R at pressure P 2 , and second pressure side 56B, which is exposed to control oil at pressure P 3 .
  • Pressure P 2 is dictated by refrigerant R and screw rotors 18 and 20, while pressure P 3 is regulated by control system 48.
  • control system 48 Based on the loading (i.e. cooling demands) of the refrigerator or air conditioner to which screw compressor 10 is connected, control system 48, which comprises switches, valves, solenoids and the like, selectively provides control oil to piston cylinder 54.
  • Control oil is admitted into piston cylinder 48 to increase pressure P 3 to exert a force on second pressure side 56B to move slide valve 36 toward slide stop 52 within slide recess 51.
  • Pressure P 3 is reduced by removing control oil from piston cylinder 54 such that slide valve 36 can be withdrawn from slide recess 51.
  • Spring assist 42 pushes on first pressure side 56A to assist in withdrawing slide valve 36 from slide recess 51.
  • Piston head 40 is also in contact with refrigerant R, which exerts pressure P 2 on first pressure side 56A to push piston head 40 away from rod flange 58.
  • Refrigerant R is admitted into piston cylinder 54 through damping channels 46A and 46B disposed within rod flange 58.
  • Damping channels 46A and 46B, piston cylinder 54 and rod flange 58 are configured to attenuate vibration and noise associated with the discharge of refrigerant R from screw rotors 18 and 20. Specifically, damping channels 46A and 46B act in concert with piston cylinder 54 to provide a Helmholtz resonator to absorb energy from the discharged pulses of refrigerant R.
  • FIG. 3 shows a partially cutaway perspective view of slide valve assembly 23 of FIG. 2 , in which damping channels 46A - 46C of rod flange 58 are shown.
  • Slide valve assembly 23 also includes slide valve 36, piston rod 38, piston head 40 and spring assist 42, which is omitted in FIG. 3 for clarity.
  • Slide valve assembly 23 extends axially through rotor case 12, outlet case 14 and slide case 16 along an actuation path defined by slide recess 51, pressure pocket 32 and piston cylinder 54.
  • Outlet case 14 is positioned within screw compressor 10 such that first end A connects with rotor case 12, and second end B connects with slide case 16.
  • Slide valve 36 extends from slide recess 51 in rotor case 12 where it is disposed between rotor screws 18 and 20, and into pressure pocket 32 within outlet case 14.
  • Piston rod 38 extends axially from slide valve 36 through central bore 60 in rod flange 58 of outlet case 14, and into piston cylinder 54 of slide case 16 where rod 38 connects with piston head 40.
  • Rod flange 58 comprises a collar positioned on second end B of outlet case 14 such that central bore 60 axially aligns with slide recess 51 (in which slide valve 36 translates within rotor case 12) and piston cylinder 54 (in which piston head 40 translates within slide case 16).
  • rod flange 58 is integrally cast or formed with outlet case 14 along second end B.
  • Rod flange 58 separates piston cylinder 54 from slide recess 51 and pressure pocket 32 to form two separate chambers for refrigerant R.
  • Rod flange 58 is provided with seal or bearing ring 62 and is attached to rod flange 58 with snap rings 64A and 64B, which are disposed within grooves in ring 62.
  • ring 62 comprises a seal and prevents refrigerant R from entering piston cylinder 54 between piston rod 38 and rod flange 58 at bore 60.
  • seal ring 62 comprises a bearing that assists in sliding of piston rod 38 though rod flange 58 as well as performing sealing functions. Damping channels 46A - 46C, however, permit refrigerant R to enter piston cylinder 54 within slide case 16.
  • Slide case 16 comprises piston cylinder 54, which forms an annular extension of outlet case 14 to accommodate piston rod 38 and piston head 40.
  • Piston head 40 divides piston cylinder 54 into discharge side 54A and control side 54B.
  • Piston head 40 includes seal 65 to prevent flow of control oil and refrigerant R past piston head 40.
  • Piston cylinder 54 therefore, comprises a sealed canister for actuating piston head 40.
  • Discharge side 54A of this sealed canister also acts as a resonance chamber, that along with damping channels 46A - 46C, absorb some of the vibrational and acoustical effects of the pulsed discharges of refrigerant R.
  • slide valve assembly 23 is connected with control system 48 ( FIG. 2 ) to actuate the position of slide valve 36 along rotor screws 18 and 20.
  • Slide valve 36 is translated to regulate the discharge capacity of refrigerant R from screw rotors 18 and 20.
  • Control system 48 regulates flow of the control oil into control side 54B of piston cylinder 54 to vary pressure P 3 .
  • Refrigerant R flows into damping channels 46A - 46C into piston cylinder 54 within slide case 16 to pressurize discharge side 54A of piston cylinder 54 to pressure P 2 .
  • Refrigerant R is compressed to pressure P 2 between screw rotors 18 and released in pulsed discharges into pressure pocket 32 at slide valve 36 as screw rotors 18 and 20 counter-rotate to open and close the helical flow paths formed by the lobes and channels.
  • the pulsed discharges of refrigerant R flow past rod flange 58 before being discharged from screw compressor 10 at pressure port 34 ( FIG. 1 ).
  • Damping channels 46A - 46C extend through rod flange 58 and permit refrigerant R to enter and pressurize piston cylinder 54 to pressure P 2 .
  • rod flange 50 includes four damping channels: damping channels 46A - 46C, each disposed in a quadrant of rod flange 50, and a fourth damping channel omitted due to the section taken out of FIG. 3 .
  • Damping channels 46A - 46C comprise hollowed-out chambers extending through rod flange 58 of outlet case 14. The lengths of damping channels 46A - 46C are determined by the thickness of rod flange 58, but can be altered by inserting hollow damping tubes 66A - 66C into damping channels 46A - 46C.
  • Damping tubes 66A - 66C are inserted into damping channels 46A - 46C such that they extend into piston cylinder 54 and into pressure pocket 32. As is illustrated in FIG. 3 , damping tube 66A is inserted into damping channel 46A, and damping tube 66B is inserted into damping channel 46B. In the embodiment shown, damping tubes 66A - 66C each having the same length and the same diameter. In one embodiment, damping tubes 66A - 66C comprise stainless steel tubes press fit into damping channels 46A - 46C.
  • damping channels 46A - 46C and damping tubes 66A - 66C is selected to dampen the acoustic and vibrational pulsation effects of refrigerant R, and can thus vary depending on the specific design parameters of screw compressor 10. Specifically, the number, length and diameter of damping tubes 66A - 66C are selected to extract the maximum amount of energy from refrigerant R as refrigerant R travels through tubes 66A - 66C into the resonance chamber formed by discharge side 54A.
  • Refrigerant R is discharged from screw rotors 18 and 20 in pulses at regular intervals having a frequency dictated by the speed at which motor 22 drives screw rotors 18 and 20. These pulses therefore produce undesirable sound waves that increase the noise generated by screw compressor 10. The energy contained in these sound waves, however, can be used to do work to attenuate the propagation of the sound waves from screw compressor 10.
  • Outlet case 14 and slide case 16 are configured to function as a Helmholtz resonator, which comprises a container of fluid or gas having a necked opening, such as is produced by discharge side 54A, refrigerant R and channels 46A - 46C.
  • a Helmholtz resonator utilizes the spring-like compressibility of the fluid or gas to extract energy from a wave oscillating at a given frequency.
  • Refrigerant R fills discharge side 54A such that additional refrigerant attempting to enter discharge side 54A through channels 46A - 46C must compress the volume of refrigerant R already present within discharge side 54A.
  • a pulsed wave of refrigerant R attempting to enter discharge side 54A compresses refrigerant R until the crest of the wave is reached. Then, the pressurized refrigerant R within discharge side 54A will push back as the wave dissipates to the trough.
  • the pressurized refrigerant R within discharge side 54A continues to compress and decompress, thus extracting energy from refrigerant R discharged from screw rotors 18 and 20.
  • the energy extraction reduces the amplitude of the pulsation wave, thereby reducing noise and vibration generated by the pulsed discharges of refrigerant R.
  • a Helmholtz resonator extracts the maximum amount of energy from the fluid or gas when the frequency of the wave matches the natural or resonance frequency of the Helmholtz resonator.
  • the resonance frequency of the Helmholtz resonator produced by discharge side 54A and damping channels 46A - 46C can be configured to match that of the pulsation discharges of refrigerant R as produced by motor 22.
  • Equation (1) illustrates the resonance frequency of an elongate tube used in a Helmholtz resonator, where f R is the resonance frequency of the tube, v is the speed of sound in the medium filling the tube, A 0 is the area of the tube, L is the length of the tube and V 0 is the volume of resonance chamber.
  • f R v 2 ⁇ A 0 V 0 L
  • the tube or "necked opening" of the Helmholtz resonator comprises the aggregate of tubes 66A - 66C.
  • f R is the resonance frequency of tubes 66A - 66C
  • v is the speed of sound in refrigerant R
  • a 0 is the total cross-sectional area of tubes 66A - 66C
  • L is the length of one of tubes 66A - 66C
  • V 0 is the volume of discharge side 54A.
  • the dimensions of tubes 66A - 66C are selected such that the frequency of the discharge pulses of refrigerant R from screw rotors 18 and 20 at a given capacity matches the resonance frequency of the tubes.
  • screw compressor 10 is configured to operate at 3,600 RPM at full load.
  • Volume V 0 therefore, comprises the volume of discharge side 54A when piston head 40 is furthest away from rod flange 50 (all the way to the left in FIG. 3 ), and frequency f R is 60 Hz.
  • the areas and lengths of tubes 66A - 66C are selected based on other design requirements, such as dimensional constraints of rod flange 58 and slide case 16. Additionally, the number of tubes can be selected based on specific design considerations. In the embodiment shown, tubes 66A - 66C have the same lengths and diameters.
  • screw compressor 10 is provided with a pulsation damper that is configured for damping pulsation effects of refrigerant R at a specific operating condition.
  • tubes 66A - 66C can have different geometries, such as different lengths and/or different diameters, such that the pulsation damper is tuned to one specific resonance frequency, or can attenuate vibration and acoustic effects over a range of frequencies.
  • rod flange 58 comprises a circular disk or annular ring that can be bolted or otherwise secured to piston cylinder 54 within slide case 16 such that pulsation dampers configured for different resonance frequencies can be interchangeably installed into screw compressor 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP07839131.5A 2007-10-01 2007-10-01 Screw compressor pulsation damper Revoked EP2198125B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/021144 WO2009045187A1 (en) 2007-10-01 2007-10-01 Screw compressor pulsation damper

Publications (3)

Publication Number Publication Date
EP2198125A1 EP2198125A1 (en) 2010-06-23
EP2198125A4 EP2198125A4 (en) 2013-07-24
EP2198125B1 true EP2198125B1 (en) 2017-06-21

Family

ID=40526475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07839131.5A Revoked EP2198125B1 (en) 2007-10-01 2007-10-01 Screw compressor pulsation damper

Country Status (5)

Country Link
US (1) US20100209280A1 (zh)
EP (1) EP2198125B1 (zh)
CN (1) CN101809251B (zh)
ES (1) ES2629981T3 (zh)
WO (1) WO2009045187A1 (zh)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4401408B2 (ja) * 2007-08-30 2010-01-20 日立アプライアンス株式会社 スクリュー圧縮機の容量制御装置
JP5683426B2 (ja) * 2011-10-05 2015-03-11 株式会社神戸製鋼所 スクリュ圧縮機
DE102012103604A1 (de) * 2012-04-24 2013-10-24 C. & E. Fein Gmbh Handführbare Werkzeugmaschine mit Gehäuse
KR101543660B1 (ko) 2013-12-24 2015-08-11 동부대우전자 주식회사 압축기 및 맥동저감 밸브조립체
KR101560696B1 (ko) 2013-12-24 2015-10-15 동부대우전자 주식회사 압축기 및 토출 머플러
CN107208643A (zh) * 2015-06-11 2017-09-26 伊顿公司 轴承板消音器
US10830239B2 (en) 2015-08-11 2020-11-10 Carrier Corporation Refrigeration compressor fittings
CN107850071B (zh) 2015-08-11 2021-01-22 开利公司 用于脉动降低的螺杆式压缩机节能器增压室
US10941776B2 (en) 2015-10-02 2021-03-09 Carrier Corporation Screw compressor resonator arrays
US10180140B2 (en) 2016-09-30 2019-01-15 Ingersoll-Rand Company Pulsation damper for compressors
CN106382231B (zh) * 2016-11-04 2023-10-20 西安交通大学苏州研究院 一种主动衰减螺杆压缩机气流脉动装置
WO2018091939A1 (en) 2016-11-15 2018-05-24 Carrier Corporation Lubricant separator with muffler
US11808264B2 (en) 2018-10-02 2023-11-07 Carrier Corporation Multi-stage resonator for compressor
CN113513474B (zh) * 2020-04-09 2023-02-21 江森自控空调冷冻设备(无锡)有限公司 螺杆压缩机、制冷系统和制冷系统的控制方法

Family Cites Families (65)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2519913A (en) * 1943-08-21 1950-08-22 Jarvis C Marble Helical rotary compressor with pressure and volume regulating means
US3146720A (en) * 1961-12-06 1964-09-01 Dresser Ind Pressure relief means for pump
US3151806A (en) * 1962-09-24 1964-10-06 Joseph E Whitfield Screw type compressor having variable volume and adjustable compression
US3874828A (en) * 1973-11-12 1975-04-01 Gardner Denver Co Rotary control valve for screw compressors
GB1517156A (en) * 1974-06-21 1978-07-12 Svenska Rotor Maskiner Ab Screw compressor including means for varying the capacity thereof
US3936239A (en) * 1974-07-26 1976-02-03 Dunham-Bush, Inc. Undercompression and overcompression free helical screw rotary compressor
US4076461A (en) * 1974-12-09 1978-02-28 Dunham-Bush, Inc. Feedback control system for helical screw rotary compressors
JPS5930919B2 (ja) * 1974-12-24 1984-07-30 北越工業 （株） 液冷式回転圧縮機の液量及び気体容量調整装置
USRE29597E (en) * 1975-07-18 1978-03-28 Chem Systems Inc. Process for the production of epoxides
US4018583A (en) * 1975-07-28 1977-04-19 Carrier Corporation Refrigeration heat recovery system
US4137018A (en) * 1977-11-07 1979-01-30 General Motors Corporation Rotary vane variable capacity compressor
JPS54163416A (en) * 1978-06-14 1979-12-26 Hitachi Ltd Screw compressor
US4222716A (en) * 1979-06-01 1980-09-16 Dunham-Bush, Inc. Combined pressure matching and capacity control slide valve assembly for helical screw rotary machine
SE427063B (sv) * 1979-06-08 1983-02-28 Stal Refrigeration Ab Kompressor av rotationstyp med varierbart inbyggt volymsforhallande
FR2459384A1 (fr) * 1979-06-18 1981-01-09 Zimmern Bernard Procede de regulation asymetrique de compresseurs monovis
US4351160A (en) * 1980-06-16 1982-09-28 Borg-Warner Corporation Capacity control systems for screw compressor based water chillers
US4342199A (en) * 1980-10-03 1982-08-03 Dunham-Bush, Inc. Screw compressor slide valve engine RPM tracking system
US4388048A (en) * 1981-03-10 1983-06-14 Dunham Bush, Inc. Stepping type unloading system for helical screw rotary compressor
US4412788A (en) * 1981-04-20 1983-11-01 Durham-Bush, Inc. Control system for screw compressor
US4457681A (en) * 1981-06-16 1984-07-03 Frick Company Volume ratio control means for axial flow helical screw type compressor
US4455131A (en) * 1981-11-02 1984-06-19 Svenska Rotor Maskiner Aktiebolag Control device in a helical screw rotor machine for regulating the capacity and the built-in volume ratio of the machine
SE430709B (sv) * 1982-04-30 1983-12-05 Sullair Tech Ab Skruvkompressor med anordning for reglering av inre kompressionen skruvkompressor med anordning for reglering av inre kompressionen
US4516914A (en) * 1982-09-10 1985-05-14 Frick Company Micro-processor control of moveable slide stop and a moveable slide valve in a helical screw rotary compressor
GB2159980B (en) * 1982-09-10 1987-10-07 Frick Co Micro-processor control of compression ratio at full load in a helical screw rotary compressor responsive to compressor drive motor current
US4508491A (en) * 1982-12-22 1985-04-02 Dunham-Bush, Inc. Modular unload slide valve control assembly for a helical screw rotary compressor
SE444601B (sv) * 1983-10-24 1986-04-21 Stal Refrigeration Ab Anordning for reglering av volymkapaciteten hos en skruvkompressor
US4575323A (en) * 1984-05-23 1986-03-11 Kabushiki Kaisha Kobe Seiko Sho Slide valve type screw compressor
JPS61265381A (ja) * 1985-05-20 1986-11-25 Hitachi Ltd スクリユ−圧縮機のガス噴射装置
JPS6255487A (ja) * 1985-09-02 1987-03-11 Toyoda Autom Loom Works Ltd 可変容量型ベ−ン圧縮機
SE464656B (sv) * 1986-01-31 1991-05-27 Stal Refrigeration Ab Lyftventil foer rotationskompressor
SE451394B (sv) * 1986-01-31 1987-10-05 Stal Refrigeration Ab Forfarande for reglering av en rotationskompressor
US4678406A (en) * 1986-04-25 1987-07-07 Frick Company Variable volume ratio screw compressor with step control
SE461927B (sv) * 1987-10-15 1990-04-09 Svenska Rotor Maskiner Ab Roterande deplacementskompressor med anordning foer reglering av dess inre volymfoerhaallande
SE461052B (sv) * 1988-04-25 1989-12-18 Svenska Rotor Maskiner Ab Lyftventil vid en skruvrotormaskin
SE464885B (sv) * 1988-04-25 1991-06-24 Svenska Rotor Maskiner Ab Skruvkompressor med lyftventil
US4878818A (en) * 1988-07-05 1989-11-07 Carrier Corporation Common compression zone access ports for positive displacement compressor
US4909716A (en) * 1988-10-19 1990-03-20 Dunham-Bush Screw step drive internal volume ratio varying system for helical screw rotary compressor
SE463223B (sv) * 1989-02-17 1990-10-22 Svenska Rotor Maskiner Ab Skruvrotormaskin med ljuddaempare
JPH0792065B2 (ja) * 1990-06-30 1995-10-09 株式会社神戸製鋼所 スクリュ圧縮機
US5044894A (en) * 1990-11-30 1991-09-03 Carrier Corporation Capacity volume ratio control for twin screw compressors
SE468325B (sv) * 1991-05-14 1992-12-14 Svenska Rotor Maskiner Ab Roterande foertraengningskompressor och foerfarande foer reglering av en roterande foertraengningskompressor
US5183395A (en) * 1992-03-13 1993-02-02 Vilter Manufacturing Corporation Compressor slide valve control
US5832737A (en) * 1996-12-11 1998-11-10 American Standard Inc. Gas actuated slide valve in a screw compressor
US5979168A (en) * 1997-07-15 1999-11-09 American Standard Inc. Single-source gas actuation for screw compressor slide valve assembly
US6135744A (en) * 1998-04-28 2000-10-24 American Standard Inc. Piston unloader arrangement for screw compressors
JPH11324919A (ja) * 1998-05-11 1999-11-26 Toyota Autom Loom Works Ltd 共振抑制方法および共振抑制装置
US6195889B1 (en) * 1998-06-10 2001-03-06 Tecumseh Products Company Method to set slot width in a rotary compressor
US6467287B2 (en) * 2000-08-15 2002-10-22 Thermo King Corporation Valve arrangement for a compressor
US6302668B1 (en) * 2000-08-23 2001-10-16 Fu Sheng Industrial Co., Ltd. Capacity regulating apparatus for compressors
US6530221B1 (en) * 2000-09-21 2003-03-11 Siemens Westinghouse Power Corporation Modular resonators for suppressing combustion instabilities in gas turbine power plants
US6659729B2 (en) * 2001-02-15 2003-12-09 Mayekawa Mfg. Co., Ltd. Screw compressor equipment for accommodating low compression ratio and pressure variation and the operation method thereof
KR100400517B1 (ko) * 2001-04-28 2003-10-08 삼성광주전자 주식회사 왕복동식 압축기의 밸브어셈블리
US6638043B1 (en) * 2002-06-28 2003-10-28 Carrier Corporation Diffuser for high-speed screw compressor
US6692243B1 (en) * 2002-08-27 2004-02-17 Carrier Corporation Screw compression flow guide for discharge loss reduction
DE10242139A1 (de) * 2002-09-03 2004-03-18 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
US6739853B1 (en) * 2002-12-05 2004-05-25 Carrier Corporation Compact control mechanism for axial motion control valves in helical screw compressors
US6792907B1 (en) * 2003-03-04 2004-09-21 Visteon Global Technologies, Inc. Helmholtz resonator
CN2608725Y (zh) * 2003-03-17 2004-03-31 中国船舶重工集团公司第七一一研究所 喷水冷却氢气螺杆压缩机
US6851277B1 (en) * 2003-08-27 2005-02-08 Carrier Corporation Economizer chamber for minimizing pressure pulsations
US6976833B2 (en) * 2003-11-17 2005-12-20 Carrier Corporation Compressor discharge chamber with baffle plate
DE10359032A1 (de) * 2003-12-15 2005-07-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
US7156624B2 (en) * 2004-12-09 2007-01-02 Carrier Corporation Compressor sound suppression
US20060165543A1 (en) * 2005-01-24 2006-07-27 York International Corporation Screw compressor acoustic resonance reduction
WO2006085865A2 (en) * 2005-02-07 2006-08-17 Carrier Corporation Screw compressor lubrication
US8082747B2 (en) * 2008-12-09 2011-12-27 Thermo King Corporation Temperature control through pulse width modulation

Also Published As

Publication number Publication date
EP2198125A4 (en) 2013-07-24
CN101809251B (zh) 2013-07-17
ES2629981T3 (es) 2017-08-17
EP2198125A1 (en) 2010-06-23
US20100209280A1 (en) 2010-08-19
CN101809251A (zh) 2010-08-18
WO2009045187A1 (en) 2009-04-09

Similar Documents

Publication Publication Date Title
EP2198125B1 (en) Screw compressor pulsation damper
US8459963B2 (en) Screw compressor pulsation damper
US9151292B2 (en) Screw compressor with a shunt pulsation trap
KR100194171B1 (ko) 스크롤 압축기
US5584674A (en) Noise attenuator of compressor
EP1805418B1 (en) Compressor sound suppression
US7568898B2 (en) Compressor sound suppression
JP4946340B2 (ja) 両頭ピストン式圧縮機
US20060165543A1 (en) Screw compressor acoustic resonance reduction
JP2008523308A (ja) 圧縮機の静音化
KR20190025250A (ko) 스크롤 압축기
US8162622B2 (en) Compressor sound suppression
AU2005312690A1 (en) Compressor
US11698072B2 (en) Compressor
EP3450763B1 (en) Screw compressor
KR100814019B1 (ko) 다기통 회전압축기
US20240018961A1 (en) Compressor
CN111417783B (zh) 双旋转式压缩机和制冷循环装置
KR100332782B1 (ko) 로터리 압축기의 소음 저감 구조
KR100304556B1 (ko) 밀폐형회전식압축기의소음저감구조
KR100273428B1 (ko) 밀폐형 회전식 압축기의 토출소음 저감구조
CN116085255A (zh) 螺杆压缩机
JPS6226398A (ja) 横形ロ−タリ式圧縮機
JP2001349292A (ja) 気体圧縮機
JPS62214291A (ja) 横形ロ−タリ式圧縮機

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20100329

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20130626

RIC1 Information provided on ipc code assigned before grant

Ipc: F01C 1/16 20060101AFI20130620BHEP

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: 20170109

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK 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: 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: AT

Ref legal event code: REF

Ref document number: 903129

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170715

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602007051434

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2629981

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20170817

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

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

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: 20170621

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: 20170922

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: 20170621

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 903129

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170621

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

Ref country code: SE

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

Effective date: 20170621

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: 20170921

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: 20170621

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

Ref country code: AT

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

Effective date: 20170621

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: 20170621

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: 20170621

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: 20170621

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: 20170621

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

Ref country code: IT

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

Effective date: 20170621

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: 20170621

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: 20171021

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 602007051434

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: BITZER KUEHLMASCHINENBAU GMBH

Effective date: 20180319

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

Ref country code: DK

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

Effective date: 20170621

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: 20170621

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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: 20171001

Ref country code: LI

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

Effective date: 20171031

Ref country code: CH

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

Effective date: 20171031

PLAF Information modified related to communication of a notice of opposition and request to file observations + time limit

Free format text: ORIGINAL CODE: EPIDOSCOBS2

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20171031

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: 20170621

Ref country code: BE

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

Effective date: 20171031

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

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

Ref country code: MT

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

Effective date: 20171001

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

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: 20171001

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

Ref country code: TR

Payment date: 20181113

Year of fee payment: 15

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

Ref country code: HU

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

Effective date: 20071001

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

R26 Opposition filed (corrected)

Opponent name: BITZER KUEHLMASCHINENBAU GMBH

Effective date: 20180319

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

Ref country code: CY

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

Effective date: 20170621

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

Ref country code: FR

Payment date: 20190919

Year of fee payment: 13

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

Ref country code: GB

Payment date: 20190923

Year of fee payment: 13

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

Ref country code: DE

Payment date: 20190918

Year of fee payment: 13

APBM Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

APBU Appeal procedure closed

Free format text: ORIGINAL CODE: EPIDOSNNOA9O

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

Ref country code: ES

Payment date: 20191104

Year of fee payment: 13

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

Ref country code: PT

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

Effective date: 20170621

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20191101

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

Ref country code: NL

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

Effective date: 20191101

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

REG Reference to a national code

Ref country code: DE

Ref legal event code: R064

Ref document number: 602007051434

Country of ref document: DE

Ref country code: DE

Ref legal event code: R103

Ref document number: 602007051434

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602007051434

Country of ref document: DE

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

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

Free format text: STATUS: PATENT REVOKED

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

Effective date: 20201001

REG Reference to a national code

Ref country code: FI

Ref legal event code: MGE

27W Patent revoked

Effective date: 20210314

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

Ref country code: FR

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

Effective date: 20201031

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

Ref country code: GB

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

Effective date: 20201001

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

Ref country code: TR

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

Effective date: 20191001

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: 20201002

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: 20201002