WO2011071284A2 - Compresseur linéaire - Google Patents

Compresseur linéaire Download PDF

Info

Publication number
WO2011071284A2
WO2011071284A2 PCT/KR2010/008672 KR2010008672W WO2011071284A2 WO 2011071284 A2 WO2011071284 A2 WO 2011071284A2 KR 2010008672 W KR2010008672 W KR 2010008672W WO 2011071284 A2 WO2011071284 A2 WO 2011071284A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
cylinder
loop pipe
sealed container
refrigerant
Prior art date
Application number
PCT/KR2010/008672
Other languages
English (en)
Korean (ko)
Other versions
WO2011071284A3 (fr
Inventor
이효재
Original Assignee
엘지전자 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to US13/259,382 priority Critical patent/US20120034114A1/en
Priority to EP10836180.9A priority patent/EP2511527A4/fr
Priority to CN201080014322.1A priority patent/CN102439311B/zh
Publication of WO2011071284A2 publication Critical patent/WO2011071284A2/fr
Publication of WO2011071284A3 publication Critical patent/WO2011071284A3/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting

Definitions

  • the present invention relates to a linear compressor capable of reducing vibration through phase inversion between vibration factors.
  • a compressor is a mechanical device that increases pressure by receiving power from a power generator such as an electric motor or a turbine to compress air, refrigerant, or various other working gases. It is widely used throughout.
  • compressors are classified into a reciprocating compressor which compresses the refrigerant while linearly reciprocating the inside of the cylinder by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder.
  • a rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder to form a compression space in which the working gas is sucked and discharged between the eccentrically rotating roller and the cylinder.
  • a scroll compressor that compresses the refrigerant while the rotating scroll rotates along the fixed scroll to form a compression space in which the working gas is absorbed and discharged between the orbiting scroll and the fixed scroll. Divided.
  • the piston is directly connected to the reciprocating linear motion drive motor, so that there is no mechanical loss due to the motion conversion to improve the compression efficiency as well as a simple linear compressor has been developed a lot.
  • 1 is a configuration diagram showing a vibration factor of a general linear compressor.
  • the linear compressor includes a sealed container 10 that is a sealed space as shown in FIG. 1, and a main body 20 including a cylinder, a piston, and a linear motor that compresses a refrigerant in the sealed container 10.
  • the main body 20 is elastically supported by a loop pipe (L) for forming a plurality of support springs (S) and the discharge passage of the refrigerant in the sealed container 10, the sealed container 10 is provided on the bottom surface
  • the mount 11 is fixed to the mounting surface so as to be elastically supported.
  • the linear compressor since the permanent magnet of the linear motor for driving the piston is driven like the piston, not only the mass of the mechanism reciprocating linearly moves but also the vibration increases.
  • the linear compressor since the linear compressor is operated in a resonant state to increase the compression efficiency, reducing the mass of the mechanism part to reduce vibration is unsuitable because it can lower the overall efficiency of the compressor. Therefore, the linear compressor needs to optimize vibration transmission characteristics between the sealed container 10 and the main body 20 in order to reduce vibration.
  • the factors affecting the vibration transmission characteristics can be seen as the mount 11, the support spring (S), the loop pipe (L), the rigidity of the mount 11, the rigidity and height of the support spring (S) is
  • the roof pipe L since the roof pipe L has a predetermined stiffness and mass, the roof pipe L may have a large influence on the overall efficiency in terms of the design of the linear compressor using resonance.
  • FIG. 2 is a graph showing the vibration displacement of the loop pipe applied to the linear compressor according to the prior art.
  • the natural frequency of the loop pipe is designed in the 70 ⁇ 90 Hz band higher than the rated operating frequency.
  • the linear motor increases the operating frequency from 0 Hz to 60 Hz like the conventional reciprocating compressor. That is, if the natural frequency of the loop pipe is lower than the operating frequency of the linear compressor, the resonance occurs at the point where the linear compressor operating frequency coincides with the natural frequency of the loop pipe in the section where the operating frequency of the linear compressor rises to the rated operating frequency at the start. It is preferable that the natural frequency of the loop pipe is designed to be higher than the rated operating frequency of the linear compressor since this can cause the loop pipe to break.
  • the main body is elastically supported by the support spring and the loop pipe in the sealed container, and the operating frequency of the roof pipe is designed to be higher than the rated operating frequency. Since the excitation force of the loop pipe increases in the same direction as the excitation force of the support spring, the vibration transmitted to the entire compressor at the start is amplified by the addition of the excitation force of the support spring and the excitation force of the loop pipe.
  • the present invention has been made to solve the above problems of the prior art, an object of the present invention to provide a linear compressor that can reduce the vibration through the phase inversion.
  • the linear compressor according to the present invention for solving the above problems is a sealed container which is a closed space provided with a suction pipe and a discharge pipe that the refrigerant is sucked / discharged; A cylinder having a compression space installed inside the sealed container; A piston reciprocating linearly in the cylinder and compressing the refrigerant in the compression space; A linear motor which provides a driving force to the piston and operates at a set driving frequency; A plurality of support springs elastically supporting an assembly including a cylinder, a piston, and a linear motor on the bottom surface of the hermetic container; And a loop pipe provided to guide the refrigerant compressed in the compression space to the discharge pipe, wherein the closed container excitation force of the loop pipe has a phase opposite to that of the support container.
  • the natural frequency of the loop pipe is set to less than the rated operating frequency of the linear motor.
  • the rated operating frequency of the linear motor is 60Hz
  • the natural frequency of the loop pipe is characterized in that it is set to 50Hz or less.
  • the linear compressor according to the present invention includes a sealed container which is a sealed space in which refrigerant is sucked and discharged, a cylinder having a compressed space installed inside the sealed container, a reciprocating linear motion in the cylinder, and a piston for compressing the refrigerant in the compressed space, the piston.
  • a support spring that provides a driving force and elastically supports an assembly including a linear motor, a cylinder, a piston, and a linear motor to operate at a set driving frequency on a bottom surface of the sealed container; And a loop pipe provided to guide the refrigerant compressed in the compression space to the discharge pipe, wherein the rated driving frequency of the linear motor is larger than the natural frequency of the loop pipe.
  • the rated operating frequency of the linear motor is characterized in that it is determined in proportion to the natural frequency of the loop pipe.
  • the main body is elastically supported by a support spring and a loop pipe in a sealed container, the natural frequency of the loop pipe is set lower than the rated operating frequency, and an inverter motor is applied at startup. Since it operates directly at the rated operating frequency, the vibration of the loop pipe at the rated operating frequency behaves in the opposite direction to that of the support spring, thereby reducing the vibration transmitted to the entire compressor.
  • 1 is a configuration diagram showing a vibration factor of a general linear compressor.
  • Figure 2 is a graph showing the vibration displacement of the loop pipe applied to the linear compressor according to the prior art.
  • Figure 3 is a side cross-sectional view showing an example of a linear compressor according to the present invention.
  • Figure 4 is a graph showing the vibration displacement of the loop pipe applied to the linear compressor according to the present invention.
  • Figure 5 is a graph showing the vibration size of the sealed container according to the change in the natural frequency of the loop pipe in the linear compressor of the present invention.
  • FIG 3 is a side sectional view showing an example of a linear compressor according to the present invention.
  • An example of the linear compressor according to the present invention is a cylinder 200, a piston 300, an inner stator 420 and an outer stator 440 and a permanent magnet in a sealed container 110 which is a sealed space as shown in FIG.
  • a linear motor 400 including a 460 when the permanent magnet 460 linearly reciprocates by mutual electromagnetic force between the inner stator 420 and the outer stator 440, connected to the permanent magnet 460
  • the piston 300 is linear reciprocating motion with the permanent magnet 460.
  • the inner stator 420 is fixed to the outer circumference of the cylinder 200
  • the outer stator 440 is fixed by the frame 520 and the motor cover 540 in the axial direction
  • the frame 520 and the motor cover 540 Is coupled to each other by a fastening member such as a bolt
  • the outer stator 440 is fixed between the frame 520 and the motor cover 540.
  • the frame 520 may be integrally formed with the cylinder 200 or may be manufactured separately from the cylinder 200 and combined with the cylinder 200. 3 illustrates an example in which the frame 520 and the cylinder 200 are integrally formed.
  • the supporter 320 is connected to the rear of the piston 300.
  • Four front main springs 800 are supported at both ends by the supporter 320 and the motor cover 540.
  • the four rear main springs 800 are supported at both ends by the supporter 320 and the back cover 560, and the back cover 560 is coupled to the rear of the motor cover 540.
  • a suction muffler 700 is also provided at the rear of the piston 300, and refrigerant flows into the piston 300 through the suction muffler 700, thereby reducing noise during refrigerant suction.
  • the inside of the piston 300 is hollow to allow the refrigerant introduced through the suction muffler 700 to enter and compress the compression space P formed between the cylinder 200 and the piston 300.
  • a suction valve 610 is installed at the front end of the piston 300, and the suction valve 610 is opened so that the refrigerant flows into the compression space P from the piston 300, and again the piston () in the compression space P.
  • the tip of the piston 300 is closed so as not to flow into the 300.
  • the discharge valve 620 located at the tip of the cylinder 200 is opened.
  • the discharge valve 620 is installed to be elastically supported by the spiral discharge valve spring 630 inside the support cap 640 fixed to one end of the cylinder 200.
  • the compressed high-pressure refrigerant is discharged into the discharge cap 660 through a hole formed in the support cap 640, and then discharged to the outside of the linear compressor 100 through the loop pipe L to circulate a refrigeration cycle.
  • Each of the components of the linear compressor 100 described above is supported by the front support spring 120 and the rear support spring 140 in the assembled state, and is spaced apart from the bottom of the sealed container 110. Since it is not in direct contact with the bottom of the sealed container 110, the vibration generated in each component of the compressor 100 while compressing the refrigerant is not directly transmitted to the sealed container (110). Therefore, the noise generated by the vibration transmitted to the outside of the shell 100 and the vibration of the sealed container 110 can be reduced.
  • Such a linear compressor needs to optimize the transmission characteristics in order to reduce vibration as described in the prior art, and it is necessary to limit the design of the loop pipe L, which is a factor that may affect the compression efficiency.
  • the main body including the cylinder 200, the piston 300 and the linear motor 400 is elastically supported by the support springs 120 and 140 and the loop pipe L inside the sealed container 110, the sealed container 110. Vibration transmitted to) can be seen as the sum of the excitation force of the support spring (120,140) and the excitation force of the loop pipe (L).
  • the excitation force of the loop pipe (L) is designed to have a phase in the opposite direction to the excitation force of the support springs (120, 140) to reduce the vibration transmitted to the entire compressor.
  • FIG. 4 is a graph showing the vibration displacement of the loop pipe applied to the linear compressor according to the present invention.
  • the linear compressor of the present invention is designed such that the natural frequency f lp of the loop pipe is lower than the rated operating frequency f in order to reduce vibration through phase inversion as shown in FIG. 4.
  • the loop pipe vibrates in the (+) direction at a frequency lower than the natural frequency (f lp ) of the loop pipe, but at a frequency higher than the natural frequency (f lp ) of the loop pipe, the loop pipe is (- Vibrate in the Therefore, when the rated operating frequency f is higher than the natural frequency f lp of the loop pipe, the vibration of the loop pipe is reversed in phase, and the excitation force of the roof pipe acts in the opposite direction to the excitation force of the support spring. The vibration transmitted is reduced.
  • the linear motor is operated at the rated operating frequency f immediately upon starting. At this time, if the linear motor is swept from 0 to the rated operating frequency f when starting, the resonance phenomenon coincides with the natural frequency f lp of the loop pipe before the operating frequency reaches the rated operating frequency f. Therefore, it is preferable that an inverter motor which is operated at the rated operating frequency f immediately after starting the linear motor is applied because the loop pipe is broken.
  • the rated operating frequency f is designed to be 60 Hz and is operated at the rated operating frequency f immediately upon startup, and the natural frequency f lp of the roof pipe is designed to be 50 Hz or less lower than the rated operating frequency f. Can be.
  • FIG. 5 is a graph showing the vibration size of the sealed container according to the change in the natural frequency of the loop pipe in the linear compressor of the present invention.
  • the vibration transmitted to the entire sealed container is increased, and the natural frequency f lp of the loop pipe is increased.
  • the vibration of the hermetic container increases to 13 to 57 Gal, but the vibration change of the hermetic container according to the change of the natural frequency ( ⁇ f lp ) of the roof pipe. Since ⁇ f is small, the vibration transmitted to the compressor can be regarded as a stable section.
  • the vibration of the hermetic container increases to 57 ⁇ 1120Gal, and the vibration change of the hermetic container ( ⁇ f lp ) according to the natural frequency change ( ⁇ f lp ) of the roof pipe.
  • the vibration change ( ⁇ f) of the hermetically sealed container according to the natural frequency change ( ⁇ f lp ) of the roof pipe is Since it appears smaller than the vibration amplification section, even if the vibration value transmitted to the actual sealed container decreases, it appears larger than the vibration stabilization section.
  • the natural frequency f lp of the loop pipe is designed in the frequency range of 50HZ or less in the compressor whose rated operating frequency f is 60Hz.
  • the rated operation frequency (f) to loop Considering that the natural frequency (f lp) of the pipe making, the rated operating frequency (f) is (f lp) the natural frequency of the loop pipe in the compressor 50Hz proportion to as the Is preferably designed in the frequency range below 41.6Hz.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention porte sur un compresseur linéaire comprenant: un récipient étanche qui forme un espace étanche et qui comprend un tube d'aspiration et un tube de refoulement à travers lesquels un fluide frigorigène est aspiré et refoulé ; un vérin monté dans le récipient étanche et formant un espace de compression ; un piston à mouvement alternatif linéaire dans le vérin de manière à comprimer le fluide frigorigène dans l'espace de compression ; un moteur linéaire travaillant à une fréquence de fonctionnement prédéfinie pour appliquer une force motrice au piston ; une pluralité de ressorts de support configurés de manière à supporter un ensemble comprenant le vérin, le piston et le moteur linéaire par rapport à une surface inférieure du récipient étanche ; et un tube recourbé en boucle à travers lequel le fluide frigorigène comprimé dans l'espace de compression est guidé vers le tube de refoulement. Étant donné que la phase d'une force sortante appliquée au récipient étanche à partir du tube recourbé en boucle est en opposition par rapport à la phase des forces sortant de la coque des ressorts de support, les vibrations d'un corps principal et du tube recourbé en boucle s'annulent mutuellement et, de cette façon, les vibrations globales peuvent être réduites.
PCT/KR2010/008672 2009-12-08 2010-12-06 Compresseur linéaire WO2011071284A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/259,382 US20120034114A1 (en) 2009-12-08 2010-12-06 Linear compressor
EP10836180.9A EP2511527A4 (fr) 2009-12-08 2010-12-06 Compresseur linéaire
CN201080014322.1A CN102439311B (zh) 2009-12-08 2010-12-06 线性压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2009-0121292 2009-12-08
KR1020090121292A KR101681322B1 (ko) 2009-12-08 2009-12-08 리니어 압축기

Publications (2)

Publication Number Publication Date
WO2011071284A2 true WO2011071284A2 (fr) 2011-06-16
WO2011071284A3 WO2011071284A3 (fr) 2011-11-10

Family

ID=44146030

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2010/008672 WO2011071284A2 (fr) 2009-12-08 2010-12-06 Compresseur linéaire

Country Status (5)

Country Link
US (1) US20120034114A1 (fr)
EP (1) EP2511527A4 (fr)
KR (1) KR101681322B1 (fr)
CN (1) CN102439311B (fr)
WO (1) WO2011071284A2 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9506460B2 (en) * 2014-02-10 2016-11-29 Haier Us Appliance Solutions, Inc. Linear compressor
US9429150B2 (en) * 2014-02-10 2016-08-30 Haier US Appliances Solutions, Inc. Linear compressor
US9841012B2 (en) * 2014-02-10 2017-12-12 Haier Us Appliance Solutions, Inc. Linear compressor
US9322401B2 (en) * 2014-02-10 2016-04-26 General Electric Company Linear compressor
US9518572B2 (en) * 2014-02-10 2016-12-13 Haier Us Appliance Solutions, Inc. Linear compressor
US10240603B2 (en) 2014-05-22 2019-03-26 Trane International Inc. Compressor having external shell with vibration isolation and pressure balance
US10088208B2 (en) * 2016-01-06 2018-10-02 Johnson Controls Technology Company Vapor compression system
KR102060175B1 (ko) * 2018-06-29 2019-12-27 엘지전자 주식회사 리니어 압축기

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3497135A (en) * 1968-04-23 1970-02-24 Copeland Refrigeration Corp Noise control for hermetic motor compressors
JPH11107931A (ja) * 1997-10-02 1999-04-20 Matsushita Refrig Co Ltd 密閉型能力制御圧縮機
KR100299217B1 (ko) * 1997-12-31 2002-02-19 구자홍 밀폐형압축기의압력파이프진동저감장치
KR100564439B1 (ko) * 2003-11-14 2006-03-29 엘지전자 주식회사 밀폐형압축기
KR100529933B1 (ko) * 2004-01-06 2005-11-22 엘지전자 주식회사 리니어 압축기
KR20050080657A (ko) * 2004-02-10 2005-08-17 엘지전자 주식회사 왕복동식 압축기의 진동저감구조
KR100527176B1 (ko) * 2004-03-09 2005-11-09 삼성광주전자 주식회사 리니어 압축기
JP4851457B2 (ja) * 2004-08-30 2012-01-11 エルジー エレクトロニクス インコーポレイティド リニア圧縮機の制御装置及び制御方法
KR100576032B1 (ko) * 2004-10-01 2006-05-02 엘지전자 주식회사 리니어 압축기의 제어장치 및 제어방법
KR100624818B1 (ko) * 2004-11-02 2006-09-18 엘지전자 주식회사 리니어 압축기
KR101507605B1 (ko) * 2007-10-24 2015-04-01 엘지전자 주식회사 리니어 압축기

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None
See also references of EP2511527A4

Also Published As

Publication number Publication date
EP2511527A2 (fr) 2012-10-17
US20120034114A1 (en) 2012-02-09
KR101681322B1 (ko) 2016-11-30
CN102439311A (zh) 2012-05-02
EP2511527A4 (fr) 2013-06-12
KR20110064610A (ko) 2011-06-15
CN102439311B (zh) 2015-10-14
WO2011071284A3 (fr) 2011-11-10

Similar Documents

Publication Publication Date Title
WO2011071284A2 (fr) Compresseur linéaire
KR100810845B1 (ko) 리니어 압축기
KR100396780B1 (ko) 스크롤 압축기
KR101273710B1 (ko) 리니어 압축기
KR20020069302A (ko) 왕복동식 압축기
JP2005226651A (ja) 往復動式圧縮機の振動低減構造
WO2009123400A2 (fr) Compresseur à volute
KR20170074527A (ko) 리니어 압축기
US20080080993A1 (en) Hermetic compressor
US8388320B2 (en) Mount for compressor shell
US20050034926A1 (en) Lubricating oil supply apparatus of reciprocating compressor
KR100404109B1 (ko) 리니어 압축기
CN102985693A (zh) 往复式压缩机
KR20120076164A (ko) 밀폐형 압축기
KR20030059614A (ko) 왕복동식 압축기의 가변형 흡입 머플러
US11905940B2 (en) Linear compressor
KR101870180B1 (ko) 2단 로터리 압축기
KR20100112479A (ko) 리니어 압축기
KR20090041706A (ko) 리니어 압축기
KR100597295B1 (ko) 리니어 압축기
KR100527580B1 (ko) 왕복동식 압축기의 완충장치
JP4810885B2 (ja) 密閉型圧縮機
KR20080065093A (ko) 리니어 압축기
KR20090041710A (ko) 리니어 압축기
KR20030039772A (ko) 공진을 이용한 왕복동식 압축기

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080014322.1

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10836180

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2010836180

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2010836180

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 13259382

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE