EP2300716A1 - A compressor - Google Patents

A compressor

Info

Publication number
EP2300716A1
EP2300716A1 EP09737978A EP09737978A EP2300716A1 EP 2300716 A1 EP2300716 A1 EP 2300716A1 EP 09737978 A EP09737978 A EP 09737978A EP 09737978 A EP09737978 A EP 09737978A EP 2300716 A1 EP2300716 A1 EP 2300716A1
Authority
EP
European Patent Office
Prior art keywords
muffler
pipe
casing
inlet pipe
compressor
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
Application number
EP09737978A
Other languages
German (de)
French (fr)
Other versions
EP2300716B1 (en
Inventor
Sarper Marasli
Bora Abdik
Umit Unlu
Atilla Kaya
Umit Fidan
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.)
Arcelik AS
Original Assignee
Arcelik AS
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 Arcelik AS filed Critical Arcelik AS
Priority to SI200931300T priority Critical patent/SI2300716T1/en
Publication of EP2300716A1 publication Critical patent/EP2300716A1/en
Application granted granted Critical
Publication of EP2300716B1 publication Critical patent/EP2300716B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • 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
    • 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
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections

Definitions

  • the present invention relates to a compressor wherein the performance is improved.
  • a suction muffler made of plastic material is used for attenuating the noise resulting from the refrigerant fluid and the refrigerant fluid with decreased temperature and pressure received from the evaporator is delivered to the suction muffler.
  • the refrigerant fluid aspirated by the suction muffler disposed inside the compressor casing is conveyed to the cylinder volume and is compressed here by the piston to partake in the refrigeration cycle.
  • semi-direct suction method is used in compressors for the aim of cooling the refrigerant received into the cylinder volume.
  • the suction muffler inlet and the inlet pipe leak-proofingly entering the casing are opposite to but not connected to each other. Since the suction muffler inlet is not directly connected to the inlet pipe, the refrigerant fluid sucked into the casing enters into the suction muffler with increased temperature due to the heat in the casing. Since the temperature of the refrigerant fluid increases, the volumetric efficiency of the compressor hence the coefficient of performance (COP) decreases.
  • COP coefficient of performance
  • refrigerant fluid is received into the suction muffler after entering the casing, it is affected by the heat in the casing and the previously above mentioned problem arises.
  • connection pipe is described that is disposed between the muffler inlet and the intake pipe, for delivering the refrigerant fluid to the suction muffler.
  • the aim of the present invention is the realization of a compressor wherein the performance is improved.
  • the compressor realized in order to attain the aim of the present invention, explicated in the first claim and the respective claims thereof, comprises a muffler pipe that by passing through an opening on the casing opens into the inlet pipe, whereof the end is connected to the opening, such that a clearance is left there between.
  • the muffler pipe is disposed inside the inlet pipe without being in contact PatXML 3/6 BB1546-7.724
  • the muffler pipe is configured frusto-conically.
  • the top angle is preferably 30 degrees maximum.
  • the muffler pipe gets wider from the casing towards the suction muffler. By means of this configuration, the compressor noise power level is diminished.
  • the inlet of the suction muffler extends outside the casing by the muffler pipe and is inserted into the inlet pipe. Accordingly, the greater portion of the refrigerant fluid entering into the suction muffler is prevented from being received through the casing. Consequently, compressor efficiency is increased by maintaining the temperature of the refrigerant fluid entering the suction muffler to be lower.
  • a lesser amount of lubricant is received into the suction muffler than the current semi-direct suction compressors. Besides, since the muffler pipe and the inlet pipe are not in contact with each other, vibrations and noise generated by the vibrations are also prevented.
  • Figure 1 - is the schematic view of the compressor of the present invention.
  • the compressor (1) comprises a casing (2), a suction muffler (5) disposed inside the casing (2) that attenuates the noise resulting from the refrigerant fluid, an inlet pipe (4) that carries the refrigerant fluid delivered from the PatXML 4/6 BB1546-7.724
  • the compressor (1) furthermore comprises a muffler pipe (6), with one end opening into the suction muffler (5), the other end extending outwards of the casing (2) by passing through the opening (3) and opening into the inlet pipe (4) so as to have a clearance there between.
  • the muffler pipe (6) is extended up to inside of the inlet pipe (4) from outside the casing (2) and almost all of the refrigerant fluid sucked by the compressor (1) is directly received into the suction muffler (5) without entering into the casing (2).
  • the inlet of the suction muffler (5) is extended up to the inside of the inlet pipe (4).
  • the muffler pipe (6) is configured to be preferably frusto-conical, getting narrower from the suction muffler (5) towards the inlet pipe (4).
  • apex (X) of the muffler pipe (6) is 30 degrees maximum.
  • the end of the muffler pipe (6) inserted into the inlet pipe (4) is narrower than the end thereof opening into the suction muffler (5).
  • the muffler pipe (6) and the inlet pipe (4) are disposed one inside the other coaxially.
  • the refrigerant fluid flowing in the inlet pipe (4) can be directly received into the suction muffler (5) by passing through the muffler pipe (6) without confronting with any obstruction.
  • the portion of the inlet pipe (4) wherein the muffler pipe (6) is inserted is configured frusto-conically with a maximum apex (Y) of 30 degrees.
  • the compressor (1) efficiency is increased by the refrigerant fluid received into the suction muffler (5) from the refrigeration cycle being cooler than the refrigerant fluid received inside the casing (2). Besides, the amount of lubricant delivered into the suction muffler (5) from the refrigeration cycle is decreased. On the other hand, the vibrations in the refrigeration cycle and noise due to vibrations are also reduced.

Abstract

The present invention relates to a compressor (1 ) comprising a casing (2) that guards the operating components within, a suction muffler (5) disposed inside the casing (2) that attenuates the noise resulting from the refrigerant fluid, an inlet pipe (4) that carries the refrigerant fluid delivered from the evaporator in the refrigeration cycle, an opening (3) arranged at the place where the inlet pipe (4) is mounted to the casing (2), providing the entrance of the refrigerant fluid flowing through the inlet pipe (4) into the casing (2).

Description

PatXML 1/6 BB1546-7.724
Description
A COMPRESSOR
[0001] The present invention relates to a compressor wherein the performance is improved.
[0002] In hermetic compressors utilized preferably in the cooling devices, a suction muffler made of plastic material is used for attenuating the noise resulting from the refrigerant fluid and the refrigerant fluid with decreased temperature and pressure received from the evaporator is delivered to the suction muffler. The refrigerant fluid aspirated by the suction muffler disposed inside the compressor casing is conveyed to the cylinder volume and is compressed here by the piston to partake in the refrigeration cycle. In the state of the art, semi-direct suction method is used in compressors for the aim of cooling the refrigerant received into the cylinder volume. In this method, the suction muffler inlet and the inlet pipe leak-proofingly entering the casing are opposite to but not connected to each other. Since the suction muffler inlet is not directly connected to the inlet pipe, the refrigerant fluid sucked into the casing enters into the suction muffler with increased temperature due to the heat in the casing. Since the temperature of the refrigerant fluid increases, the volumetric efficiency of the compressor hence the coefficient of performance (COP) decreases.
[0003] In state of the art United States of America Patent No US5496156, a funneled or countersunk inlet port on the muffler permits a large portion of the refrigerant leaving the inlet pipe to be received into the suction muffler.
[0004] In state of the art United States of America Patent No US5288212, the suction muffler inlet and the entrance pipe are connected by a buffer spring member.
[0005] In state of the art United States of America Patent No US5803717, the suction muffler inlet and the entrance pipe are connected with a spring member and a connector.
[0006] In state of the art United States of America Patent No US5888055 entrance pipe fitted into the suction muffler inlet inside the casing so that a space is formed there between.
[0007] In all the state of the art patent documents explained above, since the PatXML 2/6 BB1546-7.724
refrigerant fluid is received into the suction muffler after entering the casing, it is affected by the heat in the casing and the previously above mentioned problem arises.
[0008] Another method used in the state of the art for cooling the fluid received into the cylinder volume is the direct suction method. In these implementations, bellows like structures are used between the suction muffler inlet and the inlet pipe.
[0009] In state of the art United States of America Patent No US5451727, the suction muffler inlet and a pipe connecting the inlet pipe are joined in a chamber disposed above the casing.
[0010] In the United States of America Patent No US4793773, a bellows-like connector duct is described that connects the intake duct and the suction muffler inlet.
[0011] In the International Patent Application No WO2006/09239, a connection pipe is described that is disposed between the muffler inlet and the intake pipe, for delivering the refrigerant fluid to the suction muffler.
[0012] In these embodiments, the compressor noise power level increases since all the vibrations in the refrigeration system are transferred to the casing.
[0013] The aim of the present invention is the realization of a compressor wherein the performance is improved.
[0014] The compressor realized in order to attain the aim of the present invention, explicated in the first claim and the respective claims thereof, comprises a muffler pipe that by passing through an opening on the casing opens into the inlet pipe, whereof the end is connected to the opening, such that a clearance is left there between.
[0015] Gas is received into the muffler from outside the casing since the muffler pipe passes from the opening and goes out of the casing to enter into the inlet pipe. Accordingly, compressor efficiency is increased by lowering the temperature of the refrigerant fluid. Besides, the amount of lubricant entering into the muffler from the refrigeration cycle is reduced by receiving a greater portion of the refrigerant fluid from the refrigeration cycle into the suction muffler without entering the casing.
[0016] The muffler pipe is disposed inside the inlet pipe without being in contact PatXML 3/6 BB1546-7.724
with the walls of the inlet pipe. Thus, since the vibrations in the refrigeration cycle cannot be transferred to the muffler thereby vibrations and noise due to vibrations are prevented.
[0017] In another embodiment of the present invention, the muffler pipe is configured frusto-conically. The top angle is preferably 30 degrees maximum. In this embodiment, the muffler pipe gets wider from the casing towards the suction muffler. By means of this configuration, the compressor noise power level is diminished.
[0018] By means of the present invention, the inlet of the suction muffler extends outside the casing by the muffler pipe and is inserted into the inlet pipe. Accordingly, the greater portion of the refrigerant fluid entering into the suction muffler is prevented from being received through the casing. Consequently, compressor efficiency is increased by maintaining the temperature of the refrigerant fluid entering the suction muffler to be lower. By means of this embodiment, a lesser amount of lubricant is received into the suction muffler than the current semi-direct suction compressors. Besides, since the muffler pipe and the inlet pipe are not in contact with each other, vibrations and noise generated by the vibrations are also prevented.
[0019] A compressor realized in order to attain the aim of the present invention is illustrated in the attached figures, where:
[0020] Figure 1 - is the schematic view of the compressor of the present invention.
[0021] The elements illustrated in the figures are numbered as follows:
1. Compressor
2. Casing
3. Opening
4. Inlet pipe
5. Suction muffler
6. Muffler pipe
[0022] The compressor (1) comprises a casing (2), a suction muffler (5) disposed inside the casing (2) that attenuates the noise resulting from the refrigerant fluid, an inlet pipe (4) that carries the refrigerant fluid delivered from the PatXML 4/6 BB1546-7.724
evaporator in the refrigeration cycle, an opening (3) arranged at the place where the inlet pipe (4) is mounted to the casing (2), providing the entrance of the refrigerant fluid into the casing (2).
[0023] The compressor (1) furthermore comprises a muffler pipe (6), with one end opening into the suction muffler (5), the other end extending outwards of the casing (2) by passing through the opening (3) and opening into the inlet pipe (4) so as to have a clearance there between. The muffler pipe (6) is extended up to inside of the inlet pipe (4) from outside the casing (2) and almost all of the refrigerant fluid sucked by the compressor (1) is directly received into the suction muffler (5) without entering into the casing (2). By means of the muffler pipe (6), the inlet of the suction muffler (5) is extended up to the inside of the inlet pipe (4). This maintains to reduce the amount of the refrigerant fluid received into the suction muffler (5) from inside the casing (2). Besides, the refrigerant fluid is maintained to be as cool as possible until reaching the cylinder volume during suction of the refrigerant fluid and this increases compressor (1) efficiency (Figure 1). The diameter of the muffler pipe (6) part opening into the inlet pipe (4) is smaller than the diameter of the inlet pipe (4) and the opening (3).
[0024] The refrigerant fluid in the refrigeration cycle sucked by the compressor (1) is delivered to the cylinder volume by passing through the suction muffler (5) and is compressed to be delivered to the refrigeration cycle from there. Since the muffler pipe (6) opens into the inlet pipe (4) outside the casing (2), the refrigerant fluid sucked by the compressor (1) can be received into the suction muffler (5) without mixing with the relatively hotter refrigerant fluid inside the casing (2). Besides, with this embodiment, the amount of lubricant entering into the suction muffler (5) from the refrigeration cycle is lower.
[0025] An all around gap is provided between the inlet pipe (4) and the portion of the muffler pipe (6) entering into the inlet pipe (4). In other words, the muffler pipe (6) is inserted into the inlet pipe (4) without contacting thereto and without being directly connected to the inlet pipe (4). Thus, during the operation of the compressor (1), the muffler pipe (6), since not being in contact with the casing (2) and the inlet pipe (4), can move freely to and PatXML 5/6 BB1546-7.724
fro in the axial direction. Furthermore, since the muffler pipe (6) is inserted into the inlet pipe (4) with a clearance, a small amount of refrigerant fluid is allowed to pass into the casing (2). Accordingly, pressure inside the casing (2) is balanced and the start-up of the compressor (1) becomes easier.
[0026] In another embodiment of the present invention, the muffler pipe (6) is configured to be preferably frusto-conical, getting narrower from the suction muffler (5) towards the inlet pipe (4). In this embodiment of the present invention, apex (X) of the muffler pipe (6) is 30 degrees maximum. Thus, the end of the muffler pipe (6) inserted into the inlet pipe (4) is narrower than the end thereof opening into the suction muffler (5). This result in the noise power level of the refrigerant fluid sucked by the compressor (1) to be reduced while being received into the suction muffler (5). Accordingly, the effectiveness of the suction muffler (5) in lowering the noise power level of the compressor (1) is increased.
[0027] In another embodiment of the present invention, the muffler pipe (6) and the inlet pipe (4) are disposed one inside the other coaxially. Thus, the refrigerant fluid flowing in the inlet pipe (4) can be directly received into the suction muffler (5) by passing through the muffler pipe (6) without confronting with any obstruction.
[0028] In another embodiment of the present invention, the portion of the inlet pipe (4) wherein the muffler pipe (6) is inserted is configured frusto-conically with a maximum apex (Y) of 30 degrees.
[0029] By means of the present invention, the compressor (1) efficiency is increased by the refrigerant fluid received into the suction muffler (5) from the refrigeration cycle being cooler than the refrigerant fluid received inside the casing (2). Besides, the amount of lubricant delivered into the suction muffler (5) from the refrigeration cycle is decreased. On the other hand, the vibrations in the refrigeration cycle and noise due to vibrations are also reduced.

Claims

PatXML 6/6 BB1546-7.724Claims
1. A compressor (1) that comprises a casing (2), a suction muffler (5) disposed inside the casing (2) that attenuates the noise resulting from the refrigerant fluid, an inlet pipe (4) that carries the refrigerant fluid delivered from the evaporator in the refrigeration cycle, an opening (3) arranged at the place where the inlet pipe (4) is mounted to the casing (2), providing the entrance of the refrigerant fluid into the casing (2) and characterized by a muffler pipe (6), with one end opening into the suction muffler (5), the other end extending outwards of the casing (2) by passing through the opening (3) and opening into the inlet pipe (4) so as to have a gap there between.
2. A compressor (1) as in Claim 1 , characterized by a muffler pipe (6) with an all around gap provided between the inlet pipe (4) and the portion thereof entering into the inlet pipe (4).
3. A compressor (1) as in Claim 1 , characterized by a muffler pipe (6) having a cross section that gets narrower from the suction muffler (5) towards the inlet pipe (4).
4. A compressor (1) as in Claim 3, characterized by a muffler pipe (6) that is configured to be frusto-conic.
5. A compressor (1) as in Claim 4, characterized by a muffler pipe (6) having an apex (X) of maximum 30 degrees.
6. A compressor (1) as in any one of the above Claims, characterized by a muffler pipe (6) disposed coaxially with the inlet pipe (4).
7. A compressor (1) as in any one of the above Claims, characterized by an inlet pipe (4) with the portion wherein the muffler pipe (6) is inserted being configured frusto-conically with a maximum apex (Y) of 30 degrees.
EP09737978.8A 2008-05-01 2009-04-07 A compressor Active EP2300716B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI200931300T SI2300716T1 (en) 2008-05-01 2009-04-07 A compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TR200803043 2008-05-01
PCT/EP2009/054166 WO2009132934A1 (en) 2008-05-01 2009-04-07 A compressor

Publications (2)

Publication Number Publication Date
EP2300716A1 true EP2300716A1 (en) 2011-03-30
EP2300716B1 EP2300716B1 (en) 2015-08-05

Family

ID=40821909

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09737978.8A Active EP2300716B1 (en) 2008-05-01 2009-04-07 A compressor

Country Status (5)

Country Link
EP (1) EP2300716B1 (en)
CN (1) CN102016311B (en)
ES (1) ES2551319T3 (en)
SI (1) SI2300716T1 (en)
WO (1) WO2009132934A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR112014008004A2 (en) * 2011-10-03 2017-04-11 Arcelik As compressor comprising a protection element
BR102014029659B1 (en) * 2014-11-27 2022-01-11 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda ACOUSTIC SUCTION FILTER AND SUCTION LINE INCLUDING ACOUSTIC SUCTION FILTER
WO2016120446A1 (en) 2015-01-30 2016-08-04 Arcelik Anonim Sirketi A compressor
DE102015206684B4 (en) * 2015-04-14 2024-03-14 Hanon Systems Efp Deutschland Gmbh Pump device
CN104989620A (en) * 2015-06-09 2015-10-21 安庆卡尔特压缩机有限公司 Improved compressor
EP3336355B1 (en) * 2016-12-19 2022-05-11 Nidec Global Appliance Brasil Ltda. Hermetic compressor
US11231024B2 (en) * 2017-02-16 2022-01-25 Samsung Electronics Co., Ltd. Compressor comprising an upper shell and a lower shell wherein the upper shell comprises an upper protrusion comprising a first protrusion and a second protrusion comprising a transition and an approximately flat shape
BR102019022089A2 (en) * 2019-10-21 2021-05-04 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda. connection system applied to hermetic compressor

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Publication number Priority date Publication date Assignee Title
EP0411195B1 (en) * 1989-08-04 1994-12-07 Matsushita Refrigeration Company Hermetic compressor
IT230572Y1 (en) * 1992-12-21 1999-06-07 Gold Star Co NOISE SUPPRESSION DEVICE FOR A SEALED PLUNGER COMPRESSOR
DE4411191C2 (en) * 1994-03-30 1997-05-15 Danfoss Compressors Gmbh Refrigerant compressor arrangement
IN191465B (en) * 1995-11-02 2003-12-06 Lc Electronics Inc
KR200148573Y1 (en) * 1996-12-06 1999-06-15 구자홍 Suction noise reduction apparatus of a hermetic compressor
CN2895794Y (en) * 2005-08-30 2007-05-02 乐金电子(天津)电器有限公司 Air-suction silencer of compressor

Non-Patent Citations (1)

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Title
See references of WO2009132934A1 *

Also Published As

Publication number Publication date
CN102016311A (en) 2011-04-13
EP2300716B1 (en) 2015-08-05
ES2551319T3 (en) 2015-11-18
SI2300716T1 (en) 2015-12-31
CN102016311B (en) 2014-06-25
WO2009132934A1 (en) 2009-11-05

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