EP2300715B1 - Compresseur avec performance de débit du fluide frigorigène améliorée - Google Patents

Compresseur avec performance de débit du fluide frigorigène améliorée Download PDF

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Publication number
EP2300715B1
EP2300715B1 EP09737976.2A EP09737976A EP2300715B1 EP 2300715 B1 EP2300715 B1 EP 2300715B1 EP 09737976 A EP09737976 A EP 09737976A EP 2300715 B1 EP2300715 B1 EP 2300715B1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
refrigerant
protrusion
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.)
Active
Application number
EP09737976.2A
Other languages
German (de)
English (en)
Other versions
EP2300715A1 (fr
Inventor
Bilgin Hacioglu
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 SI200931272T priority Critical patent/SI2300715T1/sl
Publication of EP2300715A1 publication Critical patent/EP2300715A1/fr
Application granted granted Critical
Publication of EP2300715B1 publication Critical patent/EP2300715B1/fr
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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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/18—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the effective cross-section of the working surface of the piston
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

  • the present invention relates to a compressor wherein the flow performance of the refrigerant left in the cylinder during the pumping of the refrigerant is improved.
  • a piston is provided for suction of the refrigerant and a cylinder wherein the piston is disposed.
  • a valve table is provided on the cylinder whereon the suction and discharge holes are arranged.
  • the piston receives the refrigerant from the suction hole by reciprocating inside the cylinder and afterwards reciprocates for compressing and pumping the refrigerant through the discharge hole out of the cylinder.
  • One of the criteria for efficient operation of the compressor is the rate of the refrigerant, received into the cylinder in one cycle, discharged out of the cylinder.
  • the piston compresses the refrigerant, all of the refrigerant cannot be discharged from the discharge hole out of the cylinder and the compressor yield decreases.
  • a lot of patent documents explain how to decrease the dead space formed in the cylinder cavity that affects the volumetric efficiency, the refrigerant volume left in the cylinder without being discharged when the piston reaches the top point.
  • the dead space is zero. As the amount of the dead space increases, the compressor efficiency decreases. The reason for this is that, despite consuming energy for discharging the entire refrigerant inside the cylinder by compressing the piston in the entire cylinder volume, the refrigerant equaling to the dead space cannot be discharged out of the cylinder.
  • a boss arranged on one face of the piston that is seated in the delivery orifice occupies the greater part of the dead space during the compression of the refrigerant.
  • the boss and the delivery orifice can be configured of matching cylindrical or frustoconical shapes. Since the cross section through which the refrigerant passes gets narrower as the boss is seated in the delivery orifice and since the boss closes the entire delivery orifice, as a result of formed turbulences, the discharge of the refrigerant gets difficult and losses increase. Some part of the gain by decreasing the dead space is lost by making the flow difficult.
  • a projection formed on the top of the piston and the discharge port are configured to be frustoconical. Since the gradient of the conical surface of said projection is smaller than that of the side wall of the said discharge port, the narrowness of the cross section formed by the projection being seated inside the discharge port is partially decreased.
  • projections are provided on the piston that decrease the dead space without obstructing passage of the refrigerant until the piston reaches the top dead center and enter into the discharge port when the piston reaches the top dead center.
  • the aim of the present invention is the realization of a compressor wherein the flow of the refrigerant through the cylinder to the discharge hole 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 at least one groove on the lateral surfaces of the protrusion arranged on the piston, extending from the piston surface towards the top end of the protrusion.
  • the protrusion When the piston reaches the top dead center, that is when the piston surface is at the nearest position to the valve table, the protrusion is partially seated in the discharge hole.
  • the grooves formed on the protrusion By means of the grooves formed on the protrusion, the sudden narrowing of the flow path cross section is prevented and the refrigerant flow from the discharge hole is convenient, with a controllable discharge and without creating much dead space.
  • the sudden increase of the refrigerant acceleration and the temperature and respectively the decrease in yield by the reducing of pressure is prevented.
  • the groove guides the refrigerant towards the discharge hole and shapes the flow of the refrigerant.
  • the groove is formed on the portion of the protrusion near the cylinder axis. Accordingly, refrigerant flow can be improved in the region wherein the refrigerant flow is intense.
  • two opposing inner side walls of the groove extend parallel to each other.
  • the opposing inner side walls of the groove can either be parallel to the protrusion axis or can be inclined with a certain angle therebetween.
  • the groove has a cross section that gets narrower from the piston surface towards the top of the protrusion. Accordingly, the speed of flow that slows when the piston reaches the top dead center is accelerated.
  • the groove has a depth that increases from the piston surface towards the top of the protrusion.
  • the dead space is minimized by improving the refrigerant flow. This results in the increase of the compressor efficiency.
  • the circulation of the refrigerant fluid that is utilized for cooling is maintained by a hermetic compressor (1) having a piston.
  • the compressor (1) comprises a cylinder (2) wherein the refrigerant is received, a cylinder head (3) disposed on the cylinder (2), a valve table (4) whereon the cylinder head (3) is emplaced, a discharge hole (5) on the valve table (4) wherefrom the refrigerant received into the cylinder (2) is discharged, a piston (6) disposed inside the cylinder (2) that activates the refrigerant by reciprocating inside the cylinder (2) ( Figure 1 ).
  • the motion of the motor is transferred by the crank-piston rod-crank pin (not shown in the figures) to the piston (6), maintaining the piston (6) to reciprocate within the cylinder (2).
  • the refrigerant within the cylinder (2) is compressed with the reciprocating motion of the cylinder (2).
  • the opening of the discharge valve (not shown in the figures) covering the discharge hole (5) the refrigerant passes through the discharge hole (5) and reaches the cylinder head (3).
  • the compression process of the refrigerant is performed as the piston (6) starts to approach near the top dead center.
  • the grooves (8) formed on the protrusion (7) prevent the sudden decrease in the cross section wherein the flow takes place as the protrusion (7) enters into the discharge hole (5) and maintains the discharge of the refrigerant from the discharge hole (5) controllably ( Figure 8 ). Accordingly, the temperature rise of the refrigerant with sudden increase in acceleration and the decrease of pressure are prevented.
  • the piston (6) reaches the top dead center, the discharge of the refrigerant from the discharge hole (5) continues by means of the grooves (8) and the dead space in the cylinder (2) is minimized.
  • the flow of the refrigerant is controlled by means of the grooves (8) formed on the protrusion (7).
  • the protrusion (7) is cylinder shaped.
  • the protrusion (7) is configured frustoconically ( Figure 2 to Figure 7 ).
  • the protrusion (7) comprises a groove (8) formed on the region thereof near the cylinder (2) axis ( Figure 6 and Figure 7 ).
  • both opposing inner side walls of the groove (8) extend parallel to each other ( Figure 3 and Figure 4 ).
  • the opposing inner side walls of the groove (8) are inclined such that they remain parallel to each other ( Figure 5 ).
  • the groove (8) has a cross section that gets narrower from the surface of the piston (6) towards the top of the protrusion (7) ( Figure 2 ).
  • the groove (8) has a depth that increases from the surface of the piston (6) towards the top of the protrusion (7) ( Figure3 ).
  • the protrusion (7) and the groove (8) are produced in one piece.
  • the protrusion (7) is mounted on the piston (6) to be fully overlapping with the surface of the piston (6).
  • the refrigerant flow within the cylinder (2) is improved by means of the groove (8) and the flow losses are reduced. Accordingly, much more refrigerant can be discharged from the cylinder (2). This results in the increase of the compressor (1) efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (5)

  1. Un compresseur (1) qui comprend un cylindre (2) dans lequel le fluide frigorigène est reçu, une tête du cylindre (3) qui est disposée sur le cylindre (2), un tableau de soupape (4) sur lequel la tête du cylindre (3) est placée, un trou d'évacuation (5) sur le tableau de soupape (4) d'où le fluide frigorigène reçu dans le cylindre (2) est évacué, un piston (6) qui est disposé dans le cylindre (2) et qui active le fluide frigorigène par le mouvement alternatif dans le cylindre (2) et une protubérance (7) qui est arrangée sur le piston (6) et qui est placée dans le trou d'évacuation (5) lorsque le piston (6) atteint le plein centre supérieur, caractérisé en ce qu'au moins une rainure (8) est arrangée sur la surface latérale de la protubérance (7), par lequel la rainure (8) s'étend à partir de la surface du piston (6) vers le haut de la protubérance (7).
  2. Un compresseur (1) selon la Revendication 1, caractérisé par la rainure (8) qui présente deux parois latérales intérieures opposées s'étendant parallèlement l'une à l'autre.
  3. Un compresseur (1) selon la Revendication 1, caractérisé par la rainure (8) qui présente deux parois latérales intérieures opposées s'étendant d'une manière inclinée.
  4. Un compresseur (1) selon la Revendication 1, caractérisé par une rainure (8) ayant une coupe transversale qui se rétrécit à partir de la surface du piston (6) vers le haut de la protubérance (7).
  5. Un compresseur (1) selon l'une quelconque des revendications de 1 à 4, caractérisé par une rainure (8) ayant une profondeur qui augmente à partir de la surface du piston (6) vers le haut de la protubérance (7).
EP09737976.2A 2008-05-01 2009-04-07 Compresseur avec performance de débit du fluide frigorigène améliorée Active EP2300715B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI200931272T SI2300715T1 (sl) 2008-05-01 2009-04-07 Kompresor z izboljšanim učinkom toka hladiva

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TR200803042 2008-05-01
PCT/EP2009/054140 WO2009132932A1 (fr) 2008-05-01 2009-04-07 Compresseur à circulation de fluide frigorigène améliorée

Publications (2)

Publication Number Publication Date
EP2300715A1 EP2300715A1 (fr) 2011-03-30
EP2300715B1 true EP2300715B1 (fr) 2015-07-01

Family

ID=40849290

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09737976.2A Active EP2300715B1 (fr) 2008-05-01 2009-04-07 Compresseur avec performance de débit du fluide frigorigène améliorée

Country Status (4)

Country Link
EP (1) EP2300715B1 (fr)
ES (1) ES2547407T3 (fr)
SI (1) SI2300715T1 (fr)
WO (1) WO2009132932A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107923378A (zh) * 2015-08-26 2018-04-17 开利公司 往复式压缩机排气活塞

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3136477A (en) 1961-03-28 1964-06-09 Worthington Corp Multi-stage compressor
FR2617242A1 (fr) 1987-06-26 1988-12-30 Unite Hermetique Sa Compresseur a rendement ameliore
US5816783A (en) 1993-05-19 1998-10-06 Hitachi, Ltd. Electrically driven hermetic compressor
WO2000071896A1 (fr) 1999-05-25 2000-11-30 Danfoss Compressors Gmbh Compresseur a refrigerant
US6540492B2 (en) * 2001-04-09 2003-04-01 Carrier Corporation Compressor piston with reduced discharge clearance
ATE484678T1 (de) 2003-07-31 2010-10-15 Arcelik As Verdichter
US6997148B1 (en) 2004-10-15 2006-02-14 Caterpillar Inc. Engine valve actuator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107923378A (zh) * 2015-08-26 2018-04-17 开利公司 往复式压缩机排气活塞

Also Published As

Publication number Publication date
WO2009132932A1 (fr) 2009-11-05
EP2300715A1 (fr) 2011-03-30
SI2300715T1 (sl) 2015-10-30
ES2547407T3 (es) 2015-10-06

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