CN1224119A - Enclosed compressor - Google Patents

Enclosed compressor Download PDF

Info

Publication number
CN1224119A
CN1224119A CN99100933A CN99100933A CN1224119A CN 1224119 A CN1224119 A CN 1224119A CN 99100933 A CN99100933 A CN 99100933A CN 99100933 A CN99100933 A CN 99100933A CN 1224119 A CN1224119 A CN 1224119A
Authority
CN
China
Prior art keywords
valve seat
valve
cylinder
area
pressing chamber
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
CN99100933A
Other languages
Chinese (zh)
Other versions
CN1089866C (en
Inventor
熊泽健志
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.)
Toshiba Corp
Original Assignee
Toshiba 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
Application filed by Toshiba Corp filed Critical Toshiba Corp
Publication of CN1224119A publication Critical patent/CN1224119A/en
Application granted granted Critical
Publication of CN1089866C publication Critical patent/CN1089866C/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A hermetic compressor includes a cylinder housed in a sealed container; a rotary shaft provided coaxally in the cylinder; a rotating driving mechanism to rotating drive the rotary shaft; a bearing which is provided at the end face side of the above cylinder, and forms a compressive chamber in the cylinder as well as journals the rotary shaft; a compression mechanism to compress the compressed gas in the compressive chamber following the rotation of the rotary shaft; a discharge hole 52 provided to a main bearing, and to discharge the compressed gas compressed in the compressive chamber to the outer side of the compressed chamber; and a discharge valve 50 to open and close the discharge hole 52 are provided. The discharge valve is furnished with a valve seat 53 provided at the outer side of the compressive chamber, and a valve disc 54 surface- contacting with the valve seat 53. The present invention can prevent the damage of a valve disc even though the rotational frequency is increased.

Description

Hermetic compressor
The present invention relates to used hermetic compressors such as air conditioner, relate in particular to the improvement of noise-reducing structure.
Used hermetic compressor is the compressing mechanism of packing in closed container in the freezing cycle device of formation air conditioner or refrigerator etc., and discharges (refrigeration agent) to the compressing mechanism outside after being located at the pressing chamber process baffler in this compressing mechanism.
Be provided with expulsion valve shown in Figure 91 from pressing chamber to the position that baffler is discharged.Expulsion valve 1 have hole portion 2 for refrigerant gas circulation, the upper end of this hole portion 2 forms in Fig. 9 ring-type valve seat 3, and and this valve seat 3 be oppositely arranged and pushed to the valve body 4 of valve seat 3 by certain pushing force.
Hermetic compressor is in the pressing chamber inside of compressing mechanism refrigerant gas G to be compressed.In case refrigerant gas boosts to authorized pressure in pressing chamber inside, the valve body 4 of expulsion valve 1 is just opened, and discharges in baffler by (refrigeration agent).
Above-mentioned conventional hermetic-type compressor has following problem.That is, the section with position 3a valve body 4 butts valve seat 3 is a semi-circular shape, makes valve seat 3 become line with valve body 4 and contacts.Therefore, in case rotating speed raises, the bump between valve seat 3 and the valve body 4 just might cause valve body 4 breakages.
Also can prevent the hermetic compressor of valve body breakage even the object of the present invention is to provide a kind of rotating speed to rise for this reason.
In order to address the above problem and realize above-mentioned purpose, technical solution of the present invention 1 is a kind of to being compressed the hermetic compressor that gas compresses, have: closed container, be contained in the cylinder in this closed container, be located at the running shaft in this cylinder coaxially, this running shaft is rotated the running shaft driving mechanism of driving, be arranged on end face one side of above-mentioned cylinder and support above-mentioned running shaft, in above-mentioned cylinder, form the bearing of pressing chamber simultaneously, in above-mentioned pressing chamber, the above-mentioned gas that is compressed is carried out the compressor for compressing structure along with the rotation of above-mentioned running shaft, be located on the above-mentioned bearing and will in above-mentioned pressing chamber, compress after above-mentionedly be compressed the tap hole that gas is discharged outside above-mentioned pressing chamber, and the expulsion valve that this tap hole is opened and closed, above-mentioned expulsion valve has the valve seat by the above-mentioned pressing chamber outside that is located at above-mentioned tap hole, and carry out the valve body that face contacts with this valve seat.
Technical solution of the present invention 2 is in technological scheme 1, and above-mentioned valve seat forms with above-mentioned valve body and carries out ring-type valve seat planar surface portion and the above-mentioned valve seat bore portion that is compressed fluid flow of confession that face contacts.
Technical solution of the present invention 3 is in technological scheme 1 or 2, and making the area ratio between above-mentioned valve seat planes portion and the above-mentioned valve seat bore portion is more than 0.1.
Technical solution of the present invention 4 is in technological scheme 1 or 2, and making the area ratio between above-mentioned valve seat planes portion and the above-mentioned valve seat bore portion is below 0.5.
Produce following effect after adopting technique scheme.That is, the valve seat that the expulsion valve of technological scheme 1 has a pressured outdoor of contracting that is arranged on tap hole with carry out the valve body that face contacts with this valve seat, so also can not apply excessive collapsing force, can prevent the breakage of valve body to valve body even rotating speed rises.
Adopt technological scheme 2, valve seat forms and carries out ring-type valve seat planar surface portion and confession that face contacts with valve body and be compressed the valve seat bore portion of fluid flow, so can realize that with simple structure valve body contacts with the face of valve seat.
Adopting technological scheme 3, is more than 0.1 owing to make the area ratio between valve seat planes portion and the valve seat bore portion, so the scope that can expansion face contacts can prevent the breakage of valve body effectively.
Adopt technological scheme 4,,, can prevent the delay of opening of expulsion valve so can alleviate the back pressure that is applied on the valve body because the area between valve seat planes portion and the valve seat bore portion is compared below 0.5.
Simple declaration to accompanying drawing
Fig. 1 is the longitudinal section of two cylinder type rotary compressor major components of the present invention's one example.
Fig. 2 is pack into the main bearing in this pair cylinder type rotary compressor and the stereogram of running shaft.
Fig. 3 is the interior expulsion valve of this pair cylinder type rotary compressor of packing into.
Fig. 4 represent to pack into plotted curve of valve seat planes portion area and ratio, operating frequency and the valve destroyed area relation of valve seat bore portion area in this pair cylinder type rotary compressor.
Fig. 5 is the valve seat planes portion area of this expulsion valve of expression and the plotted curve of the relation between the opening valve time when of valve seat bore portion area.
Fig. 6 is the plotted curve that expression is packed into and concerned between pressing chamber inner refrigerant volume in this pair cylinder type rotary compressor and the pressure.
Fig. 7 is the plotted curve that concerns between ratio, differential pressure and the noise reduction amount of expression valve seat planes portion area of this expulsion valve and valve seat bore portion area.
Fig. 8 is the plotted curve that concerns between expression this pair cylinder type rotary compressor upper frequency and the sound power stage.
Fig. 9 is the longitudinal section of the interior expulsion valve major component of being adorned of conventional hermetic-type compressor.
The invention process form below is described.
Fig. 1 is the longitudinal section of two cylinder type rotary compressors 10 of the present invention's one example, and Fig. 2 is the stereogram of the main bearing 43 in this pair cylinder type rotary compressor (hermetic compressor) 10 of packing into.Fig. 3 expulsion valve 50 in this pair cylinder type rotary compressor 10 of representing to pack into.
Two cylinder type rotary compressors 10 have closed container 20, be contained in motor part 30 (rotary drive mechanism) in this closed container 20, compressing mechanism 40 and at the framework 60 of closed container 20 internal support compressing mechanisms 40.
Motor part 30 has the stator department 31 that is installed on closed container 20 inner wall parts, the rotor part 32 of rotating the hollow portion that is arranged on this stator department 31 freely and the running shaft 33 that is fixed on the central part of this rotor part 32.In addition, an end of running shaft 33 forms eccentric part 33a, the 33b that extends in the upper and lower air cylinders 41,42 described later.
Compressing mechanism 40 has: upper cylinder 41 cylindraceous and lower cylinder 42, be installed in the upper-end surface of upper cylinder 41 and in upper cylinder 41, form the pressing chamber 45 described later main bearing 43 of supporting rotating shaft 33 simultaneously, be installed in the lower end surface of lower cylinder 42 and in lower cylinder 42, form the pressing chamber 46 described later supplementary bearing 44 of supporting rotating shaft 33 simultaneously, the pressing chamber 45 that in upper cylinder 41, forms, the pressing chamber 46 that in lower cylinder 42, forms, rotation is eccentrically set on these pressing chambers 45 freely, in 46 again respectively with the eccentric part 33a of running shaft 33, the rotor 47a that 33b is chimeric, 47b, and the demarcation strip of between the upper-end surface of the lower end surface of upper cylinder 41 and lower cylinder 42, separating 48.
On upper and lower air cylinders 41 and 42, be respectively equipped with air intake passage 41a and 42a (not shown) in the refrigerant gas G introducing pressing chamber 45 and 46.
The upside of main bearing 43 is installed with the 1st 49a of anechoic chamber and the 2nd 49b of anechoic chamber in Fig. 1.Between pressing chamber 45 and the 1st 49a of anechoic chamber, be provided with expulsion valve 50.On the other hand, the downside of supplementary bearing 44 is installed with the 3rd 49c of anechoic chamber in Fig. 1.Between pressing chamber 46 and the 3rd 49c of anechoic chamber, be provided with expulsion valve 50.
The valve body 54 that expulsion valve 50 has main body 51, be located at hole portion 52 on this main body 51, be located at the valve seat 53 by anechoic chamber's one side of hole portion 52, be oppositely arranged with this valve seat 53, with certain pressure this valve body 54 is pressed to the block 55 of valve seat 53 1 sides.
The 53b of valve seat bore portion that valve seat 53 has the 53a of valve seat planes portion of upper end one side that is located at Fig. 2 mesopore portion 52 and is positioned at this valve seat planes portion 53a inboard.In addition, the area (to call " area A " in the following text) of the area of the 53a of valve seat planes portion (to call " area B " in the following text) and the 53b of valve seat bore portion is decided to be optimum value shown in down.
Big more with the area of the 53a of valve seat planes portion of the valve seat 53 of valve body 54 butts, valve seat 53 just can become face more with valve body 54 and contact, and valve body 54 just is difficult for destroyed.As shown in Figure 4, (area B/area A) is more little, and then valve body 54 zone of being damaged is low more.Especially be 0.1 when following when (area B/area A), the frequency that becomes the valve destroyed area just sharply reduces.Therefore, (area B/area A) is preferably more than 0.1.
On the other hand, if the 53a of valve seat planes portion of valve seat 53 increases, the area that then applies back pressure just increases, and valve body 54 just is difficult to open.And in a single day (area B/area A) increases, and hole portion 52 just narrows down, and the flow velocity of refrigeration agent is accelerated.Therefore, the power that valve body 54 is upwards pushed away just diminishes, and the time t that valve is opened postpones.Like this, sometimes just can not bring into play the cooling capacity of regulation.
As shown in Figure 5, the time of the opening t of valve is 0.5 when following, just with (area B/area A) proportional shortening in (area B/area A).And work as (area B/area A) is 0.5 just to become fixing when above.Therefore, (area B/area A) is preferably in below 0.5.
This pair of cylinder type rotary compressor 10 compresses refrigerant gas G as follows.That is, in case make motor part 30 work, running shaft 33 rotates immediately, and rotor 47a and 47b just do eccentric rotation in pressing chamber 45.Simultaneously refrigerant gas G is introduced in pressing chamber 45 and 46 through air intake passage 41c and 42c (not shown).Owing to the effect of rotor 47a and 47b, it is also boosted that inner refrigerant gas G is compressed in pressing chamber 45 and 46.The refrigerant gas G that boosts to behind the authorized pressure discharges in the 1st 49a of anechoic chamber and the 3rd 49c of anechoic chamber from expulsion valve 50 separately, and back, interflow discharge to closed container 20 in the 2nd 49b of anechoic chamber.
Fig. 6 is the plotted curve that concerns between the volume of the refrigerant gas G in the expression pressing chamber 45 and the pressure.That is, along with in pressing chamber 45 refrigerant gas G being compressed, the refrigerant pressure in the pressing chamber 45 rises to head pressure from suction pressure.Then, expulsion valve 50 is opened, and the refrigerant gas G in the pressing chamber 45 discharge in the 1st 49a of anechoic chamber, but owing to the reasons such as resistance of expulsion valve 50, pressure when expulsion valve 50 is opened in the pressing chamber 45 is higher than head pressure, and refrigerant gas G is discharging in the 1st 49a of anechoic chamber under such state.
And then, because the pressure difference between in pressure in the pressing chamber 45 and the 1st 49a of anechoic chamber makes refrigerant gas G expansion and becomes the pressure oscillation composition, the noise when forming compressor operation.Therefore, the noise when reducing compressor operation, effective method are the pressure differences (differential pressure) between the interior head pressure of the pressure in the pressing chamber 45 and the 1st 49a of anechoic chamber when reducing expulsion valve 50 and opening.Here, the differential pressure Pp between interior is shown below with the 1st 49a of anechoic chamber in the pressure chamber 45:
Pp=(Fv+Pd area B)/area A ... (1)
In the formula, Fv is the power of the valve body 54 pushing valve seats 53 of expulsion valve 50.
Therefore, in order to reduce differential pressure Pp, (area B)/(area A) is the smaller the better.Fig. 7 represents the relation of (area B)/(area A), differential pressure Pp and noise reduction amount.As we know from the figure, be that 0.5 occasion is compared with (area B)/(area A), be 0.4 occasion in (area B)/(area A), noise will reduce 1dB.
In addition, to be depicted as (area B)/(area A) be 0.53 occasion to solid line α among Fig. 8, and it is 0.22 occasion that dotted line β is depicted as (area B)/(area A), and therefrom noise significantly reduces as can be known.
Like this, if consider the breakage of valve and opening the time of valve, then the area (area B) of the valve seat planes 53a of portion is preferably within the scope of 0.1≤(area B)/(area A)≤0.5 with ratio (area B)/(area A) of the area (area A) of the 53b of valve seat bore portion.If also consider and noise problem then under possible condition, should so more help reducing noise as far as possible near 0.1.
In addition, the present invention is not limited to above-mentioned example.That is, above-mentioned example is to be used for two cylinder type rotary compressors, also can be used for single cylinder type rotary compressor in fact.Self-evident, all examples can be arranged without departing from the spirit and scope of the present invention.
Adopt such scheme, will produce following effect. That is, when adopting technical scheme 1, because the dump valve tool The valve seat that the pressured contracting outside that is arranged on tap arranged with carry out the valve body that face contacts with this valve seat, so even Rise of rotational speed can not apply excessive destructive power to valve body yet, can prevent the valve body breakage.
When adopting technical scheme 2 and since form on the valve seat ring-type valve seat planar portions that contacts as face with valve body with For the valve seat bore section of compressed fluid circulation, so available simple structure realizes that valve body contacts with the face of valve seat.
When adopting technical scheme 3, be 0.1 owing to make the Area Ratio between valve seat planes section and the valve seat bore section More than, thus can expansion face the scope of contact, can effectively prevent the breakage of valve body.
When adopting technical scheme 4, owing to make Area Ratio between valve seat planes section and the valve seat bore section 0.5 Below, so can alleviate the back pressure that valve body is applied, can prevent that dump valve from opening delay.

Claims (4)

1. hermetic compressor is to being compressed the hermetic compressor that gas compresses, it is characterized in that, has:
Closed container;
Be contained in the cylinder in this closed container;
Be located at the running shaft in this cylinder coaxially;
This running shaft is rotated the running shaft driving mechanism of driving;
Be arranged on end face one side of described cylinder and described running shaft is carried out the bearing that axle supports, forms pressing chamber simultaneously in described cylinder;
In described pressing chamber, the described gas that is compressed is carried out the compressor for compressing structure along with the rotation of described running shaft;
Be located on the described bearing and will in described pressing chamber, compress after describedly be compressed the tap hole that gas is discharged outside described pressing chamber;
The expulsion valve that this tap hole is opened and closed,
Described expulsion valve have the valve seat that is located at described tap hole by the described pressing chamber outside,
And carry out the valve body that face contacts with this valve seat.
2. hermetic compressor according to claim 1 is characterized in that, described valve seat forms with described valve body and carries out ring-type valve seat planar surface portion and the described valve seat bore portion that is compressed fluid flow of confession that face contacts.
3. hermetic compressor according to claim 1 and 2 is characterized in that, the area ratio between described valve seat planes portion and the described valve seat bore portion is more than 0.1.
4. hermetic compressor according to claim 1 and 2 is characterized in that, the area ratio between described valve seat planes portion and the described valve seat bore portion is below 0.5.
CN99100933A 1998-01-21 1999-01-08 Enclosed compressor Expired - Lifetime CN1089866C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10009470A JPH11210626A (en) 1998-01-21 1998-01-21 Hermetic compressor
JP009470/98 1998-01-21

Publications (2)

Publication Number Publication Date
CN1224119A true CN1224119A (en) 1999-07-28
CN1089866C CN1089866C (en) 2002-08-28

Family

ID=11721164

Family Applications (1)

Application Number Title Priority Date Filing Date
CN99100933A Expired - Lifetime CN1089866C (en) 1998-01-21 1999-01-08 Enclosed compressor

Country Status (4)

Country Link
JP (1) JPH11210626A (en)
KR (1) KR100288677B1 (en)
CN (1) CN1089866C (en)
TW (1) TW467202U (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100460674C (en) * 2003-10-08 2009-02-11 开利公司 Reciprocating compressor with enlarged valve seat area

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5652613B2 (en) 2011-03-08 2015-01-14 サンデン株式会社 Compressor valve equipment
WO2013140912A1 (en) * 2012-03-23 2013-09-26 東芝キヤリア株式会社 Rotating compressor and freeze-cycle apparatus
KR101872374B1 (en) * 2012-05-29 2018-06-28 한온시스템 주식회사 Compressor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5033769A (en) * 1973-07-26 1975-04-01
JPH04358772A (en) * 1991-06-03 1992-12-11 Toyota Autom Loom Works Ltd Valve device for reciprocating type compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100460674C (en) * 2003-10-08 2009-02-11 开利公司 Reciprocating compressor with enlarged valve seat area

Also Published As

Publication number Publication date
TW467202U (en) 2001-12-01
JPH11210626A (en) 1999-08-03
KR100288677B1 (en) 2001-11-15
KR19990066928A (en) 1999-08-16
CN1089866C (en) 2002-08-28

Similar Documents

Publication Publication Date Title
CN1089866C (en) Enclosed compressor
CN1239757A (en) Rotary compressor having plurality of compression chambers for multistage compression
WO2003044373A1 (en) Hermetic compressor
JPH07229481A (en) Double rotary type scroll compressor
JP3123125B2 (en) 2-cylinder rotary compressor
CN1314898C (en) Reciprocating compressor
CN1093605C (en) Noise reducing structure for hermetically sealed compressor
CN1161543C (en) Booster for closed compressor
JPH08193584A (en) Rotary type compressor
JPH06307362A (en) Rotary compressor
KR19990040633A (en) Thrust bearings in hermetic reciprocating compressors
KR0128917Y1 (en) A rotary compressor
CN1746503A (en) Scroll compressor having vacuum preventing structure
KR20010076883A (en) Apparatus for reducing axial leakage of scroll compressor
KR100332782B1 (en) Structure for reduction of noise in rotary compressor
KR100343687B1 (en) Apparatus for preventing superheating of fixing-scroll in scroll compressor
KR19980046483A (en) Rotary compressor
KR100479495B1 (en) Rotary compressor
KR100286311B1 (en) Structure for reducing noise of scroll compressor
KR100556954B1 (en) Accumulator structure of rotary compressor
KR200154001Y1 (en) Coolant filling pipe of compressor
JP2000097178A (en) Roller for rotary compressor
KR950007238Y1 (en) Rotary compressor
KR200159710Y1 (en) Discharge device of a hermetic reciprocating compressor
KR100343729B1 (en) Apparatus for preventing vacuum compression of scroll compressor

Legal Events

Date Code Title Description
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C06 Publication
PB01 Publication
C14 Grant of patent or utility model
GR01 Patent grant
CX01 Expiry of patent term
CX01 Expiry of patent term

Granted publication date: 20020828