CN1434212A - Reciprocative sealing type electric compressor - Google Patents
Reciprocative sealing type electric compressor Download PDFInfo
- Publication number
- CN1434212A CN1434212A CN03102719A CN03102719A CN1434212A CN 1434212 A CN1434212 A CN 1434212A CN 03102719 A CN03102719 A CN 03102719A CN 03102719 A CN03102719 A CN 03102719A CN 1434212 A CN1434212 A CN 1434212A
- Authority
- CN
- China
- Prior art keywords
- joint mechanisms
- ball
- ball joint
- seal type
- connecting rod
- 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
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
- 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
- F04B39/0094—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 crankshaft
-
- 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
-
- 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
- F04B39/0022—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 piston rods
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
A technical problem is an electromotive sealed reciprocating compressor that comprises a link (9) extending from a crank pin (5b) integrally formed with a rotating shaft and coupled to a piston (7) received in a cylinder (8) by a spherical joint mechanism (10). The spherical joint mechanism is comprised of a sphere (12) integrally formed with an end of the link and a ball bearing (13) arranged in the piston and slidably surrounding and supporting the sphere. The compressed object is a coolant of iso-butane (R600a). The relationship between the average velocity V of the spherical joint mechanism and the load F acting upon the spherical joint mechanism during the compression stroke is set to VxF < 200 N.m/s. The object of the present invention is to provide an electromotive sealed reciprocating compressor to which a refrigeration circulation system based on iso-butane (R600a) can be employed for effectively preventing damage to the ozonosphere and reducing influence to the warm-up of the earth.
Description
Technical field
The present invention relates to be used for refrigeration cycle, will be as the isobutane (R600a) of natural refrigeration agent reciprocating seal type motor compressor as the compressed object fluid.
Background technique
For example in refrigerator etc., as the compressor that constitutes refrigeration cycle, most reciprocating seal type motor compressors that use.And in this compressor, one being located at the crank pin on the main shaft and being housed in one of means that the piston in the cylinder couples together has ball joint mechanisms portion.
Ball joint mechanisms portion is connected with an end of connecting rod in the large-diameter portion of rotating the crank pin embed main shaft freely, and internal piston is extended in the other end of connecting rod.Ball is located at the other end of connecting rod integratedly, is embraced and free sliding by the ball bearing that is located at described piston.
Described main shaft is subjected to rotating drive, and then connecting rod carries out along with crank pin that off-centre rotatablely moves and is that oscillating motion is done at the center with ball joint mechanisms portion.Thereby piston is reciprocating in cylinder, carries out the suction and the discharge of gas refrigerant repeatedly.
Yet, for example being used for the refrigeration agent of the refrigeration cycle that refrigerator uses, the general use is the R134a (1,1,1,2 HFC-134a) of HFC (hydrocarbon fluoride) refrigeration agent.By adopting R134a, eliminate the worry that damages the ozone layer of refrigeration agent-R12 (dichlorodifluoromethan) shortcoming of in the past using, be extremely effective aspect the earth environment protection.
As refrigeration agent, except the depletion of the ozone layer coefficient, also seek the low refrigeration agent of global warming coefficient.In the occasion of R134a, the depletion of the ozone layer coefficient is " 0 ", and there is a certain degree in the greenhouse coefficient.Therefore, be limited to whole refrigeration cycle apparatus and use R134, may have influence on global warmingization in the near future.
On the other hand, and natural refrigeration agent that global warming coefficient low low as the depletion of the ozone layer coefficient, known have an isobutane (R600a).By adopting this refrigeration agent, can almost make to prevent to damage the ozone layer and prevent that global warmingization from simultaneously and deposit, being extremely desirable.
, present situation is, constitutes other part between development period in the refrigeration cycle that adapts to R134a, and the formation that adapts to isobutane (R600a) part is not in addition set about substantially.Therefore, the present inventor pays attention to use refrigeration agent to make the more significant compressor of influence by changing.
Summary of the invention
Study in view of described situation for this, its objective is, provide not only to be effectively and can to adapt to the reciprocating seal type motor compressor of the use refrigeration agent-isobutane (R600a) few, raising reliability the influence of global greenhouse effect to preventing to damage the ozone layer.
In order to realize described purpose, reciprocating seal type motor compressor of the present invention is, connecting rod is extended from the crankpin with integrated spindle axis, connect this connecting rod and the piston that is housed in the cylinder by ball joint mechanisms portion, ball joint mechanisms portion is located at the ball on the interlinking lever end and is located at the ball bearing of embracing ball on the piston sliding freely by one and forms, as refrigeration agent-isobutane (R600a), the relation that acts on the load F of ball joint mechanisms portion when the mean velocity V of ball joint mechanisms portion and compression stroke is set at V * F＜200Nm/s with the compressed object fluid.
And the diameter d that constitutes the ball of ball joint mechanisms portion is set in below the 14.5mm,
Rotatablely move and in the motion of the connecting rod swing that produces, the pendulum angle of connecting rod is set in below 54 ° in off-centre along with crank pin.
The speed setting of main shaft is below 105rps.
In addition, ball bearing is implemented nitriding treatment and manganese phosphate processing, perhaps implement wherein a kind of processing.
As ball material, adopt the high-carbon chromium steel material that contains chromium (Cr) 0.5～2.0%.
Be folded with the buffering ring of forming by moldable resins such as PTFE, PFA between ball and the ball bearing.
Be suitable for most the compressor that refrigeration agent is the compression usefulness of isobutane (R600a) owing to adopting the measure that solves described problem, becoming, to improve reliability.
The simple declaration of accompanying drawing
Fig. 1 is the vertical profile plan view of the reciprocating seal type motor compressor of expression an embodiment of the present invention.
Fig. 2 is the diagrammatic sketch of run of the explanation compression mechanical part of expression an embodiment of the present invention.
Fig. 3 is the graph of a relation of the wear extent of the F * V value of ball joint mechanisms portion of expression an embodiment of the present invention and ball bearing.
The working of an invention mode
Below, with reference to the description of drawings embodiments of the present invention.
Fig. 1 is vertical profile plan view refrigeration cycle, reciprocating seal type motor compressor that for example constitutes refrigerator.
As the refrigeration cycle of refrigerator, except described compressor, possess condenser, expansion gear and vaporizer, these constitution equipments are communicated with by refrigerant pipe, to constitute refrigeration cycle.
As the refrigeration agent that is used for such refrigeration cycle, adopt isobutane (R600a) as natural refrigeration agent, as the compressor that is adapted to most this refrigeration agent, possess reciprocating seal type motor compressor described later.
In this reciprocating seal type motor compressor, 1 is vertical seal casinghousing among the figure, and the intermediate portion of the lower direction haply in sealing housing 1, framework 2 are by spring 2a and by yielding support.The upper side of described framework 2 is carried and is provided with compressor 3, and lower side is provided with motor part 4.
Described compression mechanical part 3 adopts so-called reciprocating seal type compressor.Be noted that in addition along the central part of described framework 2 the pivot hole 2b that draws is set, rotation embeds the rotatingshaft 5 as main shaft freely.
The upper end portion of rotatingshaft 5 is wholely set lip part 5a, its be loaded in sliding freely framework 2 above, and the top of lip part 5a is connected with crank pin 5b, its central shaft that has is with the eccentricity of central axis of established amount and rotatingshaft 5.
Thus, when rotatingshaft 5 was driven in rotation, then lip part 5a rotated with sliding contact state on framework 2, and described crank pin 5b makes eccentric rotary on every side along rotatingshaft 5 centers.
Described compression mechanical part was located at above the framework 2 in 3 years, and possessed and make the cylinder 6 of axle direction towards level.The inside of this cylinder 6 becomes the cylinder chamber 8 that can back and forth accommodate piston 7 freely.
One end of connecting rod 9 is connected in piston 7 by ball joint mechanisms portion 10.The other end of described connecting rod 7 is provided with big end 11, and its rotation is entrenched on the described crank pin 5b freely.
Describe about described ball joint mechanisms portion 10, ball 12 is wholely set the end at described connecting rod 9.In one side, be provided with ball bearing 13 in the inside of piston 7.This ball bearing 13 rotates embraces described ball 12 freely.
Because constitute like this, along with the eccentric rotary of crank pin 5b, it is the oscillating motion of fulcrum that connecting rod 9 can form with ball-and-socket mechanism 10, so that piston 7 is reciprocating in cylinder 6.
On the other hand, the opening end of cylinder 6 is sealed by valve system 15, and, cover with cylinder head 16.Detailed icon not, but the spacer portion that inside is divided into two is set on the described cylinder head 16, the one side space forms induction chamber, and the opposing party space becomes exhaust chamber.
Described valve system 15 is provided with the valve plate with intakeport and relief opening, and each intakeport and relief opening open and close with Aspirating valves and outlet valve.And described intakeport is relative with induction chamber, and relief opening is relative with exhaust chamber.
For the compression mechanical part 3 of such formation, described motor part 4 comprise with from the framework of described rotatingshaft 5 downwards outstanding position setting-in rotor 17, have the inner peripheral surface of close gap with the side face of this rotor 17 and from the vertical fixing stator 18 that is provided with of described framework 2 usefulness appropriate device.
Then, the compression operation of described reciprocating seal type motor compressor is described, and along with the refrigeration cycle effect of its operation.
To motor part 4 energisings, rotation drives rotatingshaft 5, and crank pin 5b makes the one eccentric rotary.Along with this eccentric rotary, piston 7 to-and-fro motion in cylinder chamber 8 by connecting rod 9 and ball joint mechanisms portion 10.
In seal casinghousing 1, import, be full of refrigerant gas that the low pressureization by evaporator evaporation is arranged, be isobutane (R600a).This gas is introduced into the induction chamber in the compressor front cover 16, and is inhaled into the cylinder chamber 8 of cylinder 6 along with the moving (positive movement) of piston 7.
By piston 7 reverse mobile (return motion), isobutane gas is compressed.Piston 7 moves to so-called dead center position, and then expulsion valve is opened, and is compressed the discharge chamber that the isobutane gas that forms high-pressure trend is discharged to compressor front cover 16 in cylinder chamber 8.
These pressurized gas export to the external refrigeration pipe by discharge tube in the housing from seal casinghousing 1, and are imported into described refrigeration cycle.Because rotatingshaft 5 is rotated further, piston 7 to-and-fro motion are just carried out described refrigeration cycle repeatedly.
Fig. 2 is the approximate vertical view that the part of compressing mechanism 3 makes cross section.
The eccentric rotational motion, described connecting rod 9 that now specify described crank pin 5b are along with eccentric rotational motion is done oscillating motion, with the relation of described ball joint mechanisms portion 10 and described piston 7.
Along with the rotation of described rotatingshaft 5, crank pin 5b makes eccentric rotary, and crank pin center O a describes with the circular rotary motion trace of offset as the radius of gyration.Connecting rod 9 becomes the oscillating motion with the pendulum angle α of regulation, and ball 12 slides mutually with ball bearing 13 in ball joint mechanisms portion 10.
To the isobutane as refrigerant gas (R600a) that imports cylinder chamber 8 when gas compresses, load action is in the end face of piston 7, and this power acts on ball joint mechanisms portion 10 by piston 7.
Generally, as evaluation to portion of spherojoint nest mechanism 10, the surface pressure (P) that can exemplify ball joint mechanisms portion 10 is long-pending with the Sliding velocity (V) of ball joint mechanisms portion 10, and is mean velocity (V) long-pending as index when sliding with ball 12 with described maximum load (F) here.
The long-pending formula of calculating maximum load F and mean velocity V is as follows:
F＝(π/4)×(D
2)×(Pd-Ps)
V＝π×d×(α/360)×f
In the formula: D: the diameter of piston 7, Pd: exhaust pressure, Ps: pressure of inspiration(Pi),
D: the diameter of ball 12, α: the angle of oscillation of connecting rod 9
F: the rotating speed of rotating shaft 5.
Fig. 3 is F * V value and performance plot in the wear extent relation of the ball bearing 13 of ball joint mechanisms portion 10.
F * V value then is the few kilter of wear extent below 200Nm/s.And when 200Nm/s is above, the tendency that has wear extent to increase.
If consider the working pressure of isobutane (R600a), suppose that then the exhaust pressure maximum is 1 (MPa), pressure of inspiration(Pi) is minimum to be 0, the degree of 05MPa.
This kind occasion, in order to satisfy F * V＜200Nm/s, the diameter of ball 12 is that 14.5mm is following, angle of oscillation is below 54 °, the rotating speed of rotatingshaft 5 is to be good below the 105rps.
For the wear resistance performance that makes ball joint mechanisms portion 10 improves, bear the ball bearing 13 of side for forming ball joint mechanisms portion 10, implementing the processing of nitriding treatment and manganese phosphate or implementing wherein a kind of processing is effective means.
Be located at the material of ball 12 of an end of connecting rod 9 as one, it also is effective adopting the high carbon chromium steel that contain chromium (Cr) 0.2-2.0%.
Like this, as the feature in ball joint mechanisms portion 10, ball bearing 13 bears ball 12 by riveted joint (plastic deformation) processing.In addition, establish the ring-type buffering ring 20 be made up of the plastic material of PTEF, PFA etc. as padded coaming at riveting portion by folder, then the sliding action in ball joint mechanisms portion 10 is extremely level and smooth.
In addition, refrigeration agent (R600a) is a hydrocarbon system, so also be combustible refrigerant.The pressure ratio barometric pressure of refrigeration cycle is also little, under any circumstance, if the gas that comes out from refrigeration cycle becomes the condition of leakage, then air is drawn in the refrigeration cycle.
On the other hand, there is the occasion of microtrauma in the coil portion that constitutes the stator 18 of motor part 4, discharges due to wound and electric arc takes place.Consequently, burning or blast may take place in the isobutane (R600a) as inflammable gas in refrigeration cycle.
In addition, as means, the coiling of distribution being arranged and concentrate coiling the coiling of stator 18 iron cores.Described distribution coiling is when coiling, and it is injured easily that coil is subjected to stress, and the coil of described concentrated coiling is not stressed, can be not injured.
Therefore,, after coiling finishes, electrical insulation is fixed on the coil, is subjected to the wound of stress generation with repairing in the occasion of coiling that distributes.Specifically be, behind the coil-winding, varnish be coated in coiler part as electrical insulation, be heating and curing then or normal temperature cure.
Therefore, even distribute coiling, in the refrigeration cycle that adopts combustible refrigerant-isobutane (R600a), also can eliminate the danger of burning or blast.In the occasion of concentrating coiling, because not being subjected to stress, coil do not hinder, therefore just use in statu quo.
Compression mechanical part 3 in the reciprocating seal type motor compressor shown in Figure 1, the description of equipment of cylinder 6 conducts independent (single cylinder), but being not limited thereto, also can be medianly zygomorphic a pair of (twin-tub) compression mechanical part that possesses in rotating shaft 5, and the whole original states of described qualifications are suitable for.
As described above, as adopting the present invention, not only effectively prevent depletion of the ozone layer, and can be applicable to that the use little effect arrives the refrigeration cycle to the refrigeration agent-isobutane (R600a) of global warmingization, reaches the effect that improves reliability.
Claims (7)
1. reciprocating seal type motor compressor, connecting rod is extended from the crank pin with integrated spindle axis, connect this connecting rod and the piston that is housed in the oil hydraulic cylinder by ball joint mechanisms portion, it is characterized in that, described ball joint mechanisms portion is located at ball on the interlinking lever end by one, be located on the described piston, embracing the ball bearing of described ball sliding freely forms, it is isobutane that the compressed object fluid is chosen as refrigeration agent, and the relation that acts on when the mean velocity V of described ball joint mechanisms portion and compression stroke between the load F of ball joint mechanisms portion is set at V * F＜200Nm/s.
2. reciprocating seal type motor compressor as claimed in claim 1 is characterized in that, the diameter d that constitutes the described ball of described ball joint mechanisms portion is set in below the 14.5mm.
3. reciprocating seal type motor compressor as claimed in claim 1 is characterized in that in the swing that described connecting rod carries out along with the eccentric motion of described connecting rod crank pin, the angle of oscillation of connecting rod is set in below 54 °.
4. the motor compressor of reciprocating seal type according to claim 1 is characterized in that, the speed setting of described main shaft is below 105rps.
5. reciprocating seal type motor compressor as claimed in claim 1 is characterized in that, the ball bearing that constitutes described ball joint mechanisms portion is implemented nitriding treatment and manganese phosphate is handled, or implement any processing wherein.
6. reciprocating seal type motor compressor as claimed in claim 1 is characterized in that, the material as the ball that constitutes described ball joint mechanisms portion adopts the high-carbon chromium steel that contains chromium (Cr) 0.5-2.0%.
7. reciprocating seal type motor compressor as claimed in claim 1 is characterized in that, constitutes between the ball and ball bearing of described ball joint mechanisms portion, is folded with the buffering ring of being made up of moldable resins such as PTFE, PFA.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002010435 | 2002-01-18 | ||
| JP2002010435A JP4021668B2 (en) | 2002-01-18 | 2002-01-18 | Reciprocating hermetic electric compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1434212A true CN1434212A (en) | 2003-08-06 |
| CN1231673C CN1231673C (en) | 2005-12-14 |
Family
ID=27648179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031027199A Expired - Fee Related CN1231673C (en) | 2002-01-18 | 2003-01-17 | Reciprocative sealing type electric compressor |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4021668B2 (en) |
| KR (1) | KR20030063155A (en) |
| CN (1) | CN1231673C (en) |
| TW (1) | TW571026B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100381701C (en) * | 2003-08-26 | 2008-04-16 | 松下电器产业株式会社 | Hermetic compressor |
| CN101397987B (en) * | 2005-08-03 | 2011-08-03 | 日立空调·家用电器株式会社 | Closed type compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4694956B2 (en) * | 2005-12-07 | 2011-06-08 | 日立アプライアンス株式会社 | Hermetic compressor |
-
2002
- 2002-01-18 JP JP2002010435A patent/JP4021668B2/en not_active Expired - Fee Related
- 2002-12-25 TW TW091137331A patent/TW571026B/en not_active IP Right Cessation
-
2003
- 2003-01-16 KR KR10-2003-0002920A patent/KR20030063155A/en active Search and Examination
- 2003-01-17 CN CNB031027199A patent/CN1231673C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100381701C (en) * | 2003-08-26 | 2008-04-16 | 松下电器产业株式会社 | Hermetic compressor |
| CN101397987B (en) * | 2005-08-03 | 2011-08-03 | 日立空调·家用电器株式会社 | Closed type compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2003214343A (en) | 2003-07-30 |
| TW571026B (en) | 2004-01-11 |
| TW200302318A (en) | 2003-08-01 |
| CN1231673C (en) | 2005-12-14 |
| JP4021668B2 (en) | 2007-12-12 |
| KR20030063155A (en) | 2003-07-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1133006C (en) | Vibration-type compressor | |
| CN1071417C (en) | Cyclone fluid machinery | |
| CN1102202C (en) | Valve assembly of compressor | |
| US6592347B2 (en) | Rotary compressor | |
| CN1789710A (en) | Hermetic compressor | |
| CN1806122A (en) | Hermetic compressor | |
| CN1042564C (en) | Electrically driven hermetic compressor | |
| CN1231673C (en) | Reciprocative sealing type electric compressor | |
| CN1081742C (en) | Single headed swash plate type compressor | |
| JP2018529041A (en) | Fluid machine, heat exchange device, and fluid machine operating method | |
| WO2010045767A1 (en) | A stationary vane type compressor | |
| US20040040412A1 (en) | Crank Shaft | |
| KR101333039B1 (en) | Straight-line motion type compressor | |
| CN200971863Y (en) | CO2 spherical expansion compressor | |
| CN1906414A (en) | Hermetic compressor | |
| CN1249388C (en) | Method for recovering refrigerant from air conditioner | |
| CN108194356B (en) | Pump body and compressor | |
| CN111894830A (en) | Single-stage reciprocating piston compressor for mixed refrigerant | |
| CN1701180A (en) | Hermetic compressor | |
| CN107339237A (en) | Rotary compressor | |
| JP2961623B2 (en) | Swash plate compressor | |
| CN212508831U (en) | Crankshaft thrust structure and compressor | |
| KR100488008B1 (en) | compressor | |
| CN1363777A (en) | Silencer of exhaust valve for sealed rotary compressor | |
| CN1766322A (en) | Damping device of reciprocating compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20051214 Termination date: 20180117 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |