CN104632635A - Sealed compressor - Google Patents
Sealed compressor Download PDFInfo
- Publication number
- CN104632635A CN104632635A CN201410049289.6A CN201410049289A CN104632635A CN 104632635 A CN104632635 A CN 104632635A CN 201410049289 A CN201410049289 A CN 201410049289A CN 104632635 A CN104632635 A CN 104632635A
- Authority
- CN
- China
- Prior art keywords
- gas
- bent axle
- separation chamber
- liquid separation
- hole
- 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
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
- F04B39/02—Lubrication
-
- 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
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
- F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
-
- 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
- F04B53/18—Lubricating
Abstract
Provided is a sealed compressor, wherein the refrigerant gas can be efficiently separated from the lubricating oil even with the presence of a fixed part and the compression function is improved. Therefore, the cooling performance of the refrigeration system is improved. Along with the rotation of a crankshaft (12), the function of a sticking pump (16a) is realized based on a hollow sleeve (19) and a fixed part (21), so that the lubricating oil (2) can be pumped. Meanwhile, inside a gas-liquid separation chamber (18) of a shaft (12), the gas and the liquid are separated. Meanwhile, the liquid is fed to a lubricating part through a through hole (17), and the volume of the gas-liquid separation chamber is increased.
Description
Technical field
The present invention relates to a kind of closed-type compressor carried in the refrigeration system of the household electrical appliances such as refrigerator or aircondition (air-conditioning) and the refrigerator being suitable for it.
Background technique
In household electrical appliances refrigeration system in recent years, the requirement of high efficiency uprises, for the closed-type compressor wherein carried, in order to realize high efficiency, be also useful in from lower than commercial power frequency low running frequency band to be more than or equal to commercial power frequency height running frequency band broad regions band domain the compressor of type that can operate.
But, in described closed-type compressor, in frequency field high efficiency being affected to low running frequency band, also exist in running for meeting the tendency guaranteeing to become difficulty of the oil supply of reliability and efficiency.The object of oil supply is guaranteed and the known techniques proposed, than if any the use by the high and low cost approach of simple and reliable property, even about 800min as in order to tackle this tendency
-1the low movement speed of degree also reliably can carry out " oil pump of closed-type compressor " (with reference to patent documentation 1) of oil circulation effectively, or, than if any the noise of not wishing to occur caused because of compressor operation that can not be produced by the Intermittent Contact between pump main body and supporting or fixing rod at a high rotational speed, in revolving ability, pump main body is pinned relative to the rotor of pump, by the freedom of movement on the radial direction rectangular with crankshaft, " erecting device of the oil pump of refrigeration compressor " (patent documentation 2) etc. of the inner side of the tubular sleeve of oil pump can be installed on one heart.
By the way, being configured to of the closed-type compressor of general refrigerator: there is compression key element and electronic key element, the viscosity pump being formed at bent axle bottom is utilized to carry out oil supply to slide part, specifically, first viscosity pumps such as the spiral chute formed between sleeve and fixed block are utilized to draw lubricant oil (oil), and it is flowed to the slide part of bent axle through the second viscosity pump, bearing portion is lubricated.Now, gas refrigerant contained for lubricant oil is separated by the blank part that the lubricant oil drawn is being arranged in crankshaft center portion, lubricant oil transfer is to feed bore, gas refrigerant is penetrated into the gas via-hole of piston side to the central part from bent axle by transferring, the blank part that what is called is positioned at crankshaft center portion becomes gas-liquid separation chamber.
Relative to this, in the closed-type compressor of above-mentioned patent documentation 1, adopt viscosity oil supply mechanism, namely, in the underpart of bent axle, sleeve is set, arrange by the parts of the trough of belt of bearing bracket (fixed block) at this sleeve internal fixtion, with the rotation of sleeve by viscosity pump effect, make the oil between the outer surface of the parts of trough of belt and the internal surface of sleeve increase.
In addition, in the refrigeration compressor of patent documentation 2, adopt viscosity oil supply mechanism, namely, arrange the pump main body supported by fixing rod in the inside of tubular sleeve, be provided with the spiral chute arranged at the internal surface of this tubular sleeve, pump main body makes lubricant oil rise along spiral chute by the rotation of tubular sleeve.
At first technical paper
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Application Publication 2002-No. 519589 publications
Patent documentation 2: Japanese Unexamined Patent Application Publication 2012-No. 505331 publications
In above-mentioned patent documentation 1 and patent documentation 2, be all the sleeve that the sticking lubricant oil of tool is rotated with the rotation by bent axle wall together with rotate, thus the spiral chute of lubricant oil along fixed block is drawn up, the lubricant oil drawn up is sent to main bearing side from the central part of bent axle by the feed bore be communicated with outer peripheral sidewall, afterwards, by the spiral chute of the periphery of bent axle, main bearing part is lubricated, but, if such structure, then owing to being provided with fixed block at the blank part being arranged in crankshaft center portion (at patent documentation 1 for oil draws parts, the pump main body of tubulose is equivalent to) in patent documentation 2, therefore the separation of refrigerant gas is insufficient, there are the misgivings causing cooling effect to decline.
Especially, be equipped with in the refrigerator of refrigeration system nearest, in order to power saving, use inverter driving circuit to control the rotating speed of closed-type compressor at 800 ~ 4300min
-1scope in, such as, when being accommodated with a large amount of food in the cabinet of refrigerator, or during the high temperature in summer, making compressor high-speed rotary then make to cool rapidly in cabinet.Due to High Rotation Speed now, after temperature in the cabinet is stable, the rotating speed of closed-type compressor is made to be 800min
-1low speed rotation, significantly power saving can be realized thus.
But, if make the rotating speed of closed-type compressor be the rotating speed 3600min higher than usual rotating speed
-1above rotating speed operates, then be aware of: the amount of drawing based on the lubricant oil of bent axle increases terrifically, lubricant oil flows to should only for the gas via-hole that refrigerant gas passes through, blocking gas via-hole, discharge invention at gas to have problems, sometimes also cannot carry out the supply of new lubricant oil.Especially High Rotation Speed 4300min is being carried out
-1when, produce the undersupply of lubricant oil, lubricant oil stream, less than bearing side, makes the problem that slide part damages.
When operating under such High Rotation Speed, if the closed-type compressor carried in the household electrical appliances refrigeration system of above-mentioned general refrigerator, even if then get the volume that is positioned at the blank part (gas-liquid separation chamber) in crankshaft center portion, if become the form of separation chamber volume, then lubricant oil also can overflow from separation chamber, lubricant oil flows to and only for the gas via-hole that refrigerant gas passes through, should produce the problems such as blocking gas via-hole thus.
In addition, in the structure of patent documentation 1, the mechanism suitable with separation chamber for the lubricant oil drawn to be sent oil to bent axle surface by feed bore is provided with on viscosity pump top, but as essential structure, the specification of gas-liquid separation chamber is indefinite, therefore there are the misgivings causing functionally obstacle like that shown below.Specifically, because the height dimension of bent axle inner space is indefinite, so when making the rotating ratio of compressor usually promote, it is unclear that the lubricant oil that viscosity pump can be drawn suitably is separated, the effect that can the burrock formed on the top of inner space reliably play gas-liquid separation is unclear, such as, when gas-liquid separation chamber becomes the state of lubricant oil spilling, burrock is completely inoperative, and then in this state, the refrigerant gas dissolved in lubricant oil cannot be made to get back to cooling purposes, therefore, when refrigeration agent dissolves in lubricant oil in a large number, produce the problem of lack of refrigerant, or refrigerant gas flows into bearing side, lubricant oil cut-off, produce the problem bringing damage to slide part.
Summary of the invention
The present invention proposes to solve such problem, its technical problem that will solve is, even if provide a kind of to possess fixed block, also refrigerant gas can be separated efficiently from lubricant oil, improve compression function, the closed-type compressor that the cooling performance that can contribute to refrigeration system improves and the refrigerator being suitable for this compressor.
In order to solve the problems of the technologies described above, the invention provides a kind of closed-type compressor, it possesses:
Bent axle, it is rotated by the main bearing supporting in the seal container of lubrication oil, and is provided with rotor in periphery;
Gas via-hole, it is located at this bent axle to be communicated with in described seal container with the mode of the internal diameter hollow portion of described bent axle;
Intercommunicating pore, it is located at bent axle in the mode of the inside diameter and internal diameter hollow portion that are communicated with main bearing;
The sleeve of hollow, it is pressed into the bottom of the internal diameter hollow portion in bent axle; And
The fixed block of concaveconvex shape, it is installed in sleeve in the mode with gap, and surface is helical,
By the viscosity pump effect realized by sleeve and fixed block of the rotation with bent axle, draw lubricant oil, and the gas that becoming in the gas-liquid separation chamber of oil separation space in internal diameter hollow portion is separated into liquid and comprises vaporific state, this liquid is supplied to slide part by intercommunicating pore, and this gas is supplied to compression key element by gas via-hole
It is characterized in that,
The upper-end part of driving of fixed block between the rising wood and the underpart of intercommunicating pore of sleeve,
Gas-liquid separation chamber is configured to capacity increasing, makes not overflow to gas via-hole side with being stored in this indoor lubricant oil by viscosity pump effect to drawing of lubricant oil, and utilizes burrock suppression this gas via-hole side of flow direction in indoor setting.
Invention effect
According to closed-type compressor of the present invention, according to said structure, fully guarantee the volume of gas-liquid separation chamber, even if compressor rotary speed is high, also can by the burrock of gas-liquid separation chamber reliably suppress from lubricating oil be separated flow direction gas via-hole side, therefore effectively can carry out liquid and being separated of gas comprising vaporific state to lubricant oil, there will not be the lubricant oil drawn not flow to bearing side and the situation that slide part is damaged, compressed action can be carried out sleekly.
Accompanying drawing explanation
Fig. 1 represents the essential structure of the closed-type compressor of embodiments of the invention 1 to expose inner figure in longitudinal partly cut-away.
The major component of Fig. 1 is amplified and the figure that represents of partly cut-away by Fig. 2.
Fig. 3 is the stereogram of the thin portion structure of the viscosity pump that Watch with magnifier diagram 2 comprises.
Fig. 4 is in order to the viscosity pump shown in explanatory drawing 3 and support unit thereof the stereogram represented that makes electronic key element become topsy-turvydom relative to the assembled configuration of electronic key element and compression key element.
Fig. 5 is under the state being connected to electric coupler taking off support spring, represents the stereogram of the support unit of the viscosity pump the assembled configuration shown in Fig. 4 and the configuration relation of insulator from other direction.
Fig. 6 be in order to when the viscosity pump in explanatory drawing 2 and sleeve are installed in bent axle, the lower end of viscosity pump is relative to the relation of the extrusion position of sleeve lower end and figure major component partly cut-away represented.
Embodiment
Below, for closed-type compressor of the present invention, enumerate embodiment, describe in detail with reference to accompanying drawing.
[embodiment 1]
Fig. 1 represents the essential structure of the closed-type compressor of embodiments of the invention 1 to expose inner figure in longitudinal partly cut-away.The major component of Fig. 1 is amplified and the figure that represents of partly cut-away by Fig. 2.This closed-type compressor possesses compression key element 4 and the electronic key element 13 of inverter drive in seal container 1, and compression key element 4 comprises: lubrication oil (oil) 2 and be filled with the framework 7 of refrigeration agent 3, in addition formation clutch release slave cylinder 5; Back and forth be embedded in the piston 6 in clutch release slave cylinder 5 freely; The bent axle 12 etc. be made up of the main shaft part 9 of main bearing 8 and core shift portion 10 that are supported on framework 7 by axle, the electronic key element 13 of inverter drive by the stator 14 be connected with not shown inverter driving circuit and built-in not shown permanent magnet and the rotor 15 being fixed in main shaft part 9 form, and be fixed on the below of framework 7.
Wherein, core shift portion 10 has the connecting rod 11 linking piston 6, and compression key element 4 is resiliently supported in seal container 1 across stator 14 by support spring 20, thus forms shuttle compressing mechanism.Electronic key element 13 passes through inverter driving circuit, at least to comprise rotating speed 700min
-1driven at interior multiple operating frequencys.The main shaft part 9 of bent axle 12 is formed the first viscosity pump 16a and the second viscosity pump 16b be connected with the first viscosity pump 16a through intercommunicating pore 17, and lubricant oil 2 is supplied to each several parts such as main bearing 8, piston 6, clutch release slave cylinders 5.
Below, with reference to Fig. 2, on bent axle 12, gas via-hole 29 is provided with to make the mode be communicated with the internal diameter hollow portion of bent axle 12 in seal container 1, and be provided with intercommunicating pore 17 in the mode making the inside diameter of main bearing 8 be communicated with internal diameter hollow portion, at the sleeve 19 of the bottom of the internal diameter hollow portion of bent axle 12 press-in hollow, sleeve 19 in the mode with gap be provided with by be formed as spiral helicine boss part 23 and spiral chute around 25 (also can be called that first to oil groove 26) thereof and surperficial be the fixed block 21 of spiral helicine concaveconvex shape.At this, by rotating the viscosity pump effect of the first viscosity pump 16a realized based on sleeve 19 and fixed block 21 together with bent axle 12, draw lubricant oil 2, in the internal diameter hollow portion of bent axle 12 as being separated into liquid in the gas-liquid separation chamber 18 of oil separation space and containing the gas (gas of refrigeration agent 3) of vaporific state, liquid is supplied to slide part by intercommunicating pore 17, and gas is supplied to compression key element 4 by gas via-hole 29.
Gas-liquid separation chamber 18 is configured to: capacity increasing, make drawing of the lubricant oil 2 carried out than the viscosity pump effect of the first viscosity pump 16a when fast time usual with compressor rotary speed, do not overflow to gas via-hole 29 side from the liquid being stored in indoor lubricant oil 2 separation, and, utilize and be located at indoor burrock 33 (specifically, the large burrock 33a of below, the little burrock 33b of top), block and suppress flow direction gas via-hole 29 side.Gas via-hole 29 by separated via the burrock 33 formed on the top of gas-liquid separation chamber 18 and flowing gas in seal container 1 compression key element 4 side supply.The bottom that liquid is supplied to the gas-liquid separation chamber 18 in the internal diameter hollow portion of bent axle 12 by intercommunicating pore 17 is arranged and the second the second viscosity pump 16b realized to oil groove 30 arranged at the outer circumferential side of bent axle 12.Feed bore 28 is the paths flowed into for the liquid drawn by the second viscosity pump 16b, and the liquid that have passed feed bore 28 is directed onto the top of compression key element 4 from the hole in core shift portion 10.By the way, at the waste material of junk trap groove 27 for trapping by spiral chute 25 in the lubricant oil 2 of oil supply that the way meta of the spiral chute 25 being located at fixed block 21 installs.The rising wood in cover letter 19 in gas-liquid separation chamber 18 and the interference part 18a formed between the underpart of intercommunicating pore 17 have the effect reducing the decompression of pressure between the first viscosity pump 16a and gas-liquid separation chamber 18.
Below, the relation of the first viscosity pump 16a and the second viscosity pump 16b is described.First viscosity pump 16a comprises: the gas-liquid separation chamber 18 formed in bent axle 12 bottom and sleeve 19, the fixed block 21 be inserted on coaxial with the axle center of bent axle 12, the travelling support unit 22 (being described in detail later) etc. retrained at sense of rotation and above-below direction to this fixed block 21.At this, support unit 22 is inserted into two ends and is installed in the support (insulator 32 in Fig. 4 described later, support 32a) of the insulator of stator 14, the substantial middle part of support unit 22 is applied in the through hole 24 of jut 34 setting of the end of fixed block 21, and within it wall is locked.
The mounting point of this fixed block 21, in order to be communicated with the gas-liquid separation chamber 18 and main bearing 8 that are formed by the internal diameter hollow portion of bent axle 12, is in the position that the intercommunicating pore 17 that do not arrange with the sidewall at bent axle 12 overlaps.If be in the position of coincidence, then the boss part 23 being used for being formed spiral chute 25 of intercommunicating pore 17 fixture 21 is inaccessible, that is, bent axle 12 rotates at every turn, and the boss part 23 of intercommunicating pore 17 fixture 21 is inaccessible.
Sleeve 19 is general cylindrical shape, presents the hat shape shape of lower aperture, and is formed by the metallic material easily realizing degree of precision.Such as, in contrast, fixed block 21 can be illustrated by the low plastic materials of thermal conductivity with resistance to refrigeration agent, lubricating oil resistance, the situation that PPS, PBT, PEEK etc. are formed.The spiral chute 25 being located at the periphery of fixed block 21 is formed in the first viscosity pump 16a of the lubricant oil 2 that to circulate between itself and sleeve 19.It should be noted that, main bearing 8 or be fixed at framework 7, or be integrally formed with framework 7 and fix.The section shape formed at the outer surface of main shaft part 9 trapezoidal second forms the second viscosity pump 16b to oil groove 30.
Below, the oil supply action of the closed-type compressor of described structure is described.When being energized to electronic key element 13, rotor 15 rotates, and is accompanied by this, and bent axle 12 rotates, and compression key element 4 carries out the compressed action specified.By the rotation of bent axle 12, sleeve 19 also rotates, and thus, stir lubricant oil 2, it is drawn by the first viscosity pump 16a.The lubricant oil 2 drawn, using the intercommunicating pore 17 of bent axle 12 as transition point, circulates to oil groove 30 as second of the second viscosity pump 16b, is lubricated from the top etc. of hole to compression key element 4 in core shift portion 10 by main bearing 8, feed bore 28.Now, utilize the junk trap groove 27 arranged at the middle part of the spiral chute 25 being located at fixed block 21, trap the waste material in the lubricant oil 2 be supplied to by spiral chute 25.
For the structure of the first viscosity pump 16a, be formed with gas-liquid separation chamber 18 at the internal diameter hollow portion of bent axle 12, in the below of this gas-liquid separation chamber 18 by being pressed into bent axle 12 and being provided with sleeve 19, its intrusion normally about 5mm.At this, the lubricant oil 2 risen in spiral chute 25 runs into junk trap groove 27 in rotation way, but usually enter weight ratio lubricant oil 2 weight of the waste material in lubricant oil 2, therefore, waste material acts on stronger centrifugal force, waste material while with sleeve 19 in connect while rise, in rising way, enter junk trap groove 27 and be detained.So, lubricant oil 2 is purified.
The intercommunicating pore 17 being located at bent axle 12 functions as follows: make formed by the spiral chute 25 being located at fixed block 21 periphery first to the first viscosity pump 16a of realizing of oil groove 26 in the lubricant oil 2 that rises move to the second the second viscosity pump 16b side realized to oil groove 30 being located at bent axle 12 outer surface side.In addition, the gas being brought into the refrigeration agent 3 of the vaporific state containing lubricant oil 2 of gas-liquid separation chamber 18 by the spiral chute 25 etc. of fixed block 21 is blown to piston 6, clutch release slave cylinder 5 etc., for lubrication and the cooling of these each several parts by being located at the gas via-hole 29 of bent axle 12.And then the lubricant oil 2 risen in the second the second viscosity pump 16b realizing to oil groove 30, after have lubricated main bearing 8, is blown the top to compression key element 4, for lubrication and the cooling of each several parts such as piston 6, clutch release slave cylinder 5 through feed bore 28.
But, as mentioned above, if the boss part 23 of intercommunicating pore 17 fixture 21 of bent axle 21 blocks, the delivery volume of the lubricant oil 2 then supplied to the slide part of main bearing 8 reduces, or if the axial dimension of the bent axle 12 of fixed block 21 is long, then correspondingly, gas-liquid separation chamber 18 size in the same direction shortens, volume reduces, the problem that the gas separation effect producing refrigeration agent 3 declines.
Therefore, in the present invention, various research is carried out to the delivery volume of the delivery volume of the lubricant oil 2 of the first viscosity pump 16a and the gas of refrigeration agent 3, found that, if improve the structure of fixed block 21 and bent axle 12, then increase the volume of gas-liquid separation chamber 18, improve gas-liquid separating function, described problem can be solved.
Below, with reference to Fig. 3 ~ Fig. 6, its improvement measure is specifically described.Wherein, Fig. 3 is the stereogram of the thin portion structure of the first viscosity pump 16a that Watch with magnifier diagram 2 comprises.Fig. 4 is in order to the first viscosity pump 16a shown in explanatory drawing 3 and support unit 22 thereof the stereogram represented that makes electronic key element 13 become topsy-turvydom relative to the assembled configuration of electronic key element 13 and compression key element 4.Fig. 5 is under the state being connected to electric coupler 32b taking off support spring 20, represents the support unit 22 of the first viscosity pump 16a the assembled configuration shown in Fig. 4 and the stereogram of the configuration relation of insulator 32 from other direction.Fig. 6 be in order to when the first viscosity pump 16a in explanatory drawing 2 and cover letter 19 are installed in bent axle 12, the first viscosity pump 16a lower end relative to the relation of the extrusion position (outstanding size H) of sleeve lower end 19a figure that major component partly cut-away is represented.
First, with reference to Fig. 3, as illustrated in fig. 2, in the periphery of fixed block 21 around spiral helicine boss part 23 formation spiral chute 25, form the first the first viscosity pump 16a realized to oil groove 26 of this spiral chute 25.In addition, be provided with through hole 24 at the jut 34 of the front end of fixed block 21, the substantial middle part of support unit 22 runs through this through hole 24 and is locked.At this, fixed block 21, comprises jut 34, boss part 23, spiral chute 25, one-body molded by resin.By the way, sleeve 19 is pressed into fixed in bent axle 12, and fixed block 21 is given prominence to by support unit 22 etc. in the mode can not encountering the sleeve 19 of rotation on above-below direction and sense of rotation.Such as, with reference to Fig. 6, first viscosity pump 16a (fixed block 21) the lower end extrusion position outstanding relative to sleeve lower end 19a (outstanding size H) ensures before and after 1.0mm, even if fixed block 21 is before and after the axially movable 1.0mm of sleeve 19, fixed block 21 also can not encounter sleeve 19, bent axle 12.Thus, the position of the fixed block 21 shown in Fig. 2 compared by the fixed block 21 shown in Fig. 6, becomes the state moved slightly toward below.
In addition, as shown in Figure 6, by configuring the upper end portion of fixed block 21 between the rising wood and the underpart of intercommunicating pore 17 of sleeve 19, thus intercommunicating pore 17 and fixed block 21 become nonoverlapping position relationship in the height direction.This is because, if intercommunicating pore 17 is in overlapping position relationship in the height direction with fixed block 21, then when bent axle 12 rotates, size between the boss part 23 becoming the external diameter of spiral chute 25 of fixed block 21 and the entrance of intercommunicating pore 17 reduces, there are the misgivings that lubricant oil 2 is difficult to flow, flow reduces, or when fixed block 21 tilts, there are the misgivings being blocked intercommunicating pore 17 by boss part 23.Therefore, make the upper-end part of driving of fixed block 21 in the below of the underpart of intercommunicating pore 17, intercommunicating pore 17 and fixed block 21 become nonoverlapping position relationship in the height direction.
That is, in the first viscosity pump 16a, the upper end portion of fixed block 21 is given prominence to more upward than the rising wood of sleeve 19, and is positioned at the below of the underpart of intercommunicating pore 17.In addition, the internal diameter of gas-liquid separation chamber 18 is greater than the internal diameter of sleeve 19.With the rotation of bent axle 12 and sleeve 19, rise between the inner peripheral surface of the sleeve 19 of lubricant oil 2 in the first viscosity pump 16a and the outer surface of fixed block 21.Thus, even when low speed rotation and centrifugal force decline, also can adhesively draw lubricant oil 2, even if also can conveying be stablized when low speed rotation.
And then the lubricant oil 2 that the upper end comparing sleeve 19 rises further is released to the interference part 18a formed between the upper end portion of sleeve 19 and the underpart of intercommunicating pore 17.This interference part 18a be the outer surface of the diameter (when the structure of Fig. 6, and the equal diameters of the inner peripheral surface of the cylinder hollow portion of bent axle 12) of inner peripheral surface by making gas-liquid separation chamber 18 and the boss part 23 of fixed block 21 diameter between size be greater than the outer surface of the diameter of the inner peripheral surface of sleeve 19 and the boss part of fixed block 21 diameter between size formed.It should be noted that, even if the other structure when diameter of the inner peripheral surface of gas-liquid separation chamber 18 is greater than the diameter of the inner peripheral surface of the cylinder hollow portion of bent axle 12, the diameter of the inner peripheral surface of sleeve 19 is less than the diameter of the inner peripheral surface of gas-liquid separation chamber 18 (now, the relation of the diameter of the diameter of the inner peripheral surface of the cylinder hollow portion of bent axle 12 and the inner peripheral surface of sleeve 19 is not prescribed), also can form interference part 18a equally.
Therefore, when the lubricant oil 2 risen in the first viscosity pump 16a is released the gas-liquid separation chamber 18 of the low pressure to opening from the first viscosity pump 16a of high pressure, pressure sharply declines, although there is lubricant oil 2 be not separated into liquids and gases in gas-liquid separation chamber 18 and flow to the misgivings of gas via-hole 29 side, play the effect reducing pressure between the first viscosity pump 16a and gas-liquid separation chamber 18 at this interference part 18a.By the way, the size putting on the pressure of lubricant oil 2 has the relation of the first viscosity pump 16 a> interference part 18a> gas-liquid separation chamber 18.Thus, even when transferring lubricant oil 2 to draw with sudden force with high-speed rotary, also pressure can be made to reduce gradually by interference part 18a, can stablize in gas-liquid separation chamber 18 and be separated into liquids and gases.By the way, interference part 18a in above-mentioned structure in addition has just flowed to position before intercommunicating pore 17 owing to being positioned at lubricant oil 2, so lubricant oil 2 is smooth and easy to the inflow change of intercommunicating pore 17, and the gas-liquid separation chamber 18 on the top being positioned at intercommunicating pore 17 becomes stepped part, so except decompression, also there is the effect suppressing lubricant oil 2 to flow to gas via-hole 29.
In addition, the position with reference to Fig. 1, sleeve lower end 19a and fixed block 21 lower end is configured to: imagination has shock and vibration apply or put upside down, even if also do not contact with the end of seal container 1 in this case.Also there is the position of 3 ~ 4mm the central position of the through hole 24 that the support unit 22 of supporting holder 21 is arranged apart from sleeve lower end 19a.It should be noted that, if such size, then for support unit 22, preferably use outside dimension is the wire rod of the scope of 1.0 ~ 2.0mm.And then, about the pickup of the pasta relative to lubricant oil 2 of the sleeve 19 shown in Fig. 1, preset initial impregnation amount, even if under making also to be immersed in pasta when the maximum reduction of pasta.
Below, with reference to Fig. 4, electronic key element 13 is described above, by the stator 14 be connected with inverter driving circuit and built-in permanent magnet and the rotor 15 being fixed in bent axle 12 form, winding 31 is installed between stator 14 and rotor 15.This winding 31 is fixed in stator 14 through insulator 32.Be pressed into bent axle 12 at rotor 15, the sleeve 19 and the fixed block 21 that are installed on this bent axle 12 front end are given prominence to from rotor 15.In addition, in the through hole 24 of the jut 34 of fixed block 21 front end, support unit 22 is inserted.The two end part of support unit 22 are the roughly U-shaped portion 22a being flexed into roughly U-shaped, in the hole of support 32a being located at insulator 32, insert roughly U-shaped portion 22a.This support 32a is integrally formed at resinous insulator 32.The support spring 20 installed respectively in four bights of stator 14 is by the component of compression key element 4 yielding support in seal container 1 through stator 14.
At this, insulator 32 is substantially cylindrical shape, within one week, is formed with winding 31 around cylindrical part.In a part for this winding 31, as shown in Figure 5, stretch out and be provided with electric coupler 32b.At the periphery of this electric coupler 32b, the transition wire support 32c connected between winding 31 is integrally formed at a part for insulator 32.In addition, avoiding the position of this transition wire support 32c, with insulator 32 be integrally formed with cover winding 31 erect wall 32d.By the way, the support 32a that is located at insulator 32 is located at and avoids electric coupler 32b with transition wire support 32c and be connected the position erecting wall 32d in the diagonal direction.
In described structure, mounting point due to support unit 22 is in the position that can not become obstacle avoiding electric coupler 32b and transition wire support 32c, therefore, the support unit 22 vibrated because compressor rotates is avoided to contact with winding 31, even if Long-Time Service compressor, also can not damage the coil forming winding 31, prevent broken string.
And then, with reference to Fig. 2, for the gas-liquid separation chamber 18 formed on the first viscosity pump 16a top and be described in the function of the burrock 33 (large burrock 33a, little burrock 33b) of this indoor setting.
Gas-liquid separation chamber 18 is formed at the top of top, the i.e. first viscosity pump 16a of cylinder hollow portion bent axle 12 reaming formed, for the lubricant oil 2 of the gas-liquid mixture fluid drawn by the first viscosity pump 16a being separated into the gas and liquid that comprise vaporific state, play and liquid is sent to the second viscosity pump 16b side by intercommunicating pore 17, and gas is sent to the effect of compression key element 4 side by gas via-hole 29.
In gas-liquid separation chamber in the closed-type compressor of existing structure, because volume is little, do not consider in a variable manner at 700 ~ 4800min
-1scope internal control compressor rotary speed, therefore, even have the structure of burrock, can not say and be applied flexibly in gas-liquid separation, not consider the countermeasure buried by liquid than gas via-hole 29 usually fast at compressor rotary speed.Namely, the gas-liquid separation chamber of existing structure, due at the height dimension axially of bent axle 12 be embodiment 1 gas-liquid separation chamber 18 height dimension situation about 1/3, therefore, at compressor rotary speed than usually fast, gas-liquid separation chamber inevitable lubricated oily 2 is full of, and is buried the midway part of gas via-hole 29 by the lubricant oil 2 of gas-liquid mixture phase.Now, the interior voltage rise of gas-liquid separation indoor is high, obstruction draws lubricant oil 2, the oil supply performance of viscosity pump significantly declines, not only to the slide part of bent axle 12 and the oil supply hydraulic performance decline of compression key element 4 side supply, and due to the gas of the refrigeration agent 3 in lubricant oil 2 not separated, so slide part greasy property worsen, sliding function is also deteriorated.As a result, at compressor rotary speed than usually fast, not talkative gas-liquid separation chamber can give full play to its effect.
In contrast, the size of the gas-liquid separation chamber 18 of the closed-type compressor of embodiment 1 is configured to: with at compressor rotary speed than usually fast 700 above-mentioned ~ 4800min
-1scope when the drawing of lubricant oil 2, having the liquid being stored in indoor lubricant oil 2 can not from the volume of gas via-hole 29 spilling, therefore, can not by lubricant oil 2 landfill of gas or air inclusion, interior pressure improves and damages the oil supply effect of the first viscosity pump 16a due to indoor, and to be blocked by the burrock 33 arranged on indoor top and to suppress the liquid of lubricant oil 2 to move to gas via-hole 29 effluent, therefore, the structure that gas-liquid separating function improves is become.
And then with reference to Fig. 2, burrock 33 utilizes the auxiliary section of the sidewall in gas-liquid separation chamber 18 and the sky borehole wall to be formed, and is located at the upper side of gas-liquid separation chamber 18, and is connected with gas via-hole 29.Specifically, for the auxiliary section of the sky borehole wall utilized in gas-liquid separation chamber 18 and sidewall and angle between the wall of the large burrock 33a formed, little burrock 33b, each illustrate the situation of 120 degree.In addition, large burrock 33a intactly utilizes the diameter of the axis relative to bent axle 12 of gas-liquid separation chamber 18 main body and is formed, the diameter of little burrock 33b is narrower than the diameter of gas-liquid separation chamber 18 main body but be greater than the diameter of gas via-hole 29, and little burrock 33b utilizes the path be connected with gas via-hole 29 to be formed.It should be noted that, between the wall that this is formed needed for burrock 33, angle is except 120 degree, such as, also can illustrate with the situation of the formation such as less than 90 degree, 91 degree, 150 degree, can consider the geomery of gas-liquid separation chamber 18 main body and suitably set.
At the first above-mentioned viscosity pump 16a in the drawing of lubricant oil 2, liberated in the constraint of a part for the lubricant oil 2 of the spiral chute 25 fore-telling rising of fixed block 21 with the rotation of cover letter 19, gas-liquid separation chamber 18 is arrived via interference part 18a, the gas of refrigeration agent 3 is separated in gas-liquid separation chamber 18, by intercommunicating pore 17, liquid is sent to the second viscosity pump 16b side, and the gas of refrigeration agent 3 of releasing in gas-liquid separation chamber 18 because of density difference in indoor rising and towards gas via-hole 29 side.Now, for be sent to intercommunicating pore 17 and in gas-liquid separation chamber 18 accumulation lubricant oil 2 rise at sidewall due to the effect of centrifugal force, arrive the sky borehole wall and coordinate the large burrock 33a formed, little burrock 33b with sidewall, collide with each wall of described large burrock 33a, little burrock 33b, block liquid and move to gas via-hole 29 effluent.
By the way, for the closed-type compressor of embodiment 1, as mentioned above, although sleeve 19 is formed by the metal etc. that thermal distortion is less, fixed block 21 is by plastic materials, and such as PPS, PBT, PKEK etc. carry out the component of die forming.In embodiment 1, its large feature is, combine metal sleeve 19 and resinous fixed block 21, be different from and all be preferably resinous aim at patent documentation 1 or patent documentation 2 middle sleeve and fixed block, at least for sleeve 19 needs its be metal.Its reason is, because under sleeve 19 is peucinous situation, to be pressed into sleeve 19 by force in metal bent axle 12, then there is the possibility of sleeve 19 breakage, as each the present embodiment, if sleeve 19 is metal, then easily can be pressed into relative to bent axle 12.
In addition, when die forming fixed block 21, according to the closing method of peel of mould, sometimes produce overlap at spiral chute 25, the obstacle that this overlap will become lubricant oil 2 and flows.Therefore, need to improve the making method of fixed block 21 or the die-closed position of peel of mould, do not make to produce overlap at spiral chute 25.By not producing overlap, can make productivity and the extremely beneficial fixed block 21 of cost.
In any case, according to the closed-type compressor of embodiment 1, the viscosity pump effect of the first viscosity pump 16a realized by sleeve 19 and the fixed block 21 of the rotation with bent axle 12, draw lubricant oil 2, gas-liquid separation chamber 18 in the internal diameter hollow portion of axle 12 is separated into liquid and comprises the gas (gas of refrigeration agent 3) of vaporific state, liquid is supplied to slide part by intercommunicating pore 17, and gas is supplied to the top of compression key element 4 by gas via-hole 29, in gas-liquid separation chamber 18, now form the structure of enlarging volume, make to draw lubricant oil 2 with by compressor rotary speed than the viscosity pump effect of the first viscosity pump 16a when fast time usual, the liquid being stored in indoor lubricant oil 2 can not overflow to gas via-hole 29 side, and utilize burrock 33 (the large burrock 33a arranged on the top of indoor, little burrock 33b), block and suppress the liquid of lubricant oil 2 to move to gas via-hole 29 effluent.
Namely, in the closed-type compressor of embodiment 1, fully guarantee the volume of gas-liquid separation chamber 18, even if compressor rotary speed is high, also lubricant oil 2 suitably can be suppressed to flow out from gas via-hole 29 by the burrock 33 (large burrock 33a, little burrock 33b) of gas-liquid separation chamber 18, therefore, liquid and being separated of gas comprising vaporific state are carried out effectively to lubricant oil 2, there will not be the lubricant oil 2 drawn not flow to bearing (main bearing 8) side and the situation that slide part is damaged.Consequently, even if possess fixed block 21, also refrigerant gas can be separated efficiently from lubricant oil 2, when High Rotation Speed, lubricant in compressor 2 and refrigeration agent 3 gas be separated also stabilization, compressed action carries out sleekly, and therefore the cooling performance of refrigeration system improves, if described refrigeration system is applicable to refrigerator, then can contribute to the raising of cooling performance and reliability.
By the way, when the refrigeration system comprising such closed-type compressor is equipped on refrigerator, such as, directly can be suitable for the structure illustrated by Fig. 7 of Japanese Unexamined Patent Publication 2013-No. 68112 publications, therefore omit at this and describe in detail.
It should be noted that, for the gas-liquid separation chamber 18 of the closed-type compressor of embodiment 1, comprise in being configured in of burrock 33, consider that the viscosity ratio water of the liquid of lubricant oil 2 is high, as long as the function of flow direction gas via-hole 29 side preventing lubricant oil 2 can be had, then can also be suitable for the structure of other forms.Such as, except burrock being connected to the path of gas via-hole 29, can also be illustrated in the situation etc. formed in gas-liquid separation chamber 18 main body, closed-type compressor of the present invention is not limited to form disclosed in embodiment 1.
Symbol description
1 seal container
2 lubricant oil (oil)
3 refrigeration agents
4 compression key elements
5 clutch release slave cylinders
6 pistons
7 frameworks
8 main bearings
9 main shaft part
10 core shift portions
11 connecting rods
12 bent axles
12a lower front end portion
13 electronic key elements
14 stators
15 rotors
16 first viscosity pumps
16b second viscosity pump
17 intercommunicating pores
18 gas-liquid separation chamber
19 sleeves
20 support springs
21,21a ~ 21c fixed block
22 support units
22a is U-shaped portion roughly
23 boss part
24,24a ~ 24c through hole
25 spiral chutes
26 first give oil groove
27 junk box
28 feed bore
29 gas via-holes
30 second give oil groove
33 burrocks
The large burrock of 33a
The little burrock of 33b
34,34a ~ 34b jut.
Claims (5)
1. a closed-type compressor, it possesses:
Bent axle, it is rotated by the main bearing supporting in the seal container of lubrication oil, and is provided with rotor in periphery;
Gas via-hole, it is located at this bent axle to be communicated with in described seal container with the mode of the internal diameter hollow portion of described bent axle;
Intercommunicating pore, it is located at described bent axle in the mode of the inside diameter and described internal diameter hollow portion that are communicated with described main bearing;
The sleeve of hollow, it is pressed into the bottom of the described internal diameter hollow portion in described bent axle; And
The fixed block of concaveconvex shape, it is installed in described sleeve in the mode with gap, and surface is helical,
By the viscosity pump effect realized by described sleeve and described fixed block of the rotation with described bent axle, draw described lubricant oil, and the gas that becoming in the gas-liquid separation chamber of oil separation space in described internal diameter hollow portion is separated into liquid and comprises vaporific state, this liquid is supplied to slide part by described intercommunicating pore, and this gas is supplied to compression key element by described gas via-hole
It is characterized in that,
The upper-end part of driving of described fixed block between the rising wood and the underpart of described intercommunicating pore of described sleeve,
Described gas-liquid separation chamber is configured to capacity increasing, make not overflow to described gas via-hole side with being stored in this indoor lubricant oil by described viscosity pump effect to described drawing of lubricant oil, and utilization suppresses this gas via-hole side of described flow direction at the burrock of indoor setting.
2. closed-type compressor as claimed in claim 1, is characterized in that,
Described compressor rotary speed is controlled at 700 ~ 4800min by inverter driving circuit
-1scope.
3. closed-type compressor as claimed in claim 1, is characterized in that,
Described burrock utilizes the auxiliary section of the sidewall in described gas-liquid separation chamber and the sky borehole wall to be formed, and described burrock is located at the upper side of this gas-liquid separation chamber, and is connected with described gas via-hole.
4. closed-type compressor as claimed in claim 1, is characterized in that,
Described intercommunicating pore is provided at the bottom of described gas-liquid separation chamber and supplies the hole of described liquid to another viscosity pump of the outer circumferential side being located at described bent axle,
Described gas via-hole is the hole supplied from the top of described gas-liquid separation chamber to the compression key element side in described seal container by described gas.
5. a refrigerator, is characterized in that, it possesses the refrigeration system of the closed-type compressor be equipped with according to any one of Claims 1-4.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-232111 | 2013-11-08 | ||
| JP2013232111A JP6190698B2 (en) | 2013-11-08 | 2013-11-08 | Hermetic compressor and refrigerator using the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104632635A true CN104632635A (en) | 2015-05-20 |
| CN104632635B CN104632635B (en) | 2017-09-22 |
Family
ID=53196817
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410049289.6A Active CN104632635B (en) | 2013-11-08 | 2014-02-12 | Closed-type compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6190698B2 (en) |
| KR (1) | KR20150053678A (en) |
| CN (1) | CN104632635B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110998093A (en) * | 2017-07-19 | 2020-04-10 | 三星电子株式会社 | Closed compressor |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106837745B (en) * | 2017-02-17 | 2019-12-20 | 安徽美芝制冷设备有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| CN107559167A (en) * | 2017-09-01 | 2018-01-09 | 江苏江大泵业制造有限公司 | From flowing forced air cooling high-temperature pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0728946A1 (en) * | 1995-02-23 | 1996-08-28 | Zanussi Elettrodomestici S.p.A. | Improvement in the lubricating system for a hermetically sealed reciprocating compressor |
| CN1455092A (en) * | 2002-04-29 | 2003-11-12 | 乐金电子(天津)电器有限公司 | Oil pumping apparatus of closed compressor |
| CN1455100A (en) * | 2002-04-29 | 2003-11-12 | 乐金电子(天津)电器有限公司 | Oil supply structure of closed compressor |
| CN1701182A (en) * | 2003-03-14 | 2005-11-23 | 松下电器产业株式会社 | Compressor |
| CN101657639A (en) * | 2006-10-31 | 2010-02-24 | 惠而浦股份有限公司 | The oil pump that is used for refrigeration compressor |
| JP2012180796A (en) * | 2011-03-02 | 2012-09-20 | Panasonic Corp | Hermetic compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61265379A (en) * | 1985-05-16 | 1986-11-25 | Mitsubishi Electric Corp | Scroll compressor |
| KR100679130B1 (en) * | 2003-03-14 | 2007-02-07 | 마쯔시다덴기산교 가부시키가이샤 | Compressor |
| JP2013064561A (en) * | 2011-09-20 | 2013-04-11 | Hitachi Appliances Inc | Refrigerator |
-
2013
- 2013-11-08 JP JP2013232111A patent/JP6190698B2/en active Active
-
2014
- 2014-02-03 KR KR1020140011982A patent/KR20150053678A/en active Search and Examination
- 2014-02-12 CN CN201410049289.6A patent/CN104632635B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0728946A1 (en) * | 1995-02-23 | 1996-08-28 | Zanussi Elettrodomestici S.p.A. | Improvement in the lubricating system for a hermetically sealed reciprocating compressor |
| CN1455092A (en) * | 2002-04-29 | 2003-11-12 | 乐金电子(天津)电器有限公司 | Oil pumping apparatus of closed compressor |
| CN1455100A (en) * | 2002-04-29 | 2003-11-12 | 乐金电子(天津)电器有限公司 | Oil supply structure of closed compressor |
| CN1701182A (en) * | 2003-03-14 | 2005-11-23 | 松下电器产业株式会社 | Compressor |
| CN101657639A (en) * | 2006-10-31 | 2010-02-24 | 惠而浦股份有限公司 | The oil pump that is used for refrigeration compressor |
| JP2012180796A (en) * | 2011-03-02 | 2012-09-20 | Panasonic Corp | Hermetic compressor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110998093A (en) * | 2017-07-19 | 2020-04-10 | 三星电子株式会社 | Closed compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20150053678A (en) | 2015-05-18 |
| JP2015094223A (en) | 2015-05-18 |
| CN104632635B (en) | 2017-09-22 |
| JP6190698B2 (en) | 2017-08-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102076966B (en) | Compressor | |
| JP6541872B2 (en) | Scroll compressor and refrigeration cycle apparatus | |
| JP6970506B2 (en) | Variable speed cooling compressor including lubricating oil pump system | |
| JP5716161B2 (en) | Hermetic compressor | |
| KR20090085665A (en) | Motor and compressor | |
| CN103375385A (en) | Hermetic reciprocating compressor | |
| CN104632635A (en) | Sealed compressor | |
| WO2017168672A1 (en) | Scroll compressor and refrigeration cycle device | |
| CN104632580B (en) | Hermetic type compressor and refrigerator | |
| CN102022325B (en) | Rotary compressor and refrigerating device with same | |
| US20060147326A1 (en) | Hermetically sealed compressor | |
| JP2007510836A (en) | Compressor | |
| KR102328761B1 (en) | Compressors and refrigeration cycle units | |
| JP2008208812A (en) | Hermetic compressor and refrigerator | |
| KR20200020860A (en) | Compressor and refrigeration cycle unit | |
| CN116696719A (en) | Lubricant containing part for refrigerant compressor and refrigerant compressor | |
| CN106837745B (en) | Compressor with a compressor housing having a plurality of compressor blades | |
| JP2008150962A (en) | Compressor, air conditioner, and water heater | |
| CN103620219A (en) | A hermetic compressor comprising an oil sucking member | |
| WO2015078532A1 (en) | Reciprocating compressor with reduced size and improved shape for use in a refrigeration appliance | |
| JP2017141724A (en) | Hermetic type compressor and apparatus including the same | |
| JP6235318B2 (en) | Hermetic compressor | |
| JP2013096306A (en) | Hermetic compressor | |
| JP2010031817A (en) | Compressor | |
| CN105443388A (en) | Rack used for scroll compressor and scroll 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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Tokyo, Japan Patentee after: Hitachi Global Living Program Co., Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Household Electric Appliance Co. |