CN101307765A - Compressor - Google Patents

Compressor Download PDF

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Publication number
CN101307765A
CN101307765A CNA2008101256522A CN200810125652A CN101307765A CN 101307765 A CN101307765 A CN 101307765A CN A2008101256522 A CNA2008101256522 A CN A2008101256522A CN 200810125652 A CN200810125652 A CN 200810125652A CN 101307765 A CN101307765 A CN 101307765A
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CN
China
Prior art keywords
cylinder
seal container
support member
refrigeration agent
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CNA2008101256522A
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Chinese (zh)
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CN101307765B (en
Inventor
只野昌也
山崎晴久
松本兼三
松浦大
里和哉
斎藤隆泰
江原俊行
今井悟
小田淳志
佐藤孝
松森裕之
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.)
Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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
Priority claimed from JP2001295663A external-priority patent/JP2003097434A/en
Priority claimed from JP2001295673A external-priority patent/JP2003097478A/en
Priority claimed from JP2001296180A external-priority patent/JP3986283B2/en
Priority claimed from JP2001296165A external-priority patent/JP4236400B2/en
Priority claimed from JP2001295859A external-priority patent/JP3913507B2/en
Priority claimed from JP2001295866A external-priority patent/JP2003097472A/en
Priority claimed from JP2001295654A external-priority patent/JP2003097433A/en
Priority claimed from JP2001295678A external-priority patent/JP2003097479A/en
Priority claimed from JP2001311699A external-priority patent/JP3963691B2/en
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of CN101307765A publication Critical patent/CN101307765A/en
Application granted granted Critical
Publication of CN101307765B publication Critical patent/CN101307765B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • 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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/001—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 of similar working principle
    • 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

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

Abstract

There is provided a rotary compressor capable of preventing deterioration of performance following plug fixing carried out to prevent falling-off a spring member. The compressor comprises a cylinder constituting a roller engaged with an eccentric portion formed in a rotary shaft of an electric element, and eccentrically rotated in the cylinder, a vane abutted on the roller to divide an inside of the cylinder into a low pressure chamber side and a high pressure chamber side, a spring member for always pressing the vane to the roller side, a housing portion of the spring member, formed in the cylinder, and opened to the vane side and a hermetically sealed container side, a plug positioned in the hermetically sealed container side of the spring member, and inserted into the housing portion to fit into a gap, and an O ring attached around the plug to seal a part between the plug and the housing portion. In this case, a space between the cylinder and the hermetically sealed container is set smaller than a distance from the O ring to an end of the plug on the hermetically sealed container side.

Description

Compressor
The application be application number " 02143506.5 ", the applying date " on September 26th, 2002 ", denomination of invention " compressor and manufacture method thereof, and refrigerant circuit remove case apparatus, and refrigerating plant " the dividing an application of application for a patent for invention.
Technical field
The present invention relates to a kind of compressor of the compression unit that in container, is provided with electrodynamic element, drives by this electrodynamic element and manufacture method thereof, and the defrosting plant of refrigerant circuit, and refrigerating plant.
Background technique
In the rotary compressor of existing this rotary compressor, particularly bosom die mould multistage compression formula, refrigerant gas is drawn into the low pressure chamber side of cylinder (first cylinder) from the suction port of first rotary compression element through refrigeration agent ingress pipe, suction path, press in the middle of being compacted into by the action with blade of rolling on the eccentric part that is entrenched in rotating shaft, from the hyperbaric chamber side of cylinder through exhaust port, discharge the anechoic chamber and be discharged in the seal container.And, the refrigerant gas of pressing in the middle of in this seal container is drawn into the low pressure chamber side of cylinder (second cylinder) by the suction port from second rotary compression element, by on the eccentric part that is entrenched in rotating shaft roll and second level compression is carried out in the action of blade (ベ-Application), become the refrigerant gas of High Temperature High Pressure, from hyperbaric chamber side process relief opening, drain passageway, discharge the anechoic chamber and be discharged to refrigerant circuit from refrigerant discharge leader, inflow constitutes in the radiator of refrigerant circuit with rotary compressor, after having dispelled the heat, by absorbing heat with vaporizer after the expansion valve throttling, be inhaled into first rotary compression element, carry out above-mentioned circulation so repeatedly.
The eccentric part of above-mentioned rotating shaft is being set up with having 180 degree phase differences, is being connected by joint between two eccentric parts.
In such rotary compressor, will the big refrigeration agent of height pressure reduction, for example as the carbon dioxide (CO of an example of carbonic acid gas 2) when being used as refrigeration agent, discharging refrigerant pressure reaches 12MPa in becoming the second rotary compressor spare of high pressure, in addition, becomes 8MPa (the middle pressure) in becoming first rotary compression element of rudimentary side.It becomes the pressure in the seal container.And the suction pressure of first rotary compression element is about 4MPa.
Being installed in blade on such rotary compressor can be inserted in the groove that is set up along the radial direction of cylinder with moving freely along the radial direction of cylinder.And, be provided with spring eye (container) at the rear side (seal container side) of blade to the outer openings of cylinder, in this spring eye, inserting frequently blade to rolling the helical spring (spring component) that side is suppressed, the opening from the cylinder outside has inserted O type seal ring to spring eye after, with stopper (preventing deviating from) obstruction and prevent that spring from flying out.
At this moment, because the off-centre of rolling rotation, plug is subjected to the power of the direction that is forced out laterally from spring eye.Particularly, in the rotary compressor of bosom die mould, owing to low pressure in the cylinder that becomes in the seal container than second rotary compression element, even because the inside and outside pressure difference of cylinder, stopper also becomes the state that is forced out.Therefore, in the prior art, be fixed on the cylinder by stopper being pressed into spring eye, but because this is pressed into, cylinder expands and is out of shape, and stop up between the support member (bearing) of opening surface of cylinder and produce the gap, thereby can not guarantee the sealing of cylinder interior, the problem that its performance is reduced is arranged.
In addition, in the rotary compressor of such bosom die mould multistage compression formula, because the pressure (high pressure) in the cylinder of second rotary compression element becomes pressure (the middle pressure) height in the seal container of oil storage portion than the bottom, utilize pressure difference in cylinder, to supply with its difficulty of oil pole from the oilhole of rotating shaft, become the state that only is lubricated, the problem of fuel delivery deficiency is arranged by the oil that dissolves in the suction refrigeration agent.
In addition, in the rotary compressor of such bosom die mould multistage compression formula, constitute the opening surface of the cylinder of second rotary compression element, in this support member, constitute above-mentioned discharge anechoic chamber simultaneously by support member sealing.The sectional drawing of in Figure 20, representing existing this support member 291.Forming the bearing 291A of rotating shaft in the central authorities of support member 291 with erecting, in this bearing 291A cushion cover 292 is being installed, discharging anechoic chamber 293 is hollowly to form on the support member 291 in the bearing 291A outside, and this discharges anechoic chamber 293 by cover 294 sealings.And this cover 294 is by not shown a plurality of being bolted on the support member 291.
At this, owing to become high high pressure in the seal container of pressing than the centre, the sealing of cover 294 becomes important problem in the discharge anechoic chamber 293 of the second rotation compression element.Therefore, adding packing ring 296 between cover 294 and support member 291, still, the bearing 291A side of central authorities is owing to away from bolt, in any case also variation of its sealing.Therefore, in the prior art, form with step on the base portion of 291A is forming sealing surface 291B, in sealing face 291B, also adding packing ring 296 ground and sealing, simultaneously C type back-up ring 297 is being installed in that bearing 291A goes up and the edge portion that will cover 294 bearing 291A side is pressed against support member 291 sides.
But, in so existing structure, discharge the volume of anechoic chamber owing to the formation sealing surface has dwindled, and need the installation of C type back-up ring, have the problem that processing cost and component costs uprise.
In addition, intensity about above-mentioned cover, when its thin thickness, be out of shape laterally owing to discharge the pressure difference in anechoic chamber and the seal container, produce gas leakage, conversely when thickness is blocked up, can not guarantee the insulation distance with electrodynamic element, and the problem that the compressor overall height dimension is enlarged.
In addition, the head pressure of second rotary compression element becomes high pressure in this wise, in the prior art since with each cylinder only by being that the bolt that middle heart is configured to concentric circles is connected on the support member with above-mentioned bearing with bearing, therefore, have from the danger of cylinder gas leakage.
In addition, when the above-mentioned pressure reduction of height like that when becoming big, be during with coaxial circular of this rotating shaft in the section configuration of the joint of above-mentioned running shaft, the basal area that can guarantee is little physically, the easy resiliently deformable of rotating shaft.Therefore, in the prior art, the section configuration of joint formed with the wall thickness of the eccentric direction of two eccentric parts compare, wall thickness on the direction vertical with this eccentric direction becomes big rugby ball shape to seek to improve intensity, but, labor content when the cutting rotating shaft is arranged increases, the problem of manufacturing efficiency variation.
In addition, in the compressor of such sealed mode, in the obligated air tightness test of carrying out seal container in the inspection of finishing of manufacturing technology.This test pressure can be roughly about 4MPa in common compressor, still, and as previously mentioned with CO 2When using as refrigeration agent, because the pressure of seal container (pressing in the middle of under above-mentioned situation being) is high, the test pressure about the 10Mpa of the design CLV ceiling limit value of pressing in the middle of requiring to become.Therefore, be difficult to connect simply such test pressure is applied to pressurized air generating apparatus and compressor in the seal container.
In addition, in order to be drawn into the gas-liquid separation of the refrigerant gas in first rotary compression element, storage is installed in seal container.This storage is connected on the carriage on the side that is welded on seal container by welding or by band installations of etc.ing, and is being kept by the outside along seal container, when capacity that must the increase storage, can make the pipe arrangement generation interference of storage and refrigeration agent ingress pipe etc.
Therefore, in the prior art, as the measure that prevents the problems referred to above, change to such form that the shape of carriage self is left from pipe arrangement, change the holding position of storage and storage self is left from pipe arrangement, but the former situation, because carriage becomes when spraying paint of seal container etc. and draws extension portion on the suspension bracket that hangs over manufacturing mechanism, must change the suspension bracket of the usefulness of spraying paint, in the latter case, since with central authorities' (or position of centre of gravity) of storage from the place keep, the vibration that has therefore produced storage self becomes big and makes the big problem of noise change.
In addition, will be discharged in the seal container in the middle of the refrigerant gas of pressing when being arranged in another refrigeration agent ingress pipe outside the seal container and being drawn into second rotary compression element, towards the refrigeration agent ingress pipe of first rotary compression element with go into pipe towards the refrigeration agent of second rotary compression element and be connected on the seal container in position adjacent.
Therefore, two interferences of two refrigeration agent ingress pipes have configuration to become the problem of difficulty.Particularly, owing on the refrigeration agent ingress pipe of first rotary compression element, connecting storage usually, therefore this accumulation of energy is configured in the top of the link position of each refrigeration agent ingress pipe, the interference that is easy to generate two refrigeration agent ingress pipes is also arranged and the problem of the position of the storage that is difficult to descend.
In addition, in such rotary compressor, be used for the wiring terminal that electrodynamic element is powered is installed in the end cap of seal container.Figure 23 represents the sectional drawing of the rotary compressor wiring terminal 299 parts part of such prior art.Wiring terminal parts 299 are welded on end cap 298 top, and this end cap 298 is the asymmetric section configuration in relative center such shown in this figure.
At this, on end cap 298, be subjected to the influence of internal high pressure power and make with the welding portion of wiring terminal parts 299 towards the direction distortion that bloats laterally.Result at the amount of deformation of the end cap 298 of local other expression actual measurement of the upper zone of Figure 23.In the figure, the amount of deformation in the zone of representing with Z4 is 0.2 μ m, and the distortion quantitative change in the zone of representing with Z5 is big, is 0.5 μ m, and the amount of deformation maximum in the zone of representing with Z6 reaches 0.9 μ m.
Like this, because the amount of deformation of wiring terminal 299 parts becomes maximum, there is the welding portion of wiring terminal parts 299 and end cap 298 to produce be full of cracks or weld the problem of peeling off and resistance to pressure being descended.
In addition, Figure 25 represents the sectional drawing of wiring terminal parts 300 parts of another rotary compressor.Wiring terminal parts 300 are made of the glass portion 302 of the circle that is provided with electrical end 307 and metal assembly department 303 of being formed on around it, this assembly department 303 by be weldingly fixed on forms and seal container 304 on the peripheral portion of mounting hole 306.
At this, the thickness of the assembly department 303 of wiring terminal 300 has served as when thin, holds high pressure intensity of force (withstand voltage properties) deficiency of the refrigerant gas in the anti-above-mentioned seal container 304, becomes the reason that produces faults such as be full of cracks on assembly department 303.In addition, when blocked up,,, the problem of the danger that produces gas leakage or destruction is arranged because this heat produces damage to glass portion 302 easily owing to seal container 304 welding the time, need many heats.
In addition, the opening surface of the cylinder of such rotary compressor is sealing by constituting the support member of discharging the anechoic chamber in inside, still, is also constituting the bearing of the rotating shaft of electrodynamic element in these support member central authorities.And, even fuel feeding is insufficient also can to keep sliding capability and lining that the high PV value (load that applies on the per unit area) during for high load has the graphite system of high abrasion resistance energy if be provided with between this bearing and rotating shaft, then can improve the durability of rotary compressor significantly, but, the lining costliness of such graphite has the high shortcoming of cost of parts.
In addition, above-mentioned refrigeration agent ingress pipe or refrigerant discharge leader are on the sleeve pipe cylindraceous that is connected on the flexure plane that is weldingly fixed on seal container, but in order to obtain sleeve pipe with respect to the perpendicularity of the internal diameter of seal container and used jig, therefore, assembling operation variation, verticality precision are also low.
In addition, what the cylinder of the rotary compression element of high pressure used is the cylinder of thin thickness, therefore, in the thickness of cylinder, can not form and suck path and drain passageway, therefore, form to suck path and drain passageway by the opening surface of closed cylinder in support member side, on cylinder, tiltedly be formed for making the above-mentioned suction port and the exhaust port that are communicated with in this suction path and drain passageway and the cylinder with bearing.
Figure 31 and Figure 32 represent the processing method in the past of this suction port and exhaust port.In each figure, the 311st, the cylinder of formation rotary compression element, the 312nd, be formed obliquely the suction port on this cylinder 311, the 313rd, exhaust port.When the suction port 312 that forms wherein, by make the smooth end mill ML1 of front end relative to cylinder 311 tilt, promptly along on the plane of inclination that is close to suction port 312 relative to the vertical direction in the plane of inclination of suction port 312 and the true dip direction of the suction port 312 shown in the arrow among Figure 31 move, and form the groove of relative cylinder 311 inclinations.
In addition, when forming exhaust port 313, by the relative cylinder 311 of end mill ML1 is tilted, at this moment press and release the smooth end mill ML1 of front end towards the vertical direction in the plane of inclination of relative suction port 313, and form the breach that relative cylinder 311 tilts to the true dip direction of the suction port shown in the arrow among Figure 32 313.
Like this, because the past is to form suction port 312 and exhaust port 313 on cylinder 311, therefore, the edge portion of the suction passage side of suction port 312 (the upper right edge of Figure 31) becomes straight line shape, sucking gas generation turbulent flow, there is passage resistance to become big problem with the connected part that sucks path.In addition because the relative cylinder 311 of end mill ML1 is provided with obliquely, therefore, must carry out in addition with other bolt also or the identical boring of lightening hole process, increased workload, the problem that has cost of production to uprise.
In addition, in the refrigerant circuit of the two stage compression formula rotary compressor that uses such bosom die mould, owing on vaporizer, produce frost, therefore must defrost, but, for the defrosting of this vaporizer will be can't help decompressor decompression ground when supplying to vaporizer (though comprise the situation that directly supplies to vaporizer and by decompressor but in its situation that it is not supplied with reducing pressure) from the high temperature refrigerant that second rotary compression element is discharged, the suction pressure of first rotary compression element rises, thus, the head pressure of first rotary compression element (the middle pressure) uprises.
Though this refrigeration agent is discharged from by second rotary compression element, but, owing to do not reduce pressure, the head pressure of second rotary compression element becomes identical with the suction pressure of first rotary compression element, therefore, there are the discharge (high pressure) of second rotary compression element and suction (the middle pressure) to produce the problem that pressure reverses phenomenon.
In addition, in the compression type rotary compressor of the two poles of the earth of such bosom die mould, because the pressure (high pressure) in the cylinder of second rotary compression element becomes pressure (the middle pressure) height in the seal container of oil storage portion than the bottom, therefore the utmost point is not easy to utilize pressure difference to supply with oil from the oilhole of rotating shaft in cylinder, become the state that only oneself is lubricated, the fuel delivery deficiency by the oil that dissolves in refrigeration agent.
Summary of the invention
The present invention makes for the problem that solves prior art as described above, and its objective is provides a kind of rotary compressor that is used to prevent the fixing of stopper that spring component comes off and makes degradation that can prevent to be accompanied by.
Promptly, rotary compressor of the present invention is to be provided with electrodynamic element in seal container, constitute by the rotary compression element of this electrodynamic element driving, it is characterized in that, comprise and rolling, blade, spring component, the container of spring component, stopper, the O RunddichtringO, above-mentionedly roll on the eccentric part that is entrenched in the rotating shaft that is formed at the cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, be rotated prejudicially, above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, above-mentioned spring component is used for this blade is suppressed to rolling side frequently, above-mentioned spring component container is formed in the cylinder and to blade-side and seal container side opening, above-mentioned stopper is positioned at the seal container side of spring component and is inserted in the container with Spielpassung, above-mentioned O RunddichtringO is installed on the side face of stopper, is used to seal between this stopper and the container; Set the interval between cylinder and seal container littler than the distance of the end of seal container side from the O RunddichtringO to stopper.
In addition, rotary compressor of the present invention, in seal container, has electrodynamic element, first and second rotary compression elements by this electrodynamic element driving, by first rotary compression element compressed gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, comprise and rolling, blade, spring component, the container of spring component, stopper, the O RunddichtringO, above-mentionedly roll on the eccentric part that is entrenched in the rotating shaft that is formed at the cylinder that is used to constitute second rotary compression element and electronic key element and in cylinder, be rotated prejudicially, above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, above-mentioned spring component is used for this blade is suppressed to rolling side frequently, above-mentioned spring component container is formed in the cylinder and to blade-side and seal container side opening, above-mentioned stopper is positioned at the seal container side of spring component and is inserted in the container with Spielpassung, above-mentioned O RunddichtringO is installed on the side face of stopper, is used to seal between this stopper and the container; Set the interval between cylinder and seal container littler than the distance of the end of seal container side from the O RunddichtringO to stopper.
According to the present invention, by in seal container, being provided with electrodynamic element, in the rotary compressor that constitutes by the rotary compression element of this electrodynamic element driving, owing to comprise and rolling, blade, spring component, the container of spring component, stopper, the O RunddichtringO, above-mentioned roll on the eccentric part that is entrenched in the rotating shaft that forms with cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, being rotated prejudicially, above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, above-mentioned spring component is used for this blade is suppressed to rolling side frequently, above-mentioned spring component container is formed in the cylinder and to blade-side and seal container side opening, above-mentioned stopper is positioned at the seal container side of spring component and is inserted in the container with Spielpassung, above-mentioned O RunddichtringO is installed on the side face of stopper, be used to seal between this stopper and the container, therefore, can possibly prevent from sealing to be reduced stopper being pressed into cylinder deformation when being fixed in the container, the unfavorable condition of degradation.
In addition, even because above-mentioned Spielpassung, set the interval between cylinder and seal container littler than the distance of the end of seal container side from the O RunddichtringO to stopper, therefore, move to the direction that is pushed out from the container at stopper, contact it with seal container and move the moment that is prevented from, the O RunddichtringO still is positioned at the container and is sealing, so the function of stopper can not produce any problem.
Be in the rotary compressor of middle multistage compression formula of pressing particularly, with CO in seal container inside 2Gas uses as refrigeration agent, press in the middle of in seal container being, when becoming extra-high voltage in second rotary compression element, for the performance of keeping compressor and prevent spring component deviate to have significant effect.
In addition, rotary compressor of the present invention is the rotary compression element that is provided with electrodynamic element in seal container, is driven by this electrodynamic element and constituting, and it is characterized in that, comprise roll, support member, blade, spring component, the container of spring component, stopper; Above-mentionedly roll on the eccentric part that is entrenched in the rotating shaft that is formed at the cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, be rotated prejudicially; Above-mentioned support member, the opening surface of closed cylinder, and have the bearing of running shaft; Above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling; Above-mentioned spring component is used for this blade is suppressed to rolling side frequently; Above-mentioned stopper is positioned at the seal container side of spring component and is pressed into and is fixed on the container; On the support member of the part corresponding, forming the portion that dodges towards the direction depression of leaving from cylinder with this stopper.
In addition, rotary compressor of the present invention, first and second rotary compression elements that in seal container, have electrodynamic element, drive by this electrodynamic element, to be discharged in the seal container by the gas of first rotary compression element compression, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, comprise roll, blade, support member, spring component, the container of spring component, stopper; Above-mentionedly roll on the eccentric part that is entrenched in the rotating shaft that is formed at the cylinder that is used to constitute second rotary compression element and electronic key element and in cylinder, be rotated prejudicially, the opening surface of above-mentioned support member closed cylinder and have the bearing of rotating shaft; Above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling; Above-mentioned spring component is used for this blade is suppressed to rolling side frequently, and the container of above-mentioned spring component is formed in the cylinder, and to blade-side and seal container side opening; Above-mentioned stopper is positioned at the seal container side of spring component and is pressed into and is fixed on the container; On the support member of the part corresponding, forming the portion that dodges towards the direction depression of leaving from cylinder with this stopper.
According to invention, owing to the rotary compression element that is provided with electrodynamic element in seal container, driven by this electrodynamic element constitutes in the rotary compressor, comprise roll, support member, blade, spring component, the container of spring component, stopper; Above-mentionedly roll on the eccentric part that is entrenched in the rotating shaft that is formed at the cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, be rotated prejudicially, the opening surface of above-mentioned support member closed cylinder and have the bearing of running shaft; Above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, and above-mentioned spring component is used for this blade is suppressed to rolling side frequently; The container of above-mentioned spring component is formed in the cylinder, and to blade-side and seal container side opening; Above-mentioned stopper is positioned at the seal container side of spring component and is pressed into and is fixed on the container; On the support member of the part corresponding, forming the portion that dodges towards the direction depression of leaving from cylinder with this stopper, therefore, even because stopper is pressed into the container, cylinder is to the dilatancy of support member side, also can absorb the distortion of this cylinder by this portion of dodging, can avoid between cylinder and support member producing the bad phenomenon in gap, thus, can possibly avoid the reduction of the sealing brought owing to cylinder deformation to make the bad phenomenon of degradation.
Particularly in the rotary compressor of seal container bosom die mould multistage compression formula, with CO 2Gas uses as refrigeration agent, press in the middle of in seal container being, when becoming extra-high voltage in second rotary compression element, for the performance of keeping compressor and prevent spring component deviate to have significant effect.
In addition, the objective of the invention is in the rotary compressor of bosom die mould multistage compression formula to carry out smoothly and positively to becoming the partial second rotary compression element fuel feeding.
Promptly, rotary compressor of the present invention, in seal container, has electrodynamic element, first and second rotary compression elements by this electrodynamic element driving, to be discharged in the seal container by the gas of first rotary compression element compression, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, comprise the cylinder that is used for constituting respectively each rotary compression element, be folded in the intermediate section dividing plate that is used to separate each rotary compression element between each cylinder, the opening surface of inaccessible respectively each cylinder and have the support member of the bearing of rotating shaft, be formed on the oilhole in the rotating shaft; The fuel feeding road that will be used to be communicated with the suction side of this oilhole and second rotary compression element is formed in the intermediate section dividing plate.
According to the present invention, because first and second rotary compression elements that in seal container, have electrodynamic element, drive by this electrodynamic element, to be discharged in the seal container by the gas of first rotary compression element compression, the intermediate pressure gas body that again this is discharged from is by the compression of this second rotary compression element, comprise the cylinder that is used for constituting respectively each rotary compression element, be folded in be used between each cylinder to separate the intermediate section dividing plate of each rotary compression element, respectively seal the opening surface of each cylinder and have the bearing of rotating shaft support member, be formed on the oilhole in the rotating shaft; The fuel feeding road that will be used to be communicated with the suction side of this oilhole and second rotary compression element is formed in the intermediate section dividing plate, even under the high situation of the pressure in the seal container of pressing in the middle of the pressure ratio therefore in the cylinder of second rotary compression element becomes, also can utilize the suction crushing in the suction process of second rotary compression element positively to supply with oil from the fuel feeding road direction cylinder that is formed in the intermediate section dividing plate.
Thus, the lubricated of second rotary compression element can be positively carried out, the raising with reliability guaranteed of performance can be sought.
In addition, rotary compressor of the present invention, it is characterized in that, in above-mentioned, the through hole that wears the inner peripheral surface that is communicated with outer circumferential face and rotation shaft side on the intermediate section dividing plate constitutes the fuel feeding road, and the opening of the outer circumferential face side of sealing through hole is located in the cylinder that is used to constitute second rotary compression element with the intercommunicating pore that is communicated with this through hole and suction side.
According to the present invention, on the basis of the above, constitute the fuel feeding road owing on the intermediate section dividing plate, wear the through hole that is communicated with outer circumferential face and rotation shaft side inner peripheral surface, and the opening of the outer circumferential face side of sealing through hole, the intercommunicating pore that is communicated with this through hole and suction side is located in the cylinder that is used to constitute second rotary compression element, therefore, the processing transfiguration of intermediate section oiled-plate method that is used to constitute the fuel feeding road is easy, and cost of production is reduced.
In addition, the objective of the invention is in the rotary compressor of bosom die mould multistage compression formula positively to be used for the sealing of cover of the discharge anechoic chamber of inaccessible second rotary compression element with simple structure.
That is, rotary compressor of the present invention has electrodynamic element, by first and second rotary compression elements that this electrodynamic element drives in seal container, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, have the cylinder that is used to constitute second rotary compression element, inaccessible this cylinder opening surface and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, periphery be fixed on the lid of the opening portion that is used for inaccessible discharge anechoic chamber on the support member with bolt; Between this lid and support member, sandwich packing ring, and between interior all end faces that cover and bearing outside, be provided with the O RunddichtringO.
According to the present invention because in seal container, have electrodynamic element, by first and second rotary compression elements that electrodynamic element drives, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, have the cylinder that is used to constitute second rotary compression element, the opening surface that seals this cylinder and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, periphery be fixed on the lid of the opening portion that is used for inaccessible discharge anechoic chamber on the support member with bolt; Between this lid and support member, sandwich packing ring, and between interior all end faces that cover and bearing outside, be provided with the O RunddichtringO, therefore, can on the bearing base portion, not form under the situation of sealing surface and seal fully by the interior all end faces in the lid, prevent from cover and support member between gas leakage.
Thus, the volume expansion of having sought the discharge anechoic chamber is unnecessary to be fixed on lid on the bearing by C type back-up ring as originally, therefore, also can realize the remarkable reduction of processing cost and cost of parts generally.
In addition, the objective of the invention is in the rotary compressor of bosom die mould multistage compression formula, is appropriate value with the thickness setting of the lid of the discharge anechoic chamber of inaccessible second rotary compression element.
That is, rotary compressor of the present invention has electrodynamic element, by first and second rotary compression elements that this electrodynamic element drives in seal container, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, have the cylinder that is used to constitute second rotary compression element, inaccessible this cylinder opening surface and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, be installed in the lid of the opening portion that is used for inaccessible discharge anechoic chamber on the support member; The thickness size of this lid is set at below the above 10mm of 2mm.
In addition, rotary compressor of the present invention is characterized in that, in above-mentioned, is 6mm with the thickness setting of this lid.
According to the present invention because in seal container, have electrodynamic element, by first and second rotary compression elements that this electrodynamic element drives, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, have the cylinder that is used to constitute second rotary compression element, inaccessible this cylinder opening surface and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, be installed in the lid of the opening portion that is used for inaccessible discharge anechoic chamber on the support member; The thickness size of this lid is set at below the above 10mm of 2mm, further be that the thickness size that will cover is set at 6mm, therefore in the intensity of having guaranteed lid itself, prevent gas leakage by its distortion generation in, can also guarantee and electrodynamic element between insulation distance, can realize the miniaturization of compressor.
In addition, rotary compressor of the present invention is characterized in that, in above-mentioned each invention, cover bolt is fixed on periphery on the support member, sandwiches packing ring between this lid and support member, and is provided with the O RunddichtringO between interior all end faces that cover and bearing outside.
According to the present invention, because on above-mentioned basis, cover bolt is fixed on periphery on the support member, between this lid and support member, sandwich packing ring, and between interior all end faces that cover and bearing outside, be provided with the O RunddichtringO, therefore, can on the bearing base portion, not form under the situation of sealing surface and seal fully by the interior all end faces in the lid, prevent from cover and support member between gas leakage.
Thus, necessity was fixed on lid on the bearing by C type back-up ring as originally owing to realized enlarging not by the volume of discharge anechoic chamber, therefore, also can realize the remarkable reduction of processing cost and cost of parts generally.
In addition, the objective of the invention is to prevent CO effectively 2The rotary compressor that uses as refrigeration agent from the cylinder gas leakage.
That is, rotary compressor of the present invention has electrodynamic element, by first and second rotary compression elements that this electrodynamic element drives in seal container, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, comprise the cylinder that is used for constituting respectively each rotary compression element, the opening surface of inaccessible respectively each cylinder also has the support member of the bearing of running shaft in central authorities, be formed on the discharge anechoic chamber that is communicated with cylinder interior on each support member in the bearing outside, be installed in the inaccessible respectively lid of discharging the opening portion of anechoic chamber that is used on each support member, by affixed each cylinder of a plurality of kingbolts, each support member and each lid, and by affixed each cylinder of auxiliary bolt and each support member that are positioned at the kingbolt outside.
According to the present invention because in seal container, have electrodynamic element, by first and second rotary compression elements that electrodynamic element drives, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, it is characterized in that, comprise the cylinder that is used for constituting respectively each rotary compression element, the opening surface of inaccessible respectively each cylinder also has the support member of the bearing of running shaft in central authorities, be formed on the discharge anechoic chamber that is communicated with cylinder interior on each support member in the bearing outside, be installed in the inaccessible respectively lid of discharging the opening portion of anechoic chamber that is used on each support member, by affixed each cylinder of a plurality of kingbolts, each support member and each lid, and by affixed each cylinder of auxiliary bolt and each support member that are positioned at the kingbolt outside, therefore can prevent to improve sealing from gas leakage such as between the cylinder of second rotary compression element that becomes high pressure and support member.
In addition, rotary compressor of the present invention, in above-mentioned, it is characterized in that, have roll, blade, guide slot, above-mentioned roll on the eccentric part that is entrenched on the running shaft that is formed at electrodynamic element and carry out off-centre and rotate in the cylinder that constitutes second rotary compression element, above-mentioned blade are rolled with this and are contacted and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder, and above-mentioned guide slot is formed on the cylinder, be used to take in blade; Auxiliary bolt is positioned near the guide slot.
According to the present invention, since have on the basis of the above roll, blade, guide slot, above-mentioned roll on the eccentric part that is entrenched on the running shaft that is formed at electrodynamic element and in the cylinder that constitutes second rotary compression element, carry out off-centre and rotate, above-mentioned blade rolls with this and contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder, and above-mentioned guide slot is formed on and is used to take in blade on the cylinder; Auxiliary bolt is positioned near the guide slot, therefore, can be prevented to be applied to the gas leakage of the back pressure on the blade by auxiliary bolt effectively.
In addition, the purpose of this invention is to provide a kind of rotary compressor of when the intensity of seeking running shaft improves, also seeking the improvement of processability.
I.e. Fa Ming rotary compressor, in seal container, has electrodynamic element, first and second rotary compression element by this electrodynamic element driving, compress the gas that compressed with first rotary compression element by second rotary compression element, it is characterized in that, having first and second rolls, this first and second roll and be embedded on first and second eccentric part, this first and second eccentric part is formed at with having 180 degree phase differences and is used to constitute first and second cylinder of first and second rotary compression element and the rotating shaft of electrodynamic element, the section configuration that connects the joint of two eccentric parts is formed the big shape of wall thickness of comparing the direction vertical with the wall thickness of the eccentric direction of two eccentric parts with this eccentric direction, and the side of the eccentric direction side of first eccentric part of this joint is formed and the concentric circular shape of second eccentric part, and the face of the eccentric direction side of second eccentric part forms and the concentric circular shape of first eccentric part.
According to the present invention, owing in seal container, have electrodynamic element, first and second rotary compression element by this electrodynamic element driving, compress the gas that compressed with first rotary compression element by second rotary compression element, having first and second rolls, this first and second roll and be entrenched on first and second eccentric part, this first and second eccentric part is formed at with having 180 degree phase differences and is used to constitute first and second cylinder of first and second rotary compression element and the rotating shaft of electrodynamic element, the section configuration that connects the joint of two eccentric parts is formed the big shape of wall thickness of comparing the direction vertical with the wall thickness of the eccentric direction of two eccentric parts with this eccentric direction, therefore, improve the rigidity intensity of running shaft, can prevent its resiliently deformable effectively.
Particularly, because the side of the eccentric direction side of first eccentric part of this joint is formed and the concentric circular shape of second eccentric part, the face of the eccentric direction side of second eccentric part forms and the concentric circular shape of first eccentric part, therefore when cutting has the rotating shaft of two eccentric parts and joint, can reduce the number of times that changes holding position.Thus, can reduce manufacturing procedure, can realize the raising of manufacturing efficiency, and then can realize that cost reduces.
In addition, the purpose of this invention is to provide a kind of with CO 2As refrigeration agent compressor that use, that also can easily carry out the sealed mode of airtight experiment when in seal container, becoming high pressure.
That is, closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside from refrigerant discharge leader, it is characterized in that, have the sleeve pipe that connects refrigeration agent ingress pipe and refrigerant discharge leader respectively that is located in the seal container, on the external surface peripheral of this sleeve pipe, forming the lip part that is used for connecting the connector of usefulness in conjunction with pipe arrangement.
According to the present invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside closed-type compressor from refrigerant discharge leader, has the sleeve pipe that connects refrigeration agent ingress pipe and refrigerant discharge leader respectively that is located in the seal container, external surface peripheral at this sleeve pipe is forming the lip part that is used for connecting in conjunction with pipe arrangement the connector of usefulness, therefore, utilize this lip part will be located at connector on the pipe arrangement that comes from the pressurized air generating apparatus simply in conjunction with being connected on the sleeve pipe of seal container.
Thus, can finish inside at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
In addition, closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside from refrigerant discharge leader, it is characterized in that, have be located on the seal container, connect the sleeve pipe of refrigeration agent ingress pipe and refrigerant discharge leader respectively, forming the thread groove that pipe arrangement connects usefulness at the external surface peripheral of this sleeve pipe.
According to this invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged in the outside closed-type compressor by refrigerant discharge leader, has the sleeve pipe that connects refrigeration agent ingress pipe and refrigerant discharge leader respectively that is located on the seal container, external surface peripheral at this sleeve pipe is forming the thread groove that pipe arrangement connects usefulness, therefore utilizes this thread groove the pipe arrangement from the pressurized air generating apparatus can be connected on the sleeve pipe of seal container simply.
Thus, can finish inside at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
In addition, closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside from refrigerant discharge leader, it is characterized in that, have a plurality of sleeve pipes that connect refrigeration agent ingress pipe and refrigerant discharge leader respectively that are located in the seal container, external surface peripheral at an adjacent square casing is forming the lip part that is used for connecting in conjunction with pipe arrangement the connector of usefulness, and the external surface peripheral at the opposing party's sleeve pipe is forming the thread groove that pipe arrangement connects usefulness simultaneously.
According to the present invention, because first and second rotary compression element that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged in the outside closed-type compressor by refrigerant discharge leader, have a plurality of sleeve pipes that connect refrigeration agent ingress pipe and refrigerant discharge leader respectively that are located in the seal container, external surface peripheral at an adjacent square casing is forming the lip part that is used for connecting in conjunction with pipe arrangement the connector of usefulness, external surface peripheral at the opposing party's sleeve pipe is forming the thread groove that pipe arrangement connects usefulness simultaneously, therefore utilize lip part to utilize this thread groove the pipe arrangement from the pressurized air generating apparatus can be connected on the opposing party's sleeve pipe of seal container simply with the connector on the pipe arrangement that is located at from the pressurized air generating apparatus simply in conjunction with being connected on the square casing of seal container.Can finish inside thus at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
Particularly owing on an adjacent square casing, forming lip part, on the opposing party's sleeve pipe, forming thread groove, therefore can not be adjacent to the bigger connector of Conncetion cimension mutually, can utilize a plurality of pipe arrangements of this narrow space connection when the interval between sleeve pipe is narrow yet from the pressurized air generating apparatus.
In addition, the compressor that the purpose of this invention is to provide a kind of capacity change of the device of corresponding stored easily.
Promptly, compressor of the present invention, the compression unit that in container, has electrodynamic element, drives by this electrodynamic element, it is characterized in that, have vessel side carriage, storage on the container side of being located at, the memory side carriage of this storage is installed,, storage is installed on the container by two carriages by this memory side carriage is fixed on the vessel side carriage.
In addition, compressor of the present invention, in above-mentioned, base is characterised in that, the memory side carriage be installed in the central authorities of storage or position of centre of gravity or they near.
According to the present invention, because compressor has electrodynamic element, driven by this electrodynamic element in container compression unit, have vessel side carriage, storage on the container side of being located at, the memory side carriage of this storage is installed, by this memory side carriage is fixed on the vessel side carriage, by two carriages storage is installed on the container, therefore, when changing the capacity of storage, can not change the seal container lateral bracket, only need to change the memory side carriage and get final product, thereby can prevent interference with pipe arrangement.Therefore, also eliminated influence for the manufacturing equipment of compressor.
In addition, even when the capacity of storage changes, only need change memory side carriage, near the installation memory side carriage central authorities of storage or position of centre of gravity or them, can be near the central authorities of storage or position of centre of gravity or them this storage of maintenance, can prevent to vibrate the increase of the noise that causes.
In addition, the purpose of this invention is to provide a kind of first and second refrigeration agent ingress pipe phase mutual noninterference, and can improve the compressor of space efficiency.
Compressor of the present invention, first and second compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, to this first compression unit imports the refrigerant pipe of refrigeration agent, the refrigerant gas of pressing in the middle of will be with this first compression unit compression import second compression unit refrigerant pipe, discharge the refrigerant pipe of the pressurized gas that compress with second compression unit, it is characterized in that, the refrigerant pipe of first and second compression unit is connected with seal container in position adjacent, arranges in the opposite direction around this seal container from this seal container.
In addition, compressor of the present invention, in above-mentioned compressor, it is characterized in that, the refrigerant pipe of first compression unit is connected with seal container in the position of the downside of the refrigerant pipe of second compression unit, disposing storage above each refrigerant pipe and link position seal container, this storage is connected with the refrigerant pipe that refrigeration agent is imported first compression unit.
According to the present invention, because its compressor has electrodynamic element in seal container, first and second compression unit by this electrodynamic element driving, import the refrigerant pipe of refrigeration agent to this first compression unit, to import the refrigerant pipe of second compression unit with the refrigerant gas of pressing in the middle of this first compression unit compression, discharge will be with the refrigerant pipe of the pressurized gas of second compression unit compression, the refrigerant pipe of first and second compression unit is connected with seal container in position adjacent, from this seal container unrolling in the opposite direction, therefore can in limited space, make each refrigerant pipe arrange each refrigerant pipe mutually uninterruptedly.
Particularly, refrigerant pipe at first compression unit is connected with seal container in the position of the downside of the refrigerator pipes of second compression unit, above each refrigerant pipe and link position seal container, disposing storage, when this storage is connected with the refrigerant pipe that refrigeration agent is imported first compression unit, can be when having avoided two refrigerant pipes to interfere mutually, descend to greatest extent by position and can make the refrigerant pipe of itself and second compression unit approaching, can improve space availability ratio significantly storage.
In addition, compressor of the present invention, in seal container, has electrodynamic element, first and second compression unit by this electrodynamic element driving, refrigerant pipe, be discharged in the seal container after this first refrigeration agent ingress pipe imports refrigeration agent with this first compression unit compression, the refrigerant gas of pressing in the middle of will discharging again sucks by the second outer refrigeration agent ingress pipe of the dried seal container in position, compress with second compression unit, it is characterized in that, first and second refrigeration agent ingress pipe is connected with seal container in position adjacent, from this seal container around this seal container towards mutually opposite direction setting.
In addition, compressor of the present invention, be in above-mentioned compressor, it is characterized in that, the first refrigeration agent ingress pipe is connected with seal container in the position of the second refrigeration agent ingress pipe downside, above each refrigeration agent ingress pipe and link position seal container, dispose storage, on this storage, connecting the first refrigeration agent ingress pipe.
According to the present invention, because in its compressor, in seal container, has electrodynamic element, first and second compression unit by this electrodynamic element driving, be discharged in the seal container behind the refrigerant gas of first refrigeration agent suction by the compression of first compression unit, the refrigerant gas of pressing in the middle of will discharging again sucks by being positioned at the second outer refrigeration agent ingress pipe of seal container, compress with second compression unit, first and second refrigeration agent ingress pipe is connected with seal container in position adjacent, arrange towards mutually opposite direction around this seal container from this seal container, therefore, can in limited space, make each refrigerant pipe not interfere ground to arrange each refrigeration agent ingress pipe mutually.
Particularly be connected with seal container in the position of the first refrigeration agent ingress pipe at the second refrigeration agent ingress pipe downside, above each refrigeration agent ingress pipe and link position seal container, disposing storage, when on this storage, connecting the first refrigeration agent ingress pipe, can be when having avoided two refrigerant pipes to interfere mutually, descend to greatest extent by position and can make the refrigeration agent ingress pipe of itself and second compression unit approaching, can improve space availability ratio significantly storage.
In addition, but the object of the invention provides the unfavorable condition that a kind of possible trouble prevents that the distortion by the end cap of seal container from producing.
Promptly, closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element, drives by this voltage component, by in this compression unit compressed refrigerant and the seal container of discharging, it is characterized in that, have the wiring terminal parts on the end cap that is installed in seal container, on the end cap around these wiring terminal parts, forming the step of regulation curvature by punching press.
According to the present invention, because its closed-type compressor, the compression unit that in seal container, has electrodynamic element, drives by this voltage component, by in this compression unit compressed refrigerant and the seal container of discharging, have the wiring terminal parts on the end cap that is installed in seal container, on the end cap around this joint, forming the step of regulation curvature by punching press, therefore, improved near the rigidity of the end cap the wiring terminal parts, particularly with CO 2When compressing, under the situation that the seal container internal pressure uprises, the amount of deformation of pressing the end cap that causes in the seal container can be reduced, resistance to pressure can be improved as refrigeration agent.
In addition, closed-type compressor of the present invention is in above-mentioned compressor, and it is roughly bowl-shape that above-mentioned end cap is, and the central shaft that step is with this end cap is the axisymmetric shape in center, and the wiring terminal parts are installed in the center of this end cap.
According to the present invention, because in above-mentioned closed-type compressor, it is roughly bowl-shape that above-mentioned end cap is, the central shaft that step is with this end cap is the axisymmetric shape in center, and the wiring terminal parts are installed in the center of this end cap, therefore even by the distortion of the end cap of pressing the wiring terminal parts welding portion that causes in the seal container, can possibly avoid because the be full of cracks of the welding portion that inhomogeneous deformation produces or peel off can further improve resistance to pressure.
In addition, the invention provides the closed-type compressor of the unfavorable condition that a kind of wiring terminal parts that can possibly avoid being used for to the electrodynamic element power supply partly produce.
That is, closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element, drives by this voltage component, by this compression unit compression CO 2In the seal container of refrigeration agent and discharge, it is characterized in that, have the wiring terminal parts on the end cap that is installed in seal container, these wiring terminal parts have the glass portion of the circle that connects and be installed with electrical end and be formed on this glass portion around the mounting hole peripheral portion that is weldingly fixed on seal container on flange shape metallic assembly department, the thickness size of this assembly department is the scope of 2.4 ± 0.5mm.
In addition, closed-type compressor of the present invention, first and second rotary compression element that in seal container, has electrodynamic element, drives by this voltage component, will be by the CO of this first rotary compression element compression 2Refrigerant gas is discharged in the seal container, compress the middle refrigerant gas of pressing of this ejection again with second rotary compression element, it is characterized in that, have the wiring terminal parts that are installed on the seal container, these wiring terminal parts have the glass portion of the circle that connects and be installed with electrical end and form this glass portion around the mounting hole peripheral portion that is weldingly fixed on seal container on flange shape metallic assembly department, the thickness size of this assembly department is the scope of 2.4 ± 0.5mm.
According to the present invention, owing to have the joint on the seal container that is installed in closed-type compressor, this joint have the glass portion of the circle that connects and be installed with electrical end and form this glass portion around the mounting hole peripheral portion that is weldingly fixed on seal container on flange shape metallic assembly department, the thickness size of this assembly department is the scope of 2.4 ± 0.5mm.Therefore, the use CO that the pressure in seal container is high 2In the closed-type compressor of refrigeration agent, can in the withstand voltage properties of fully guaranteeing joint, can suppress to weld the increase of fixing needed heat.
Thus, can possibly prevent owing to the assembly department at joint produces be full of cracks or produce gas leakage or the joint destruction that damage causes on glass portion.
In addition, the raising that the purpose of this invention is to provide a kind of cost that will be caused by the carbon system lining that is located between bearing and the rotating shaft is suppressed to the rotary compressor of irreducible minimum.
Promptly, rotary compressor of the present invention is provided with electrodynamic element and is driven by electrodynamic element in seal container rotary compression element, it is characterized in that, have one or more cylinders, first support member and second support member, this cylinder constitutes rotary compression element, this first support member inaccessible cylinder and the opening surface electrodynamic element opposition side, the bearing that has the rotating shaft of electrodynamic element simultaneously, the opening surface of the electrodynamic element side of this second support member closed cylinder, and have the bearing of rotating shaft, be provided with in the bearing of a certain side in first and second support member and add the carbon system lining that is located between this bearing and the rotating shaft.
In addition, rotary compressor of the present invention is characterized in that, in above-mentioned, is provided with lining in the bearing of first support member.
In addition, rotary compressor of the present invention, first and second rotary compression element that in closed container, has electrodynamic element and drive by this electrodynamic element, to be discharged in the seal container by the gas of this first rotary compression element compression, compress the middle gas of pressing of this discharge again with this second rotary compression element, it is characterized in that, has first and second cylinder that is used for constituting respectively first and second rotary compression element, seal the opening surface of first cylinder and have first support member of the bearing of electrodynamic element rotating shaft, seal the opening surface of second cylinder and have second support member of the bearing of rotating shaft, be provided with the carbon system lining that is folded between this bearing and the rotating shaft in the bearing of a certain side in first and second support member.
In addition, rotary compressor of the present invention is characterized in that, in above-mentioned, is provided with lining in the bearing of second support member.
In addition, rotary compressor of the present invention is characterized in that, in above-mentioned, rotary compression element is with CO 2Gas compresses as refrigeration agent.
According to the present invention, because rotary compressor of the present invention is provided with electrodynamic element and is driven by electrodynamic element in seal container revolution compression unit, have one or more cylinders, first support member and second support member, this cylinder constitutes the revolution compression unit, this first support member inaccessible cylinder and the opening surface electrodynamic element opposition side, the bearing that has the rotating shaft of electrodynamic element simultaneously, the opening surface of the electrodynamic element side of the inaccessible cylinder of this second support member, and has a bearing of rotating shaft, therefore be provided with the carbon system lining that is folded between this bearing and the rotating shaft in the bearing of a certain side in first and second support member, compare the reduction of the cost that can realize part with the situation that in the bearing of both sides' support member, is respectively equipped with lining.
Particularly, if in the bearing of first support member, be provided with lining, in the bearing of the second big support member of the area of contact of the electrodynamic element side of cylinder and rotating shaft, do not establish lining, then keep compression area little and be applied to the bearing of the first big support member of load on the unit area sliding capability, keep endurance quality in, by removing the lining that compression area is applied to greatly the bearing of the second less support member of duty ratio on the unit area, thereby can reduce cost.
In addition, according to the present invention, first and second rotary compression element that in closed container, has electrodynamic element and drive by this electrodynamic element, will be in seal container by the gas exhaust of this first rotary compression element compression, compressing the middle gas of pressing of this discharge with this second rotary compression element, it is characterized in that, has first and second cylinder that is used for constituting respectively first and second rotary compression element, the opening surface of inaccessible first cylinder also has first support member of the bearing of electrodynamic element rotating shaft, the opening surface of inaccessible second cylinder also has second support member of the bearing of rotating shaft, be provided with the carbon system lining that is folded between this bearing and the rotating shaft in the bearing of a certain side in first and second support member, therefore compare with the situation that packing ring is set in the bearing of both sides' support member respectively, can reduce the cost of part.
Particularly, if in the bearing of second supporting, be provided with lining, do not establish lining in the bearing of first support member of the opening surface of first cylinder below the pressure in obturation becomes seal container, then can keep inaccessible second cylinder higher than seal container internal pressure opening surface, carry out fuel feeding by pressure difference and become sliding capability in the bearing of second support member of difficulty, safeguard endurance quality, and, can eliminate the lining that carries out the bearing of the first no problem support member of fuel feeding by pressure difference, can reduce cost.
In addition, with CO 2Gas can have significant effect for the endurance quality of keeping compressor as becoming under the situation of extra-high voltage in refrigeration agent use, the seal container.
In addition, the object of the invention provides a kind of closed-type compressor of easily keeping the perpendicularity that is weldingly fixed on the sleeve pipe on the seal container.
Closed-type compressor of the present invention, the compression unit that in seal container, has electrodynamic element and drive by this electrodynamic element, discharge from the refrigerated medium discharge tube behind the refrigeration agent of refrigeration agent ingress pipe suction by the compression unit compression, it is characterized in that, has sleeve pipe, this sleeve pipe is installed accordingly with the open-work on the flexure plane that is formed on seal container, and be used to connect refrigeration agent ingress pipe and refrigerant discharge leader, forming tabular surface on the seal container outside around open-work, and around on sleeve pipe, forming the insertion part that is used to insert in the open-work and being positioned at it and the contacting part that contacts with the tabular surface of seal container, connect the contacting part of affixed this sleeve pipe and the tabular surface of seal container by projection welding.
According to the present invention, the compression unit that in seal container, has electrodynamic element and drive by this electrodynamic element, discharge from the refrigerated medium discharge tube behind the refrigeration agent of refrigeration agent ingress pipe suction by the compression unit compression, has sleeve pipe, this sleeve pipe is installed accordingly with the open-work on the flexure plane that is formed on seal container, and be used to connect refrigeration agent ingress pipe and refrigerant discharge leader, forming tabular surface on the seal container outside around open-work, and around on sleeve pipe, forming the insertion part that is used to insert in the open-work and being positioned at it and the contacting part that contacts with the tabular surface of seal container, connect the contacting part of affixed this sleeve pipe and the tabular surface of seal container by projection welding, by contacting of the contacting part of the tabular surface of seal container and sleeve pipe, can guarantee the perpendicularity of the internal diameter of sleeve pipe and seal container, thus, do not using the perpendicularity that can form sleeve pipe under the situation of anchor clamps etc., can improve producibility and improve precision.
In addition, closed-type compressor of the present invention is characterized in that, in above-mentioned, tabular surface is hollowly being formed around open-work.
According to this invention because on the basis of the above, tabular surface is hollowly formed around open-work, therefore, by the outside of the sleeve pipe in the depressed part that is embedded in seal container and depressed part more precision keep the perpendicularity of sleeve pipe well.
In addition, the purpose of this invention is to provide and a kind ofly can reduce the passage resistance that sucks gas, carry out the rotary compressor and the manufacture method thereof of the processing of the suction port of cylinder and exhaust port easily.
Promptly, rotary compressor of the present invention is provided with electrodynamic element and is driven by this electrodynamic element in seal container rotary compression element, it is characterized in that, comprise and rolling, support member, suck path, suction port, this rolls and is formed on the chimeric and eccentric rotation in cylinder of the rotating shaft eccentric part of the cylinder that is used to constitute rotary compression element and electrodynamic element, the opening surface of the inaccessible cylinder of above-mentioned support member also has the bearing of rotating shaft, above-mentioned suction path is formed on the support member, above-mentioned suction port, be formed obliquely on cylinder, with be communicated with in the suction path of support member makes this suction path and cylinder accordingly, the edge portion of the suction passage side of this suction port forms the semicircle arcuation.
According to the present invention because the rotary compression element that in seal container, is provided with electrodynamic element and drives by this electrodynamic element, comprise roll, support member, suction path, suction port; This rolls and is formed on the chimeric and eccentric rotation in cylinder of the rotating shaft eccentric part of the cylinder that is used to constitute rotary compression element and electrodynamic element, the opening surface of the inaccessible cylinder of above-mentioned support member also has the bearing of rotating shaft, above-mentioned suction path is formed on the support member, above-mentioned suction port, be formed obliquely on cylinder, with be communicated with in the suction path of support member makes this suction path and cylinder accordingly, the edge portion of the suction passage side of this suction port forms the semicircle arcuation, therefore, can alleviate the passage resistance of suction port and the interconnecting part office that sucks path, can reduce the disorder of air-flow and realize high efficiency running.
In addition, manufacture method of the present invention is characterized in that, the rotary compression element that in being manufactured on seal container, is provided with electrodynamic element and drives by this electrodynamic element, comprise roll, support member, suction path, suction port; This rolls and is formed on the chimeric and eccentric rotation in cylinder of the rotating shaft eccentric part of the cylinder that is used to constitute rotary compression element and electrodynamic element, the opening surface of the inaccessible cylinder of above-mentioned support member also has the bearing of rotating shaft, above-mentioned suction path is formed on the support member, above-mentioned suction port is formed obliquely on cylinder, and during with the rotary compressor that is communicated with in the suction path of support member makes this suction path and cylinder accordingly, the end mill and the cylinder of Transverse plane vertically are close on cylinder before making, it is moved along the direction that tilts relative to cylinder, process suction port thus.
According to the present invention, owing to the end mill of preceding Transverse plane can be formed the suction port of inclination under the state vertical with cylinder on cylinder, therefore, can form suction port with tapped hole or the same operation of the boring processing of lightening hole etc., can realize reducing production costs of bringing by reducing operation quantity with other.In addition, by such processing, even the end mill by preceding Transverse plane also can make the edge portion of the suction side of intakeport form the semicircle arcuation, therefore with similarly above-mentioned, can reduce the place mix of the connected part of intakeport and suction path, can realize high efficiency running by the disorder that reduces air-flow.
In addition, manufacture method of the present invention is characterized in that, the rotary compression element that in being manufactured on seal container, is provided with electrodynamic element and drives by this electrodynamic element, comprise roll, support member, suction path, exhaust port; This rolls and is formed on the chimeric and eccentric rotation in cylinder of the rotating shaft eccentric part of the cylinder that is used to constitute rotary compression element and electrodynamic element, the opening surface of above-mentioned support member closed cylinder also has the bearing of rotating shaft, above-mentioned suction path is formed on the support member, above-mentioned exhaust port is formed obliquely on cylinder, and during with the rotary compressor that is communicated with in the suction path of support member makes this drain passageway and cylinder accordingly, vertically be close on cylinder the processing exhaust port by a part and cylinder with the end mill of preceding end toper.
According to the present invention, owing to vertically be close at the exhaust port that can on its cylinder, form inclination on the cylinder by a part with the end mill of preceding end toper, therefore, can use with other tapped hole or the same operation of the boring processing of lightening hole etc. and form suction port, can realize reducing production costs of bringing by reducing operation quantity.
In addition, the objective of the invention is to, in the refrigerant circuit of the two stage compression type compressors that use the bosom die mould, the discharge in second compression unit that prevents to produce when evaporator defrost and the pressure of suction reverse.
Promptly, defrosting plant of the present invention, it is characterized in that, the refrigerant circuit of the refrigeration agent that comes out from vaporizer with the compression of first compression unit, stream control gear with refrigeration agent circulation of defrost circuit and this defrost circuit of control, this refrigerant circuit has compressor, gas cooler, decompressor and vaporizer, this compressor has electrodynamic element and driven by this electrodynamic element in seal container first and second compression unit, in the seal container that the first compression unit refrigerant compressed gas is discharged, compress the middle refrigerant gas of pressing of this discharge again with second compression unit, this gas cooler flows into the refrigeration agent of discharging from second compression unit of above-mentioned compressor, this decompressor is connected with the outlet side of this gas cooler, and this vaporizer is connected with the outlet side of this decompressor.
In addition, the defrosting plant of refrigerant circuit of the present invention is characterized in that, in above-mentioned, each compression unit is with CO 2Gas compresses as refrigeration agent.
In addition, the defrosting plant of refrigerating circuit of the present invention is characterized in that, generates hot water by the heat radiation from gas cooler.
According to the present invention, owing to compress with first compression unit the refrigerant circuit of the refrigeration agent that comes out from vaporizer, stream control gear with refrigeration agent circulation of defrost circuit and this defrost circuit of control, this refrigerant circuit has compressor, gas cooler, decompressor and vaporizer, this compressor has electrodynamic element and driven by this electrodynamic element in seal container first and second compression unit, in the seal container that the first compression unit refrigerant compressed gas is discharged, compress the middle refrigerant gas of pressing of this discharge again with second compression unit, this gas cooler flows into the refrigeration agent of discharging from second compression unit of above-mentioned compressor, this decompressor is connected with the outlet side of this gas cooler, this vaporizer is connected with the outlet side of this decompressor, therefore, when carrying out the defrosting of vaporizer, can make the refrigeration agent of discharging flow to defrost circuit by the stream control gear, under the state that does not reduce pressure, supply to vaporizer and heat from first compression unit.
Thus, can prevent under the state that not only makes the high-pressure refrigerant decompression of discharging from second compression unit, to supply to the problem that the pressure of the discharge that produces the situation that vaporizer defrosts second compression unit and suction reverses.
Particularly with CO 2In the refrigerant circuit of gas as the refrigeration agent use, can produce significant especially effect.In addition, when generating hot water, can the heat of the hot water of gas cooler be transported to vaporizer, can more promptly carry out the defrosting of vaporizer by refrigeration agent with gas cooler.
The objective of the invention is in the rotary compressor of bosom die mould multistage compression formula, carry out the fuel feeding in the cylinder of second rotary compression element that becomes high pressure smoothly and positively.
Promptly, rotary compressor of the present invention, first and second rotary compression element that in seal container, has electrodynamic element and drive by this electrodynamic element, to be discharged in the seal container by the gas of the first revolution compression unit compression, the gas of pressing in the middle of again this being discharged from compresses with second rotary compression element, it is characterized in that, has first and second cylinder that is used for constituting respectively first and second revolution compression unit, be added in and separate the intermediate clapboard that respectively turns round compression unit between these cylinders, seal the opening surface of each cylinder respectively and have the support member of bearing of the rotating shaft of electrodynamic element, be formed on the oilhole in the rotating shaft, the oil supply that will be used to be communicated with the low pressure chamber in this oilhole and second cylinder is formed on the face of second cylinder side of intermediate clapboard.
According to the present invention, because first and second rotary compression element that in seal container, has electrodynamic element and drive by this electrodynamic element, to be discharged in the seal container by the gas of the first revolution compression unit compression, the gas of pressing in the middle of again this being discharged from compresses with second rotary compression element, has first and second cylinder that is used for constituting respectively first and second rotary compression element, be added in the intermediate clapboard of separating each rotary compression element between these cylinders, seal the opening surface of each cylinder respectively and have the support member of bearing of the rotating shaft of electrodynamic element, be formed on the oilhole in the rotating shaft, the oil supply that will be used to be communicated with the low pressure chamber in this oilhole and second cylinder is formed on the face of second cylinder side of intermediate clapboard, therefore, even high situation in the seal container of pressing in the middle of the pressure ratio of the cylinder of second rotary compression element becomes also can utilize the pressure of inspiration(Pi) loss in the breathing process of second rotary compression element positively to supply with oily in cylinder from the oil supply that is formed on the intermediate clapboard.
Thus, the lubricated of second rotary compression element can be positively carried out, the raising with reliability guaranteed of performance can be realized.Particularly can constitute oil supply, therefore, can make simple structureization, can suppress the raising of cost of production owing to only carry out groove processing by face to second cylinder side of intermediate clapboard.
Description of drawings
Fig. 1 is the sectional arrangement drawing of rotary compressor of the present invention.
Fig. 2 is the front view of the rotary compressor of Fig. 1.
Fig. 3 is the side view of the rotary compressor of Fig. 1.
Fig. 4 is another sectional arrangement drawing of the rotary compressor of Fig. 1.
Fig. 5 is the another sectional arrangement drawing of the rotary compressor of Fig. 1.
Fig. 6 is the electrodynamic element top plan view partly of the rotary compressor of Fig. 1.
Fig. 7 is the amplification profile of rotary compressor structure portion of the rotary compressor of Fig. 1.
Fig. 8 is the expansion sectional drawing of blade-section of second compression unit of the rotary compressor of Fig. 1.
Fig. 9 is the lower support member of rotary compressor of Fig. 1 and the sectional drawing of lower cover.
Figure 10 is the worm's eye view of lower support member of the rotary compressor of Fig. 1.
Figure 11 is the upper support member of rotary compressor of Fig. 1 and the top figure of upper cap.
Figure 12 is the upper support member of rotary compressor of Fig. 1 and the sectional drawing of upper cap.
Figure 13 is the top figure of intermediate clapboard of the rotary compressor of Fig. 1.
Figure 14 is the A-A sectional drawing of Figure 13.
Figure 15 is the top figure of upper cylinder of the rotary compressor of Fig. 1.
Figure 16 is the figure of pressure oscillation of suction side of upper cylinder of the rotary compressor of presentation graphs 1.
Figure 17 is the sectional drawing of shape of joint of rotating shaft that is used for the rotary compressor of explanatory drawing 1.
Figure 18 has been to use the refrigerant circuit figure of hot watering supply device of the rotary compressor of Fig. 1.
Figure 19 is other embodiment's the amplification profile of blade-section of second rotary compression element of the rotary compressor of Fig. 1.
Figure 20 is the support member of second rotary compression element of rotary compressor of prior art and the sectional drawing of cover.
Figure 21 is the sectional drawing of explanation state of connector and joint on the pipe arrangement that connects airtight experiment usefulness on the sleeve pipe of the rotary compressor of Fig. 1.
Figure 22 is the figure of relation of the amount of deformation of the section of wiring terminal part of rotary compressor of presentation graphs 1 and end cap.
Figure 23 is the figure of relation of the amount of deformation of the section of wiring terminal part of rotary compressor of expression prior art and end cap.
Figure 24 is the wiring terminal amplification profile partly of the rotary compressor of Fig. 1.
Figure 25 is the amplification profile of the rotary compressor when the thin wiring terminal of assembly department has been installed.
Figure 26 is the sectional arrangement drawing of the rotary compressor of another embodiment of the present invention.
Figure 27 is the sectional arrangement drawing of the rotary compressor of another embodiment of the present invention.
Figure 28 is the figure of erection sequence of sleeve pipe of the rotary compressor of explanatory drawing 1.
Figure 29 is the figure of processing method of suction port of second rotary compression element of the rotary compressor of explanatory drawing 1.
Figure 30 is the figure of processing method of exhaust port of second rotary compression element of the rotary compressor of explanatory drawing 1.
Figure 31 be the explanation prior art the figure of processing method of suction port of second rotary compression element of rotary compressor.
Figure 32 be the identical prior art of explanation the figure of processing method of exhaust port of second rotary compression element of rotary compressor.
Figure 33 has been to use the refrigerant circuit figure of the hot watering supply device of another embodiment of the present invention.
Figure 34 has been to use the refrigerant circuit figure of another embodiment's of the present invention hot watering supply device.
Figure 35 is the top figure of upper support member of the rotary compressor of additional embodiments of the present invention.
Figure 36 is the upper support member of Figure 35 and the sectional drawing of loam cake.
Figure 37 is other embodiment's the sectional arrangement drawing of rotary compressor of the present invention.
Figure 38 is another sectional arrangement drawing of the rotary compressor of Figure 37.
Figure 39 is the electrodynamic element top plan view partly of the rotary compressor of Figure 37.
Figure 40 is the sectional arrangement drawing of the rotary compressor of another embodiment of the present invention.
Figure 41 is the sectional drawing of intermediate clapboard of the rotary compressor of Figure 40.
Figure 42 is the plan view of upper cylinder 38 of the rotary compressor of Figure 40.
Figure 43 is the figure of the pressure oscillation in the upper cylinder of rotary compressor of expression Figure 40.
Figure 44 is the figure of suction-compression stroke of refrigeration agent of upper cylinder of the rotary compressor of explanation Figure 40.
Figure 45 is the explanatory drawing that expression another refrigerating plant of the present invention constitutes.
Figure 46 is the explanatory drawing of formation of the oil separator of the expression refrigerating plant that is used in Figure 45.
Figure 47 is the explanatory drawing of formation of the compressor of the expression refrigerating plant that is used in Figure 45.
Figure 48 is the explanatory drawing that is illustrated in the formation of the compressor that uses in the refrigerating plant of prior art.
Embodiment
Below, describe embodiments of the invention with reference to the accompanying drawings in detail.
In each figure, the 10th, with carbon dioxide (CO 2) rotary compressor (motor compressor of sealed mode) of bosom die mould multistage (secondary) compression type that uses as refrigeration agent, this rotary compressor 10 is by seal container 12 cylindraceous, electrodynamic element 14, rotary compressor structure portion 18 constitutes, this rotary compressor structure portion 18 is made of first rotary compression element 32 (first order) and second rotary compression element 34 (second level), this seal container 12 is made of steel plate, above-mentioned electrodynamic element 14 configurations are accommodated in the upside of the inner space of above-mentioned seal container 12, above-mentioned first compression unit 32 (first order) and second rotary compression element 34 (second level) are configured in the downside of above-mentioned electrodynamic element 14, and are driven by the rotating shaft 16 of electrodynamic element 14.The high-precision size of embodiment's rotary compressor 10 is 220mm (external diameter 120mm), the height dimension of electrodynamic element 14 is 80mm (external diameter 110mm), the height dimension of rotary compressor structure portion 18 is about 70mm (external diameter 110mm), and electrodynamic element 14 is about 5mm with rotary compressor structure portion 18 at interval.In addition, the eliminating volume settings of second rotary compression element 34 must be littler than the eliminating volume of first rotary compression element 32.
In an embodiment, seal container 12 is that the steel plate of 4.5mm constitutes by thickness, with the bottom as oil storage portion, constitute by the vessel 12A cylindraceous that accommodates electrodynamic element 14 and rotary compressor structure portion 18 and roughly bowl-shape end cap (lid) 12B of the upper opening of this vessel of sealing 12A, and, be formed centrally circular mounting hole 12D on this end cap 12B, the wiring terminal parts (omission distribution) 20 that are used for to electrodynamic element 14 supply capabilities are being installed in this mounting hole 12D.
At this moment, on the end cap 12B around the wiring terminal parts 20, be the stepped part 12C that the axisymmetric shape at center is forming regulation curvature annularly with central shaft with this end cap 12B by drawing.In addition, wiring terminal parts 20 by the glass portion 20A of the circle that electrical end 139 penetratingly is installed shown in Figure 24 and be formed on this glass portion 20A around to oblique outer below stretch out flange shapely iron (the assembly department 20B formation of S25C～S45C), the central shaft that it also is with end cap 12B is the axisymmetric shape in center.The thickness size of assembly department 20B is the scope (the above 2.9mm of 1.9mm is following) of 2.4 ± 0.5mm.And, wiring terminal parts 20 insert mounting hole 12D with this glass portion 20A and face with upside from downside, by under with the periphery state of contact of assembly department 20B and mounting hole 12D, assembly department 20B being welded on the mounting hole 12D periphery of end cap 12B, be fixed on the end cap 12B.
At this, pressure in the seal container 12 is set at middle pressure the described later, when making the thin thickness of assembly department 20B of wiring terminal parts 20, following test effect is arranged in test, when thinner than 1.9mm, intensity (withstand voltage properties) deficiency of the high pressure of the refrigerant gas in the antagonism seal container 12 (the middle pressure) produces be full of cracks at assembly department 20B from one's body.In addition, when the thickness that makes assembly department 20B is thicker than 2.9mm, need a large amount of heats in the time of at this moment on being welded on seal container 304, might produce bad influence glass portion 20A.
In the present invention, in view of this, become 2.4 ± 0.5mm, can guarantee the withstand voltage properties of wiring terminal parts 20 fully, and can suppress to weld the increase of fixing needed heat by thickness with the assembly department 20B of wiring terminal parts 20.
In addition, end cap 12A is subjected to the influence of the high pressure (the middle pressure) in the seal container 12, and it is out of shape with the direction that the welding portion of wiring terminal parts bloats toward the outer side.Result with the end cap 12A amount of deformation of different region representation actual measurement Figure 22.In the figure, the amount of deformation in the zone of representing with Z1 is 0.05 μ m, and the amount of deformation in the zone of representing with Z2 is 0.2 μ m, and the amount of deformation in the zone of representing with Z3 is 0.25 maximum μ m.This is the result who the rigidity of the end cap 12A the wiring terminal parts 20 near is uprised owing to stepped part 12C, and it is compared with the amount of deformation of the end cap of aforesaid prior art is minimum value.
In addition, wiring terminal parts 20 in the center fixation of roughly bowl-shape end cap 12A, stepped part 12C also is formed on around it, and thus, it is the concentric circles at center that amount of deformation itself is distributed as with wiring terminal parts 20 equably.
Thus, in the present invention, with CO 2Gas compresses as refrigeration agent, under the situation that the pressure in the seal container 12 uprises, can reduce the amount of deformation by the next end cap 12A of the interior pressure zone of seal container 12, can improve its resistance to pressure.In addition, can make distortion homogenization by the end cap 12A of the welding portion of the wiring terminal parts 20 of cutting down output living in the seal container 12A, thereby can possibly avoid the be full of cracks of the welding portion that causes by inhomogeneous deformation and peel off, can further improve its resistance to pressure.
In addition, electrodynamic element 14 is made of stator 22 and rotor 24, and this stator 22 is mounted along the inner peripheral surface of the upper space of seal container 12 annularly, and this rotor 24 is provided with plurality of gaps ground and inserts the inboard that is configured in this stator 22.This rotor 24 is fixed on by the center along in the rotating shaft 16 of vertical extension.
Stator 22 has duplexer 26 and stator coil 28 (Fig. 6), and this duplexer 26 is formed by the electromagnetic steel plate of stacked ring-type, and this stator coil 28 installs around the tooth portion at this duplexer 26 by string around (concentrate around) mode.In addition, rotor 24 is also formed by the duplexer 30 of electromagnetic steel plate in the same manner with stator 22, inserts permanent magnet MG in this duplexer 30.
Intermediate clapboard 36 in clamping between above-mentioned first rotary compression element 32 and second rotary compression element 34.That is, first rotary compression element 32 and second rotary compression element 34 are by intermediate clapboard 36; Be configured in the less cylinder 38 (second cylinder) of the wall ratio of this intermediate clapboard about in the of 36, cylinder 40 (first cylinder); In the pressing chamber 38A of this upper and lower air cylinders 38,40 (Figure 15), 40A, be entrenched in have 180 degree phase differences ground be located at last eccentric part 42 (second eccentric part) in the rotating shaft 16, down eccentric part 44 (first eccentric part) and carry out that off-centre rotates on roll 46 (second rolls), roll 48 (first rolls) down; With this roll up and down 46,48 contact and will be divided into respectively in the upper and lower air cylinders 38,40 blade 50 (the downside blade is not shown) up and down described later of low pressure chamber side and hyperbaric chamber side; The open lower side face of sealing upside opening surface of upper cylinder 38 and lower cylinder 40 and the upper support member 54 and the lower support member 56 of support member that is also used as the bearing of rotating shaft 16 constitute.
On upper cylinder 38, forming the suction port 161 that rises obliquely from the edge portion of above-mentioned pressing chamber 38A, be formed obliquely exhaust port 184 in the edge portion of pressing chamber 38A at the opposite side that clips blade 50 as illustrated in fig. 15 with this suction port 161.In addition, on lower cylinder 40, also forming the suction port 162 that rises sideling from the edge portion of compressor 40A, and, clipping the opposite side of above-mentioned blade with this suction port 162, the exhaust port (figure does not show) that forms sideling in the edge portion of pressing chamber 40A.
In addition, on upper support member 54, form suction path 58 and drain passageway 39 respectively, on lower support member 56, forming suction path 60 and drain passageway 41 respectively.At this moment, above-mentioned suction port 161,162 is corresponding with each suction path 58,60, and each sucks path 58,60 and is communicated with pressing chamber 38A, the 40A of cylinder 38,40 inside respectively by this suction port 161,162.In addition, above-mentioned exhaust port 184 and each drain passageway 39,41 corresponding (, not shown) for cylinder 40, by this exhaust port 184 respectively with being communicated with of pressing chamber 38A, the 40A of upper and lower air cylinders 38,40 inside.
On upper support member 54 and lower support member 56, also forming the discharge anechoic chamber 62,64 of depression, and this two opening portion of discharging anechoic chamber 62,64 is inaccessible by lid respectively.That is, discharge anechoic chamber 62, discharge anechoic chamber 64 by lower cover 68 sealings as lid by upper cap 66 sealings as lid.
At this moment, erect in the central authorities of upper support member 54 and to form bearing 54A, the lining 122 of tubular is installed on the inner face of this bearing 54A.In addition, connect in the central authorities of lower support member 56 and to form bearing 56A, following (with the face of lower cylinder opposite side) of lower support member 56 forms tabular surface, and, the lining 123 of tubular also is installed on bearing 56A inner face.This lining 122,123 is made of the good material of sliding wear resistance described later, and rotating shaft 16 remains on the bearing 56A of the bearing 54A of upper support member 54 and lower support member 56 by these linings 122,123.
At this moment, lower cover 68 is made of the circular steel plate of annular, and by metal processing, punch process, cutting etc. its attachment face to lower support member 56 being processed as planeness is below the 0.1mm.And, lower cover 68 is fixed on the lower support member 56 from following four positions with its periphery by the kingbolt 129... that with bearing 56A is middle heart concentric circles configuration, seals the lower aperture portion of the discharge anechoic chamber 64 that is communicated with the pressing chamber 40A of the therapeutic method to keep the adverse qi flowing downward 40 inside of first rotary compression element 32 with drain passageway 41.The front end screw thread of this kingbolt 129... is combined on the upper support member 54.The inner circumference edge of lower cover 68 is inwardly being given prominence to the side from the bearing 56A inner face of lower support member 56, and thus, the lower end surface of lining 123 (with the end of the opposition side of lower cylinder 40) kept by lower cover 68, prevents that it from coming off.
Thus, need be in the anti-avulsion shape of the underpart shaping lining 123 of the bearing 56A of lower support member 56, thus make the simple shapeization of lower support member 56, can realize the reduction of cost of production.In addition, Figure 10 represent lower support member 56 below, the 128th, the expulsion valve of first rotary compression element 32 of switching drain passageway 41 in discharging anechoic chamber 64.
At this, lower support member 56 is made of the burn-back material (also can be mo(u)lding) of iron system, the face of the side that lower cover 68 will be installed (below) be processed as flatness be below the 0.1mm after, apply steam treated.Make the face of the side that lower cover 68 is installed become iron oxide by this steam treated, so the hole of agglomerated material inside is blocked, thereby has improved its sealing.Thus, need between lower cover 68 and lower support member 56, not press from both sides and establish sealing gasket.
In addition, electrodynamic element 14 sides of discharging the upper cap 66 in anechoic chamber 64 and the seal container 12 are being communicated with (Fig. 4) by the intercommunicating pore 63 as the hole of perforation upper and lower air cylinders 38,40 and intermediate clapboard 36.At this moment, the upright centre discharge tube 121 of establishing in the upper end of intercommunicating pore 63, this centre discharge tube 121 points to the gap (Fig. 6) of 28,28 of adjacent stator coils, and this stator coil 28,28 installs around on the stator 22 of electrodynamic element 14 up.
In addition, upper cap 66 inaccessible top opening portions (opening portions of electrodynamic element 14 sides) of discharging anechoic chamber 62, this discharge anechoic chamber 62 is communicated with by the pressing chamber 38A of drain passageway 39 with upper cylinder 38 inside of second rotary compression element 34, will be divided in the seal container 12 and discharge anechoic chamber 62 and electrodynamic element 14 sides.This upper cap 66 its thickness as shown in figure 11 is the above 10mm of 2mm following (is 6mm preferably at present embodiment), constitute by the circular steel plate of roughly ring-type that is forming the hole that the bearing 54A that supplies above-mentioned upper support member 54 connects, and upper support member 54 between clip under the state of the packing ring 124 that has stiffening rib by this packing ring 124 by 4 kingbolt 78... its periphery from being fixed on the upper support member 54.The front end of this kingbolt 78... is combining with lower support member 56 screw threads.
At this, with the thickness of upper cap 66 when experimentizing than 2mm is thin, produced because the danger that the interior pressure of discharge anechoic chamber 62 is out of shape.In addition, become when thicker than 10mm at thickness size with upper cap 66, approaching above it with stator 22 (stator coil 8), become the result who jeopardizes insulation.In the present invention, by upper cap 66 being become aforesaid ranges of thicknesses size, can hold the pressure of anti-discharge anechoic chamber 62 than seal container 12 inner high voltages fully, the miniaturization of rotary compressor 10 own can be realized simultaneously, insulation distance can be guaranteed with electrodynamic element 14.In addition, between the outside of interior all end faces of this upper cap 66 and bearing 54A, be provided with O V-shaped ring 126 (Figure 12), by carrying out the sealing of bearing 54A side by this O V-shaped ring 126, can seal fully by interior all end faces of upper cap 66, prevent gas leakage, when having realized discharging the volume expansion of anechoic chamber 62, do not need as original, to be fixed on the bearing 54A by the inner side edge portion of O V-shaped ring with upper cap 66 yet.At this, in Figure 11, the 127th, the expulsion valve of second rotary compression element 34 of switching drain passageway 39 in discharging anechoic chamber 62.
At this, the suction port 161 of above-mentioned upper cylinder 38 (lower cylinder 40 is also identical) and the processing method of exhaust port 184 are described with Figure 29 and Figure 30.When forming suction port 161, the end mill ML1 that front end is smooth vertically is close to cylinder 38 as the arrow that hangs down among Figure 29, keeping the direction that the relative like that cylinder 38 of the arrow of oblique left bottom tilts in Figure 29 under the state of this plumbness to make end mill ML1 move to pressing chamber 38A, thus, on cylinder 38, form the groove of inclination.
In addition, when forming exhaust port 184, as shown in figure 30, half the relative cylinder 38 of the end mill ML2 by end toper before making vertically press cylinder 38 pressing chamber 38A edge portion and on cylinder 38, form the breach of inclination.
By processing suction port 161 and exhaust port 184 in this wise, on cylinder 38, form the suction port 161 and the exhaust port 184 of inclination under can be again that the relative cylinder of end mill ML1, ML2 38 is the vertical state, therefore can be in the operation identical with the boring processing of such other screw hole H1 (wearing the hole of kingbolt 78 grades) of Figure 15 and lightening hole H2 etc. formation suction port 161 and exhaust port 184, can reduce operation quantity, thereby can reduce production costs.
Particularly, when being suction port 161, because by such processing, also the edge portion of suction path 58 sides of suction port 161 can be formed the semicircle arcuation as illustrated in fig. 15 by the end mill ML1 of preceding Transverse plane, therefore, the edge portion such with the past is comparing of straight line shape, can alleviate the passage resistance of the connected part of suction port 161 and suction path 58, thereby the disorder that reduces air-flow can realize high efficiency running.
Below, in the intermediate clapboard 36A of the opening surface of the upside of the open lower side face of inaccessible upper cylinder 38 and lower cylinder 40, in the position corresponding such as Figure 13, shown in Figure 14 from the outer circumferential face to the inner peripheral surface, wear the through hole 131 that is communicated with outer circumferential face and inner peripheral surface and constitutes the fuel feeding road by pore processing with the suction side in the upper cylinder 38, the opening 13,14 of plugging material (blocking pin) the 132 obstruction outer circumferential face sides of the outer circumferential face side by being pressed into this perforations road 131.In addition, the middle part at this through hole 131 is wearing the intercommunicating pore (vertical hole) 133 that extends to upside.
In addition, wearing the intercommunicating pore 134 of the injection usefulness that is communicated with the intercommunicating pore 133 of intermediate clapboard 36 at the suction port 161 (suction side) of upper cylinder 38.And, in rotating shaft 16, as shown in Figure 7, be formed centrally the oilhole 80 of vertical and the horizontal oil supply hole 82,84 that is communicated with this oilhole 80 (on the eccentric part up and down 42,44 of rotating shaft 16, also forming) in the axle of edge.The perforate of the inner peripheral surface side of the through hole 131 of intermediate clapboard 36 is being communicated with oilhole 80 by these oil supply holes 82,84.
Owing to be middle the pressure as described later in the seal container 12, supply oily in place, the second level becomes the upper cylinder 38 of high pressure becomes difficulty, but by intermediate clapboard 36 is formed such structure, suct and enter intermediate clapboard 36 through holes 131 from the store oil portion of seal container 12 inner bottom parts, supply to the suction side (suction port 161) of upper cylinder 38 from intercommunicating pore 133,134 along oilhole 80 oil that comes out from oil supply hole 82,84 that rises.
Among Figure 16, L represents the pressure oscillation of the suction side in the upper cylinder 38, P1 among the figure represents the pressure in the intermediate clapboard 36, shown in the L1 of this figure, the suction side pressure of upper cylinder 38 (suction pressure), in suction process because suction pressure loss and lower than the pressure of the inner peripheral surface side of intermediate clapboard 36.In the meantime, from the oilhole 80 of rotating shaft 16 through the through hole 131 of intermediate clapboards 36, intercommunicating pore 133 and from the intercommunicating pore 134 of upper cylinder 38 with oil spurts in upper cylinder 38, finish fuel feeding.
As mentioned above, upper and lower air cylinders 38,40, intermediate clapboard 36, up and down support member 54,56 and upper and lower covers 66,68 respectively by 4 bolt 78... and kingbolt 129... from affixed up and down, and upper and lower air cylinders 38,40, intermediate clapboard 36, support member 54,56 is also by the auxiliary bolt 136,136 affixed (Fig. 4) that is positioned at these kingbolt 78,129 outsides up and down.These auxiliary bolts 136,136 insert from upper support member 54 sides, on the lower support member 56 of its front end screw thread combination.
In addition, this auxiliary bolt 136 be positioned at above-mentioned blade 50 guide slot described later 70 near, make rotary compressor structure portion 18 integrated by appending this auxiliary bolt 136, Tightening moment increases, prevent from gas leakage such as to reach between the upper cylinder 38 of second rotary compression element 34 of 12MPa and the upper support member 54, can realize inside is become the sealing of the parts of extra-high voltage from head pressure.In addition and since the guide slot 70 of auxiliary bolt 136 fastening blades 50 near, therefore also can prevent back pressure (high pressure) gas leakage (from leakage between upper support member 54 and the upper cylinder 38) on the blade 50 of being added in as described later.
In addition, the outside that is forming the guide slot 70 of taking in above-mentioned blade 50 and be positioned at this guide slot in upper cylinder 38 is used to take in the container 70A as the spring 76 of spring component, and this container 70A is at guide slot 70 sides and seal container 12 (vessel 12A) side opening (Fig. 8).Above-mentioned spring 76 contacts with the outboard end of blade 50, frequently blade 50 is suppressed to rolling 46 sides.And, in the container 70A of seal container 12 sides of this spring 76, be provided with metal stopper 137, play the anticreep effect of spring 76.Back pressure chamber not shown in the figures is being communicated with guide slot 70, because the head pressure (high pressure) of second rotary compression element 34 is added on the blade 50, therefore, spring 76 sides of stopper 137 become high pressure, presses in the middle of seal container 12 sides become.
At this moment, the outside dimension of stopper 137 is littler than the inside dimension of container 70A, be inserted in the accommodation chamber 70A to stopper 137 Spielpassung, in addition, at the O type seal ring 138 that is installed with on the side face of stopper 137 between the inner face that is used to seal this stopper 137 and container 70A.And, the outer end of upper cylinder 38, be that interval between the vessel 12A of the outer end of container 70A and seal container 12 is littler than the distance of the end of seal container 12 sides from O type seal ring 138 to stopper 137.And, with not shown back pressure chamber that the guide slot 70 of blade 50 is communicated with in apply second rotary compression element as back pressure head pressure be high pressure.Therefore spring 76 sides of stopper 137 become high pressure, press in the middle of seal container 12 sides become.
By constituting such size relationship, can possibly prevent as stopper 137 is pressed into situation about being fixed in the 70A of container, upper cylinder 38 distortion, and upper support member 54 between the sealing step-down and bring the problem of mis-behave etc.In addition, even such Spielpassung, owing to the interval of 12 of upper cylinder 38 and seal containers is set at littler than the distance of the end of seal container 12 sides from O type seal ring 138 to stopper 137, therefore, owing to the high pressure (back pressure of blade 50) of spring 76 sides makes stopper 137 move to the direction that is pushed out from container 70A, the moment that stops it to move contacting with seal container 12, O type seal ring 138 also still is positioned at container 70A and seals, therefore, stopper 138 functions can not produce any problem.
Connection is formed on the mutual joint 90 of eccentric part up and down 42,44 on the running shaft 16 with the phase differences of 180 degree and has rigidity for its shape of cross section is made greatly than the cross-section area of the circular cross section of rotating shaft 16, therefore form it into the so-called rugby ball shape of non-circular shape as shown in figure 17, form the big shape (the hatching part among the figure) of wall thickness that side's wall ratio vertical with the eccentric direction of eccentric part 42,44 up and down is located at the eccentric direction of the eccentric part up and down 42,44 in the rotating shaft 16.
Thus, increased and connect the cross-section area that is located at 42,44 joints 90 of eccentric part up and down in the rotating shaft 16 integratedly, second moment of area increases, and intensity (rigidity) increases, and has improved the durability and the reliability of rotating shaft 16.Particularly as embodiment during the high refrigeration agent of two stage compression working pressure, because the pressure difference of high low pressure is big, the load that is applied in the rotating shaft 16 also becomes greatly, but increases its intensity (rigidity) by the cross-section area that increases joint 90, therefore can prevent rotating shaft 16 resiliently deformables.
In addition, under situation of the present invention, be made as at center the eccentric part 42 of upside O1, with the radius of this eccentric part be made as R1, with the center of the eccentric part 44 of downside be made as O2, when the radius of this eccentric part 44 is made as R3, the face (face in the left side of the shadow part of Figure 17) of the joint 90 of the eccentric direction side of the eccentric part of upside (first eccentric part) 42 becomes the circular shape of its center as O2, and the face of the joint 90 of the eccentric direction side of eccentric part 44 (face on the right side of the shadow part of Figure 17) becomes the circular shape of its center as O1.
In addition, when the radius of arc of the face of the joint 90 of the eccentric direction side of the eccentric part 42 of upside is made as R4, this radius R 4 can maximum extension to the radius R 3 of the eccentric part 44 of downside, when the radius of arc of the face of the joint 90 of the eccentric direction side of the eccentric part 44 of downside is made as R2, this radius R 2 can maximum extension to the radius R 1 of the eccentric part 42 of upside.
Like this, be set at O2 by center of arc with the face of the joint 90 of the eccentric direction side of the inclined to one side portion 42 of upside, the center of arc of the face of the joint 90 of the eccentric direction side of the eccentric part 44 of downside is set at O2, the eccentric part up and down 42 of cutting rotating shaft 16 on cutting machinery that rotating shaft 16 is installed, 44 when the joint 90, after having processed eccentric part 42, only change radius or do not change the face (face on the right side of Figure 17) of eccentric direction side of the eccentric part 44 of radius ground processing joint 90, then change the position that is installed, the face (face in the left side of Figure 17) of the eccentric direction side of the eccentric part 42 of processing joint 90 only changes radius or does not change the eccentric part 44 that radius ground processes joint 90.Thus, reduce the number of times of the rotating shaft 16 that is installed again, reduced manufacturing procedure, improved productivity significantly.
And, as at this moment refrigeration agent considered that the earth environment influence is little, back uses such as combustibility and toxicity be above-mentioned carbon dioxide (CO as an example of the carbonic acid gas of natural refrigeration agent 2), as the lubricant oil use is for example to be the existing oil of mineral oil, alkyl phenyl ring oil, ether oil, ester oil etc.
In addition, on the face of the bending of the vessel 12A of seal container 12, with the suction path 58,60 of upper support member 54 and lower support member 56, discharge to weld respectively on the relative position of the upside (position roughly corresponding) of anechoic chamber 62 and upper cap 66 and fixing sleeve pipe 141,142,143 and 144 cylindraceous with the lower end of electrodynamic element 14. Sleeve pipe 141 and 142 is neighbouring, and sleeve pipe 143 is on the roughly diagonal of sleeve pipe 141.Sleeve pipe 144 is positioned at sleeve pipe 141 and staggers roughly on the positions of 90 degree.
At this, the mounting construction of above-mentioned sleeve pipe 141～144 (representing sleeve pipe 142 in the drawings) is described with Figure 28.On the flexure plane of the vessel 12A of seal container 12, on the position of mounting sleeve 141～144, forming circular open-work 190 (at this moment being 4 positions) respectively, and, counterbit is being processed to form circular depressed part 192 around the exterior side of the vessel 12A of each open-work 190, in the bottom surface of this depressed part 192 be open-work 190 around forming the parallel tabular surface 193 of tangent line with the internal diameter of the vessel 12A of seal container 12.
In addition, on the end of seal container 12 sides of sleeve pipe 142 (other sleeve pipe is also identical), forming the insertion part 194 littler than external diameter diameter, around this insertion part 194, forming the axial vertical smooth abutting part 196 with sleeve pipe 142, also forming the projection 197 that projection welding is used on every side outstandingly at this abutting part 196.
In Figure 28, for convenience of explanation, represent projection 197 enlargedly, but be actually minimum outstanding size.In addition, the internal diameter of above-mentioned depressed part 192 is to have the size that minimum clearance ground can insert sleeve pipe 142, and the external diameter of insertion part 194 also is the size that can insert in the open-work 190 with having minimum clearance.
And, when being fixed on sleeve pipe 142 on the vessel 12A, the insertion part 194 of sleeve pipe 142 is inserted in the open-work 190 of vessel 12A, again abutting part 196 parts of sleeve pipe 142 are imbedded in the depressed part 192, so tabular surface 193 butts at the end of abutting part 196 of sleeve pipe 142 (being actually projection 197) and depressed part 192.At this moment, tabular surface 193 is parallel with the tangent line of the internal diameter of vessel 12A, and abutting part 196 and sleeve pipe 142 is axial vertical, therefore, in the moment that abutting part 196 has contacted with tabular surface 193, the internal diameter of sleeve pipe 142 relative vessel 12A becomes right angle (be arranged in from the mind-set radial direction of vessel 12A and extend and outstanding from the outside state).Particularly, therefore, can easily guarantee the perpendicularity of sleeve pipe 142 because the outside on every side of the abutting part 196 of lining 142 forms the form on the inner face that remains on depressed part 192.
Under this state, by not shown soldering appliance weld above-mentioned protruding 197 and with sleeve pipe 142 projection weldings on vessel 12A.By constituting in this wise, can under the situation of not using anchor clamps, correctly keep the perpendicularity of sleeve pipe 142 (141,143,144 is also identical) with respect to vessel 12A internal diameter.
And, in the sleeve pipe of installing in this wise 141, insert the refrigeration agent ingress pipe 92 (refrigerant pipes that connection is used to import refrigerant gas.The second refrigeration agent ingress pipe.) an end, an end of this refrigeration agent ingress pipe 92 is communicated with the suction path 58 of upper cylinder 38.(therefore, refrigeration agent ingress pipe 92 is positioned at outside the seal container 12 upside of this refrigeration agent ingress pipe 92 by seal container 12.) and arrive sleeve pipe 144, its other end insert be connected in the sleeve pipe 144 and with seal container 12 in are communicated with.
In addition, insertion is connecting the refrigeration agent ingress pipe 94 (refrigerant pipes that are used for importing to lower cylinder 40 refrigerant gas in sleeve pipe 142.The first refrigeration agent ingress pipe.) an end, an end of this refrigeration agent ingress pipe 94 is being communicated with the suction path 60 of lower cylinder 40.Insertion is connecting refrigerant discharge leader 96 in sleeve pipe 143 in addition, and an end of this refrigerant discharge leader 96 is communicated with discharge anechoic chamber 62.
Above-mentioned storage 146 is to suck the jar that refrigerant air-liquid separates, and the carriage 148 by memory side on the carriage 147 of the seal container side on the upper side of the vessel 12A that is welded on seal container 12 is being mounted.Be positioned at the top of sleeve pipe 141 and 142.These carriage 148 its both sides, underpart are fixed on the carriage 147 by bolt 181, extend upward from this carriage 147, use by both sides, bolt 183 end mounted thereto with the 182 substantial middle portions that keep the above-below direction of storagies 146.At this moment, storage 146 also can be by being weldingly fixed on the carriage 148.Under its state, storage 146 is being configured with the side form along seal container 12.
Like this, storage 146 is installed on the body 12A of seal container 12 by carriage 147 and carriage 148, therefore, capacity at storage 146 is extended, when size has also become greatly about it, just can under the state of the substantial middle that is keeping storage 146, its lower end position be lifted in following size up and down that enlarges (change) carriage 148 of the situation that does not change carriage 147.Thus, be difficult to interfere with its below refrigeration agent ingress pipe 92.
In addition, carriage 147 be when seal container 12 sprays paint, become the suspender of hanging manufacturing equipment draw extension portion, but, do not need the change of this suspender by making such formation yet.And, when the capacity change that has produced storage 146, also can only change carriage 148 as described above and carriage 148 is installed near its substantial middle (or basic position of centre of gravity or its), can keep storage 146 in its position, can prevent the noise increase that causes by vibration.
In addition, as shown in Figure 3, refrigeration agent ingress pipe 92 rises to right-hand crooked back after coming out from lining 141 in the present embodiment, and the lower end of storage 146 drops to the position approaching with this refrigeration agent ingress pipe 92.Therefore, the refrigeration agent ingress pipe 94 that descends from the lower end of storage 146 is bent into from sleeve pipe 141 and sees at and arrival sleeve pipe 142 circuitous with the crooked opposite left side of refrigeration agent ingress pipe 92.
Promptly the refrigeration agent ingress pipe 92,94 that is communicated with the suction path 58,60 of upper support member 38 and lower support member 40 respectively from seal container 12 see with on horizontal plane in the opposite direction (the different direction of 180 degree) crooked mode be provided with, thus, enlarged the size up and down of storage 146 and increased volume or by the decline mounting point with its lower end near refrigeration agent ingress pipe 92, also can make each refrigeration agent ingress pipe 92,94 phase mutual noninterference.
Around the outside of sleeve pipe 141,143,144, form lip part 151, around the outside of lining 142, forming thread groove 152.And, but on this lip part 151, engaging to clutch the connecting part 172 that pipe arrangement connects the joint 171 of usefulness as shown in figure 21, but screw thread is being fixed the joint 173 that pipe arrangement connects usefulness on thread groove 152.
In addition, the direction pressurized that the connecting part 172 of pipe joint 171 is escaped frequently toward the outer side in its arranged outside and to be had flexible operation unit 177.And, the mode by overlapping casing tube 141 push pipe joint 171 make connecting part 172 push open operation unit 177 fall back on outside the rear flank, combine with the vessel 12A side of lip part 151.In addition, move to the direction of leaving from vessel 12A by making operation unit 177, connecting part 172 falls back on the outside, and pipe joint 171 is unloaded from lining 141.
Aforementioned tube joint 171 is installed in the front end from the pipe arrangement 174 of pressurized air generating apparatus not shown in the figures, and joint 173 is installed in the front end from the pipe arrangement 176 of pressurized air generating apparatus similarly.And in the manufacturing process of rotary compressor 10, finish when checking, above-mentioned pipe joint 171 is connected with sleeve pipe 141,143,144 combinations respectively, screws in and jointing 173 on sleeve pipe 142.And, be added to from the above-mentioned pressurized air generating apparatus pressurized air that 10MPa is such and carry out air tightness test in the seal container 12.
By making such structure,, therefore can finish air tightness test at short notice owing to pipe arrangement 174, the 176 usefulness pipe joints 171 from the pressurized air generating apparatus can be connected simply with joint 173.Particularly neighbouring sleeve pipe 141 and 142 is by forming lip part 151 on a square casing 141, on the opposing party's lining 142, form thread groove 152, can not become two is adjacent to install and compares with joint 173, the situation of the pipe joint 171 that size is big is even also can utilize narrow space that pipe arrangement 174,176 is connected on each sleeve pipe 141,142 at the interval of sleeve pipe 141 and 142 when narrow.
Figure 18 is the refrigerant circuit figure that the hot watering supply device 153 of embodiments of the invention is used in expression.Embodiment's rotary compressor 10 is used in the refrigerant circuit of hot watering supply device shown in Figure 180 153.The refrigerant discharge leader 96 that is rotary compressor 10 is connected with the inlet of the gas cooler 154 of water heating usefulness.This gas cooler 154 is located on the thermal storage water tank not shown in the figures of hot watering supply device 153.The pipe arrangement that comes out from gas cooler 154 passes through the inlet that arrives vaporizers 157 as the expansion valve 156 of decompressor, and the outlet of vaporizer 157 is connected with refrigeration agent ingress pipe 94.In addition, white pipe 158 (not shown among Fig. 2, Fig. 3) that go from the middle part branch of refrigeration agent ingress pipe 94 constitutes defrost circuit are connected with the refrigerant discharge leader 96 that arrives the inlet of gas coolers 154 by the solenoid valve 159 as the stream control gear.In addition, in Figure 18, omitted storage 146.
The below action in the above formation of explanation.In adding heat run, solenoid valve 159 is cutting out, when by wiring terminal parts 20 and not shown distribution during to stator coil 28 energisings of electrodynamic element 14, and electrodynamic element 14 startings, rotor 24 rotations.Make to be entrenched in by this rotation and roll 46,48 eccentric rotations in upper and lower air cylinders 38,40 up and down on the eccentric part up and down 42,44 that is provided with integratedly with rotating shaft 16.
So, through refrigeration agent ingress pipe 94 and be formed on suction path 60 on the lower support member 56 be inhaled into from suction port 162 the low pressure chamber side of lower cylinder 40 low pressure (first order suction pressure LP:4MPa) refrigerant gas by roll 48 and the action of blade be compressed and press (MP1:8MPa) in the middle of becoming, be discharged in the seal container 12 from middle discharge tube 121 by access 63 from the discharge anechoic chamber 64 that is formed on the lower support member 56 through exhaust port, drain passageway 41 from the hyperbaric chamber side of lower cylinder 40.
At this moment, middle discharge tube 121 is owing to point to the gap of 28,28 of adjacent stator coils on the stator 22 that installs around electrodynamic element 14 up, therefore the refrigerant gas than lower temperature also can be fed to electrodynamic element 14 directions energetically, the temperature that suppresses electrodynamic element 14 rises.In addition, thus, press in the middle of becoming in the seal container 12 (MP1).
And the refrigerant gas of pressing in the middle of in the seal container 12 comes out (middle discharge press be above-mentioned MP1) via refrigeration agent ingress pipe 92 and be formed on suction path 58 on the upper support member 54 is inhaled into upper cylinder 38 from suction port 161 low pressure chamber side (second level sucks and presses MP2) from sleeve pipe 144.The refrigerant gas of pressing in the middle of being inhaled into since roll 46 and the action of blade 50 carry out the second level and compress, thereby become the refrigerant gas (second level discharge press HP:12MPa) of High Temperature High Pressure, from the hyperbaric chamber side by exhaust port 184 and drain passageway 39 again via being formed in discharge anechoic chamber 62 on the upper support member 54, the refrigerant discharge leader 96 inflow gas coolers 154.At this moment refrigerant temperature rises to+100 ℃, like this refrigerant gas of High Temperature High Pressure by gas cooler 154 heat radiations the water in the heating thermal storage water tank, thereby generate+90 ℃ water approximately.
In addition, in gas cooler 154, carry out refrigerant cools repeatedly, come out from gas cooler 154, then, evaporate (at this moment from heat absorption on every side) with expansion valve 156 decompression back inflow evaporators 157, be inhaled into circulation in first rotary compression element 32 from refrigeration agent ingress pipe 94 through storage 146 (not shown in Figure 18).
Particularly, in the environment of temperature,, long white on vaporizer 157 outside low by such heat run that adds.At that time, open solenoid valve 159, expansion valve 156 becomes full-gear, carries out the defrosting running of vaporizer 157.Thus, the middle refrigeration agent of pressing in the seal container 12 (containing a spot of high-pressure refrigerant of discharging from second rotary compression element 34) is by removing frost pipe 158 arrival gas coolers 154.The temperature of this refrigeration agent is+about 50～+ 60 ℃, in gas cooler 154, do not dispel the heat, and become the form of refrigeration agent heat absorption originally on the contrary.Then, the refrigeration agent that comes out from gas cooler 154 arrives vaporizer 157 by expansion valve 156.That is, become the form that can not be supplied directly onto vaporizer 157 with the temperature of pressing in the middle of roughly than higher refrigeration agent with being depressurized.Thus, vaporizer 157 is heated, and is defrosted.At this moment, the heat that becomes hot water is transported to forming of vaporizer 157 by refrigeration agent from gas cooler 154.
At this, make the high-pressure refrigerant of discharging from second rotary compression element 34 supply to vaporizer 157 when defrosting, because expansion valve 156 standard-sized sheets, the suction pressure of first rotary compression element 32 rises with not reducing pressure, thus, the head pressure of first rotary compression element 32 (the middle pressure) uprises.This refrigeration agent is discharged from by second rotary compression element 34, because expansion valve 156 standard-sized sheets, therefore it is identical with the suction pressure of first rotary compression element 32 that the head pressure of second rotary compression element 34 becomes, in the discharge (high pressure) of second rotary compression element 34 with suck generation pressure reverse phenomenon in (the middle pressure).But, carry out the defrosting of vaporizer 157 owing to take out the middle refrigerant gas of pressing of discharging from seal container 12 as described above from first rotary compression element 32, therefore, can prevent such high pressure and middle reverse phenomenon of pressing.
At this, Figure 33 is the other refrigerant circuit that hot watering supply device 153 of the present invention has been used in expression.In the figure, identical with Figure 18 symbol is the member that produces identical or equal effect.At this moment, another that also is provided with the pipe arrangement that is communicated with between refrigerant discharge leader 96 and expansion valve 156 and the vaporizer 157 except the refrigerant circuit of Figure 18 removes frost pipe 158A, goes to press from both sides on the frost pipe 158A at this and establishes another solenoid valve 159A.
In such formation, in adding heat run,, move same as described above owing to closing both sides' solenoid valve 159,159A.In addition, when vaporizer 157 defrostings, the both sides that open solenoid valve 159 and 159A.So a spot of high-pressure refrigerant that the refrigeration agent of pressing in the middle of in the seal container 12 is discharged from second rotary compression element 34 flows directly into vaporizer 157 through the downstream side that past frost pipe 158 and 158A flow to expansion valve 156 under the state that is not depressurized.Reverse by the so pressure that also can avoid in second rotary compression element 34 that constitutes.
In addition, Figure 34 represents the another refrigerant circuit of hot watering supply device 153.The symbol identical with at this moment Figure 18 is the member that produces identical equivalent effect.At this moment, the frost pipe 158 that goes among Figure 18 is not connected with the inlet of gas cooler 154, and is connected on the pipe arrangement between expansion valve 156 and the vaporizer 157.If adopt and make such formation, same with Figure 33 when having opened solenoid valve 159, the middle refrigeration agent of pressing in the seal container 12 flows to the downstream side of expansion valve 156, flows directly into vaporizer 157 under the state that is not depressurized.Thus, the pressure of second rotary compression element 34 that is produced when defrosting except not producing reverses, compare the advantage that also has the quantity that can reduce solenoid valve with Figure 33.
In addition, in the above-described embodiments, stopper 137 Spielpassung ground is inserted container 70A, but when joint 137 is pressed into container 70A as shown in figure 19, if on the upper support member 54 of the part corresponding, forming the 54C of the portion of keeping out of the way to the direction depression of leaving from upper cylinder 38 with this stopper 137, then can keep out of the way the 54C of portion and absorb the distortion be accompanied by the upper cylinder 38 that stopper is pressed into, can prevent degenerating of sealing by this.
In addition, in an embodiment,, sleeve pipe 141 and 142 are set neighbouringly, but also comprise the adjacent situation in the two sleeve pipe left and right sides as walking crosswise rotary compressor owing to be vertical shape rotary compressor.And at that time, refrigeration agent ingress pipe 92,94 upward with below or right-hand and leftwards arrange in the opposite direction.
In addition, in the above-described embodiments, to be discharged in the seal container 12 with the refrigerant gas of pressing in the middle of 32 compressions of first rotary compression element, but be not limited thereto, the refrigerant gas of discharging from first rotary compression element 32 can be discharged in the seal container 12 yet and be fed directly to refrigeration agent ingress pipe 92, be inhaled in second rotary compression element 34.
In the above-described embodiments, the refrigeration agent ingress pipe 92 of second rotary compression element 34 and the refrigeration agent of first rotary compression element 32 are set neighbouringly import 94, but be not limited thereto, the refrigerant discharge leader 96 of second rotary compression element 34 and the refrigeration agent ingress pipe 94 of first rotary compression element 32 also can be set neighbouringly.At this moment, refrigerant discharge leader 96 and refrigeration agent ingress pipe 94 are provided with around seal container in the opposite direction from seal container 12.
At this, Figure 26 represents the sectional drawing of another rotary compressor 10 of the present invention.At this moment, forming bearing 54A in the central authorities of upper support member 54 (second support member), this bearing 54A is to the outstanding long bearing of electrodynamic element 14 directions, and the lining 122 of tubular is installed on this bearing 54A inner face with erecting.This lining 122 is clipped between rotating shaft 16 and bearing 54A.The inner face of this lining 122 is contacting with rotating shaft 16 with being free to slide.Lining 122 is that the high material with carbon element of wear resistance that is used in the sliding that also can keep good under the inadequate situation of fuel feeding constitutes.
In addition, connect in the central authorities of lower support member 56 and to form the bearing 56A shorter than bearing 54A, on this bearing 56A inner face lining is not installed, the inner face of bearing 56A directly contacts with rotating shaft 16 with being free to slide.Thus, rotating shaft 16 is maintained at by lining 122 on the bearing 56A of upper support member 54 in electrodynamic element 14 sides (upside) of rotary compressor structure portion 18, directly is being maintained on the bearing 56A of lower support member 56 with electrodynamic element 14 opposite sides (downside).T among the figure represents above-mentioned store oil portion.
In the running of such rotary compressor 10, the rotating shaft 16 of eccentric part 44 belows is slided in the bearing 56A of lower support member 56 on one side and is rotated on one side, but, since the pressure in the cylinder 40 of first rotary compression element 32 of the first order be in the seal container 12 in the middle of press below, therefore, by from enter 16 of bearing 56A and rotating shafts by memory section T, on sliding, do not have problems.
In addition, the cylinder 38 of partial second rotary compression element 34 is interior owing to be than high high pressure in the seal container 12, the bearing 54A of the upper support member 54 that the rotating shaft 16 of eccentric part 42 tops is rotated while sliding is interior owing to pressure difference is difficult to enter oil, but, in bearing 54A,, so on sliding, do not have problems because rotating shaft 16 is being located in the lining 122 of its inner carbon system is rotated while sliding.
And, in bearing 56A,, therefore can save the lining of comparison costliness because lining 122 is not set as described above, can realize the reduction of cost of parts.
At this, in the embodiment of Figure 26, in bearing 54A, be provided with lining 122, in bearing 56A, do not establish lining and reduced cost, but suction head pressure according to each compression unit, also can in bearing 56A, establish carbon system lining 123 as shown in figure 27 on the contrary and be clipped in bearing 56A and rotating shaft 16 between, in bearing 54A, do not establish lining.
According to such formation, while keep the load that compression area is little, per unit area bears that holds as minor axis to become the sliding capability of big bearing 56A and keep its durability, can realize the reduction of cost by the lining that saves the less bearing 54A of duty ratio that the big per unit area of compression area bears.
At this moment, the internal diameter of lower cover 68 is littler than the internal diameter of lower support member 56, and the lower edge by lower cover 68 maintenance linings 123 can prevent coming off of lining 123 thus.
In addition, Figure 35, Figure 36 represent other embodiment of above-mentioned support member 54.Figure 35 represents the plan view of upper support member 54 at this moment, and 186 is holes of passing above-mentioned kingbolt 78 among the figure, is formed on 4 positions with 90 intervals of spending in the outside of bearing 54A.In addition, the 187th, pass the hole of above-mentioned auxiliary bolt 136, be formed with two in the outside of hole 186....
In addition, discharging anechoic chamber 62 cuts apart chamber 62A, 62B, 62C, 62D by four in an embodiment and is used in series being communicated with mutually the narrow path 62E... of these width of cutting apart chamber 62A～62D (three places) formation.That is, cut apart chamber 62A and be communicated with by path 62E respectively with 62D with 62C, 62C, but do not have path between chamber 62A and the 62D cutting apart with 62B, 62B.
In addition, respectively cut apart chamber 62A～62D and path 62E... and be configured in the bearing 54A outside round the bearing 54A outside, cut apart chamber 62A～62D and be configured in 186,186 in adjacent respectively hole, path 62E... is configured in the bearing 54A side of hole 186....And what 39 pairs of above-mentioned drain passageways were positioned at an end cuts apart chamber 62A inner opening, and expulsion valve 127 is to be contained through the form that path 62E arrives 62A from cutting apart chamber 62B.In addition, the refrigerant passage 188 (refrigeration agent outflow portion) that is formed in the upper support member 54 is cut apart chamber 62D inner opening to what be positioned at the other end.This refrigerant passage 188 is being communicated with above-mentioned refrigerant discharge leader 96.
Respectively cut apart chamber 62A～62D and path 62E... by what anechoic chamber 62 was discharged in configuration in this wise, make and respectively cut apart chamber 62A～62D and be positioned at 78,78 of kingbolts, path 62E is positioned at the bearing 54A side of kingbolt 78.Thus, can utilize the space beyond the kingbolt 78... efficiently, can form thus discharge anechoic chamber 62 respectively cut apart chamber 62A～62D and the narrow path 62E... of width.
And refrigeration agent is discharged to cutting apart in the 62A of chamber of the discharge anechoic chamber 62 that is formed on the upper support member 54 by drain passageway 39 from the hyperbaric chamber side of upper cylinder 38.Flowing into this higher pressure refrigerant gas of cutting apart in the 62A of chamber comes out then to enter by the narrow path 62E of width and cuts apart chamber 62B from cutting apart chamber 62A.Then cutting apart chamber 62B from this then comes out then to enter by path 62E and cuts apart chamber 62C.Then, cutting apart chamber 62C from this comes out to enter at last by path 62E and cuts apart chamber 62D.Come out to enter refrigerant passage 188 from cutting apart chamber 62D then, by herein after flow in the coolers 154 by refrigerant discharge leader 96.
Like this, in embodiment's in this case the structure, be compressed in upper cylinder 38 inside, flow into the higher pressure refrigerant gas of discharging in the anechoic chamber 62 from drain passageway 39, owing to go out from refrigerant passage 188 after cutting apart chamber 62A～62D and being communicated with the narrow path 62E... of their width by a plurality of one by one, therefore the pulsation of refrigerant gas is absorbed noise and vibration in the time of can suppressing rotary compressor effectively effectively in by the process of respectively cutting apart the narrow path 62E... of chamber 62A～62D and width.
As detailed above, according to the present invention, by in seal container, being provided with electrodynamic element, in the rotary compressor that constitutes by the rotary compression element of this electrodynamic element driving, owing to comprise and rolling, blade, spring component, the container of spring component, stopper, the O RunddichtringO, above-mentioned roll on the eccentric part that is entrenched in the rotating shaft that forms with cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, being rotated prejudicially, above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, above-mentioned spring component is used for this blade is suppressed to rolling side frequently, above-mentioned spring constitutes the container and is formed in the cylinder, and to blade-side and seal container side opening, above-mentioned stopper is positioned at the seal container side of spring component and is inserted in the container with Spielpassung, above-mentioned O RunddichtringO is installed on the side face of stopper and is used to seal between this stopper and the container, therefore, can possibly prevent from sealing to be reduced stopper being pressed into cylinder deformation when being fixed in the container, the unfavorable condition of degradation.
In addition, even because above-mentioned Spielpassung, set the cylinder and the interval of seal container formula littler than the distance of the end of seal container side from the O RunddichtringO to stopper, therefore, move to the direction that is pushed out from the container at stopper, contact it with seal container and move the moment that is prevented from, the O RunddichtringO still is positioned at the container and is sealing, and therefore can not produce any problem to the function of stopper.
Be in the rotary compressor of middle multistage compression formula of pressing particularly, with CO in seal container inside 2Gas uses as refrigeration agent, press in the middle of in seal container being, when becoming extra-high voltage in second rotary compression element, for the performance of keeping compressor and prevent spring component deviate to have significant effect.
According to invention, owing in seal container, be provided with electrodynamic element, constitute in the rotary compressor by the rotary compression element of this electrodynamic element driving, comprise and rolling, support member, blade, spring component, the container of spring component, stopper, above-mentioned roll on the eccentric part that is entrenched in the rotating shaft that forms with cylinder that is used to constitute rotary compression element and electronic key element and in cylinder, being rotated prejudicially, above-mentioned support member, the opening surface of inaccessible cylinder, and bearing with running shaft, above-mentioned blade contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder with above-mentioned rolling, above-mentioned spring component is used for this blade is suppressed to rolling side frequently, above-mentioned spring constitutes the container and is formed in the cylinder, and to blade-side and seal container side opening, above-mentioned stopper is positioned at the seal container side of spring component and is pressed into and is fixed on the container; On the support member of the part corresponding, forming the portion that dodges towards the direction depression of leaving from cylinder with this stopper, therefore, even because stopper is pressed into the container, cylinder to the distortion of support member side with bloating, also can absorb the distortion of this cylinder by this portion of dodging, can avoid between cylinder and support member producing the bad phenomenon in gap, thus, can possibly avoid the reduction of the sealing brought owing to cylinder deformation to make the bad phenomenon of degradation.
Be in the rotary compressor of middle multistage compression formula of pressing particularly, with CO in seal container inside 2Gas uses as refrigeration agent, press in the middle of in seal container being, when becoming extra-high voltage in second rotary compression element, for the performance of keeping compressor and prevent spring component deviate to have significant effect.
In addition, the objective of the invention is in the rotary compressor of inside during with slick and sly and positively carry out to becoming the partial second rotary compression element fuel feeding for middle multistage compression of pressing.
In addition, the rotary compressor according to the present invention, owing in seal container, have electrodynamic element, first and second rotary compression elements by this electrodynamic element driving, to be discharged in the seal container by the gas of first rotary compression element compression, the intermediate pressure gas body that again this is discharged from comprises the cylinder that is used for constituting respectively each rotary compression element by this second rotary compression element compression, be folded in the intermediate section dividing plate that is used to separate each rotary compression element between each cylinder, seal the opening surface of each cylinder respectively and have the support member of the bearing of rotating shaft, be formed on the oilhole in the rotating shaft; The fuel feeding road that will be used to be communicated with the suction side of this oilhole and second rotary compression element is formed in the intermediate section dividing plate, even under the high situation of the pressure in the seal container of pressing in the middle of the pressure ratio therefore in the cylinder of second rotary compression element becomes, also can utilize the suction crushing in the suction process of second rotary compression element positively to supply with oil from the fuel feeding road direction cylinder that is formed in the intermediate section dividing plate.
Thus, the lubricated of second rotary compression element can be positively carried out, the raising with reliability guaranteed of performance can be sought.
In addition according to rotary compressor of the present invention, on the basis of the above, constitute the fuel feeding road owing in the intermediate section dividing plate, wear the through hole that is communicated with outer circumferential face and rotation shaft side inner peripheral surface, and the opening of the outer circumferential face side of sealing through hole, the intercommunicating pore that is communicated with this through hole and suction side is located in the cylinder that is used to constitute second rotary compression element, therefore, the processing transfiguration of intermediate section dividing plate that is used to constitute the fuel feeding road is easy, and cost of production is reduced.
According to rotary compressor of the present invention because first and second rotary compression elements that in seal container, have electrodynamic element, drive by this electrodynamic element, by first rotary compression element with compressed CO 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by the compression of this second rotary compression element, have the cylinder that is used to constitute the second rotation compression element, the opening surface that seals this cylinder and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, with bolt periphery be fixed on being used on the support member and seal the lid of the opening portion of discharge anechoic chamber; Between this lid and support member, sandwich sealing gasket, and between interior all end faces that cover and bearing outside, be provided with the O RunddichtringO, therefore, can on the bearing base portion, not form under the situation of sealing surface and seal fully by the interior all ends in the lid, prevent from cover and support member between gas leakage.
Thus, necessity was fixed on lid on the bearing by C type back-up ring as originally owing to the volume of having sought the discharge anechoic chamber enlarges not, therefore, also can realize the remarkable reduction of processing cost and cost of parts generally.
According to rotary compressor of the present invention because in seal container, have electrodynamic element, by first and second rotary compression elements that electrodynamic element drives, will be by the CO of first rotary compression element compression 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by the compression of this second rotary compression element, the opening surface of the electrodynamic element side of have the cylinder that is used to constitute the second rotation compression element, sealing this cylinder and central part have the bearing of the running shaft that erects support member, be formed on the discharge anechoic chamber that is communicated with cylinder interior on the support member in the bearing outside, be installed in being used on the support member and seal the lid of the opening portion of discharge anechoic chamber; The thickness size of this lid is set at below the above 10mm of 2mm, further be that the thickness size that will cover is set at 6mm, therefore in the intensity of having guaranteed lid itself, prevent gas leakage by its distortion generation in, can also guarantee and electrodynamic element between insulation distance, can realize the miniaturization of compressor.
In addition, according to rotary compressor of the present invention, in above-mentioned each invention, cover bolt is fixed on periphery on the support member, sandwiches sealing gasket between this lid and support member, and is provided with the O RunddichtringO between interior all end faces that cover and bearing outside.Therefore, can on the bearing base portion, not form under the situation of sealing surface and seal fully by the interior all ends in the lid, prevent from cover and support member between gas leakage.
Thus, necessity was fixed on lid on the bearing by C type back-up ring as originally owing to realized enlarging not by the volume of discharge anechoic chamber, therefore, also can realize the remarkable reduction of processing cost and cost of parts generally.
According to rotary compressor of the present invention because first and second rotary compression elements that in seal container, have electrodynamic element, drive by electrodynamic element, by first rotary compression element with compressed CO 2Refrigerant gas is discharged in the seal container, the intermediate pressure gas body that again this is discharged from is by this second rotary compression element compression, comprise the cylinder that is used for constituting respectively each rotary compression element, seal the opening surface of each cylinder respectively and have the support member of the bearing of running shaft in central authorities, be formed on the discharge anechoic chamber that is communicated with cylinder interior on each support member in the bearing outside, being installed in being used on each support member seals the lid of the opening portion of discharging the anechoic chamber respectively, by affixed each cylinder of a plurality of kingbolts, each support member and each lid, and by affixed each cylinder of auxiliary bolt and each support member that are positioned at the kingbolt outside, therefore can prevent to improve sealing from gas leakage such as between the cylinder of second rotary compression element that becomes high pressure and support member.
According to the present invention, since have on the basis of the above roll, blade, guide slot, above-mentioned roll on the eccentric part that is entrenched on the running shaft that is formed at electrodynamic element and eccentric rotation in the cylinder that constitutes second rotary compression element, above-mentioned blade rolls with this and contacts and will be divided into low pressure chamber side and hyperbaric chamber side in the cylinder, and above-mentioned guide slot is formed on and is used to take in blade on the cylinder; Auxiliary bolt is positioned near the guide slot, therefore, can be prevented to be applied to the gas leakage of the back pressure on the blade by auxiliary bolt effectively.
According to the present invention, owing in seal container, have electrodynamic element, first and second rotary compression element by this electrodynamic element driving, by the gas of second rotary compression element compression with the compression of first rotary compression element, having first and second rolls, this first and second roll on chimeric first and second eccentric part, this first and second eccentric part is formed at with having 180 degree phase differences and is used to constitute first and second cylinder of first and second rotary compression element and the rotating shaft of electrodynamic element, the section configuration that connects the joint of two eccentric parts is formed the big shape of wall thickness of comparing the direction vertical with the wall thickness of the eccentric direction of two eccentric parts with this eccentric direction, therefore, improve the rigidity intensity of running shaft, can prevent its resiliently deformable effectively.
Particularly, because the side of the eccentric direction side of first eccentric part of this joint is formed and the concentric circular shape of second eccentric part, the side of the eccentric direction side of second eccentric part forms and the concentric circular shape of first eccentric part, therefore when cutting has the rotating shaft of two eccentric parts and joint, can reduce the number of times that changes holding position.Thus, can reduce manufacturing procedure, can realize the raising of manufacturing efficiency, and then can realize that cost reduces.
According to rotary compressor of the present invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside by refrigerant discharge leader, has the sleeve pipe that connects refrigeration agent ingress pipe and refrigerant discharge leader respectively that is located on the seal container, external surface peripheral at this sleeve pipe is forming the lip part that is used for connecting in conjunction with pipe arrangement the connector of usefulness, therefore, utilize this lip part will be located at joint on the pipe arrangement that comes from the pressurized air generating apparatus simply in conjunction with being connected on the sleeve pipe of seal container.
Thus, can finish inside at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
According to the rotary compressor of this invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside by refrigerant discharge leader, has the sleeve pipe that connects refrigeration agent ingress pipe and refrigerant discharge leader respectively that is located on the seal container, external surface peripheral at this sleeve pipe is forming the thread groove that pipe arrangement connects usefulness, therefore utilizes this thread groove the pipe arrangement from the pressurized air generating apparatus can be connected on the sleeve pipe of seal container simply.
Thus, can finish inside at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
According to rotary compressor of the present invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, the CO that sucks from the refrigeration agent ingress pipe with the compression unit compression 2Refrigeration agent also is discharged in the seal container, be discharged to the outside by refrigerant discharge leader, have a plurality of sleeve pipes that connect refrigeration agent ingress pipe and refrigerant discharge leader respectively that are located in the seal container, external surface peripheral at an adjacent square casing is forming the lip part that is used for connecting in conjunction with pipe arrangement the joint of usefulness, external surface peripheral at the opposing party's sleeve pipe is forming the thread groove that pipe arrangement connects usefulness simultaneously, therefore utilize and to utilize this thread groove the pipe arrangement from the pressurized air generating apparatus can be connected on the sleeve pipe of seal container simply with the joint on the pipe arrangement that is located at from the pressurized air generating apparatus simply in conjunction with being connected on the sleeve pipe of seal container.Can finish inside thus at short notice and be the air tightness test in the manufacturing technology of the compressor of the sealed mode of high pressure.
Particularly owing on an adjacent square casing, forming lip part, on the opposing party's sleeve pipe, forming thread groove, therefore can not be adjacent to Conncetion cimension ratio joint significantly mutually, can utilize a plurality of pipe arrangements of this narrow space connection when the interval between sleeve pipe is narrow yet from the pressurized air generating apparatus.
According to rotary compressor of the present invention, because the compression unit that in seal container, has electrodynamic element, drives by this electrodynamic element, have vessel side carriage, storage on the container side of being located at, the memory side carriage of this storage is installed, by this memory side carriage is fixed on the vessel side carriage, by two carriages storage is installed on the container, therefore, can be under the situation that does not change the seal container lateral bracket when changing the capacity of storage, only need to change the memory side carriage and get final product, thereby can prevent interference with pipe arrangement.Therefore, also eliminated influence for the manufacturing equipment of compressor.
In addition, even when the capacity of storage has produced variation, only need change transition storage lateral bracket, near the installation memory side carriage central authorities of storage or position of centre of gravity or them, promptly can be near the central authorities of storage or position of centre of gravity or them this storage of maintenance, can prevent to vibrate the increase of the noise that causes.
According to the present invention, because its compressor has electrodynamic element in seal container, first and second compression unit by this electrodynamic element driving, import the refrigerant pipe of refrigeration agent to this first compression unit, to import the refrigerant pipe of second compression unit with the refrigerant gas of pressing in the middle of this first compression unit compression, discharge will be with the refrigerant pipe of the pressurized gas of second compression unit compression, the refrigerant pipe of first and second compression unit is connected with seal container in position adjacent, from the turning in the opposite direction of this seal container, therefore can in limited space, make each refrigerant pipe arrange each refrigerant pipe mutually uninterruptedly.
Particularly, refrigerant pipe at first compression unit is connected with seal container in the position of the downside of the refrigerator pipes of second compression unit, above each refrigerant pipe and link position seal container, disposing storage, when this storage is connected with the refrigerant pipe that refrigeration agent is imported first compression unit, can be when having avoided two refrigerant pipes to interfere mutually, descend to greatest extent by position and can make the refrigerant pipe of itself and second compression unit approaching, can improve space availability ratio significantly storage.
According to the present invention, because its compressor, in seal container, has electrodynamic element, first and second compression unit by this electrodynamic element driving, import the refrigerant pipe of refrigeration agent to this first compression unit, the refrigerant gas that is sucked by the first refrigeration agent ingress pipe with first compression unit compression also is discharged in the seal container, the refrigerant gas of pressing in the middle of will discharging again sucks by being positioned at the second outer refrigeration agent ingress pipe of seal container, compress by second compression unit, first and second refrigeration agent ingress pipe is connected with seal container in position adjacent, arrange towards mutually opposite direction from this seal container, therefore, can in limited space, make each refrigerant pipe arrange each refrigerant pipe mutually uninterruptedly.
Particularly be connected with seal container in the position of the first refrigeration agent ingress pipe at the second refrigeration agent ingress pipe downside, above each refrigeration agent ingress pipe and link position seal container, disposing storage, when this storage is connected on the first refrigeration agent ingress pipe, can be when having avoided two refrigerant pipes to interfere mutually, descend to greatest extent by position and can make itself and the second refrigeration agent ingress pipe approaching, can improve space availability ratio significantly storage.
According to the present invention, because its closed-type compressor, the compression unit that in seal container, has electrodynamic element, drives by this voltage component, by in this compression unit compressed refrigerant and the seal container of discharging, have the wiring terminal parts on the end cap that is installed in seal container, on the end cap around these wiring terminal parts, forming the step of regulation curvature by punching press, therefore, improved near the rigidity of the end cap the wiring terminal parts, particularly with CO 2When compressing, under the situation that the seal container internal pressure uprises, the amount of deformation of pressing the end cap that causes in the seal container can be reduced, resistance to pressure can be improved as refrigeration agent.
According to the present invention, because in above-mentioned closed-type compressor, it is roughly bowl-shape that above-mentioned end cap is, the central shaft that step is with this end cap is the axisymmetric shape in center, the wiring terminal parts are installed in the center of this end cap, therefore even by the distortion of the end cap of pressing the wiring terminal parts welding portion that causes in the seal container, can possibly avoid because the be full of cracks of the welding portion that inhomogeneous deformation produces or peel off can further improve resistance to pressure.
According to the present invention, owing to have the wiring terminal parts on the seal container that is installed in closed-type compressor, these wiring terminal parts have the glass portion of the circle that connects and be installed with electrical end and form this glass portion around the mounting hole peripheral portion that is weldingly fixed on seal container on flange shape metallic assembly department, the thickness size of this assembly department is the scope of 2.4 ± 0.5mm.Therefore, the use CO that the pressure in seal container is high 2In the closed-type compressor of refrigeration agent, can in the withstand voltage properties of fully guaranteeing the wiring terminal parts, can suppress to weld the increase of fixing needed heat.
Thus, can possibly prevent owing to the assembly department at the wiring terminal parts produces be full of cracks or produce gas leakage or the joint destruction that damage causes on glass portion.
According to the present invention, because rotary compressor of the present invention is provided with electrodynamic element and is driven by this electrodynamic element in seal container revolution compression unit, have one or more cylinders, first support member and second support member, these a plurality of cylinders constitute rotary compression element, the opening surface of the electrodynamic element opposition side of this first support member obturation and cylinder, the bearing that has the rotating shaft of electrodynamic element simultaneously, the opening surface of the electrodynamic element side of the inaccessible cylinder of this second support member, and has a bearing of rotating shaft, therefore be provided with the carbon system lining that is folded between this bearing and the rotating shaft in the bearing of a certain side in first and second support member, compare the reduction of the cost that can realize part with the situation that in the bearing of both sides' support member, is respectively equipped with lining.
Particularly, if in the bearing of first support member, be provided with lining, in the bearing of the second big support member of the area of contact of the electrodynamic element side of cylinder and rotating shaft, do not establish lining, then keeping compression area little and when being applied to sliding capability in the bearing of the first big support member of load on the unit area, keeping endurance quality, by removing the lining that compression area is applied to greatly the bearing of the second less support member of duty ratio on the unit area, thereby can reduce cost.
In addition, according to rotary compressor of the present invention, first and second rotary compression element that in closed container, has electrodynamic element and drive by this electrodynamic element, will be in seal container by the gas exhaust of this first rotary compression element compression, compress the middle gas of pressing of this discharge again with this second rotary compression element, has first and second cylinder that is used for constituting respectively first and second rotary compression element, the opening surface of inaccessible first cylinder also has first support member of the bearing of electrodynamic element rotating shaft, the opening surface of inaccessible second cylinder also has second support member of the bearing of rotating shaft, be provided with the carbon system lining that is folded between this bearing and the rotating shaft in the bearing of a certain side in first and second support member, therefore compare with the situation that lining is set in the bearing of both sides' support member respectively, can reduce the cost of part.
Particularly, if in the bearing of second supporting, be provided with lining, do not establish lining in the bearing of first support member of the opening surface of first cylinder below the pressure in sealing becomes seal container, then, can keep sealing second cylinder higher than seal container internal pressure opening surface, carry out fuel feeding by pressure difference and become sliding capability in the bearing of second support member of difficulty, safeguard endurance quality, and, can eliminate the lining that carries out the bearing of the first no problem support member of fuel feeding by pressure difference, can reduce cost.
In addition, with CO 2Gas can have significant effect for the endurance quality of keeping compressor as becoming under the situation of extra-high voltage in refrigeration agent use, the seal container.
In addition, according to closed compressor of the present invention, the compression unit that in seal container, has electrodynamic element and drive by this electrodynamic element, discharge from the refrigerated medium discharge tube behind the refrigeration agent of refrigeration agent ingress pipe suction by the compression unit compression, has sleeve pipe, this sleeve pipe is installed accordingly with the open-work on the flexure plane that is formed on seal container, and be used to connect refrigeration agent ingress pipe and refrigerant discharge leader, forming tabular surface on the seal container outside around open-work, and around on sleeve pipe, forming the insertion part that is used to insert in the open-work and being positioned at it and the contacting part that contacts with the tabular surface of seal container, connect the contacting part of affixed this sleeve pipe and the tabular surface of seal container by projection welding, by contacting of the contacting part of the tabular surface of seal container and sleeve pipe, can guarantee the perpendicularity of the internal diameter of sleeve pipe and seal container, thus, do not using the perpendicularity that to make sleeve pipe under the situation of anchor clamps etc., can improve producibility and improve precision.
According to this invention because on the basis of the above, tabular surface is hollowly formed around open-work, therefore, by the outside of the sleeve pipe in the depressed part that is embedded in seal container and depressed part more precision keep the perpendicularity of sleeve pipe well.
According to rotary compressor of the present invention because the rotary compression element that in seal container, is provided with electrodynamic element and drives by this electrodynamic element, comprise roll, support member, suction path, suction port; This rolls and is formed on the chimeric and eccentric rotation in cylinder of eccentric part in the rotating shaft of the cylinder that is used to constitute rotary compression element and electrodynamic element, the opening surface of the inaccessible cylinder of above-mentioned support member also has the bearing of rotating shaft, above-mentioned suction path is formed on the support member, above-mentioned suction port is formed obliquely on cylinder, and be communicated with in the suction path of support member makes this suction path and cylinder accordingly, the edge portion of the suction passage side of this suction port forms the semicircle arcuation, therefore, can alleviate the passage resistance of suction port and the interconnecting part office that sucks path, can reduce the disorder of air-flow and realize high efficiency running.
In addition, according to the present invention, owing to the end mill of preceding Transverse plane can be formed the suction port of inclination under the state vertical with cylinder on cylinder, therefore, can with other tapped hole or the identical operation of the boring processing of lightening hole etc. in form suction port, can realize reducing production costs of bringing by reducing operation quantity.In addition, by such processing, even also the edge portion of the suction side of intakeport can be formed the semicircle arcuation by the end mill of preceding Transverse plane, therefore with similarly above-mentioned, can reduce the passage resistance of the connected part of intakeport and suction path, can realize high efficiency running by the disorder that reduces air-flow.
In addition, according to the present invention, owing to vertically be close at the exhaust port that can on its gas gas, form inclination on the cylinder by a part with the end mill of preceding end toper, therefore, can with other tapped hole or the identical operation of the boring processing of lightening hole etc. in form suction port, can realize reducing production costs of bringing by reducing operation quantity.
In addition, according to compressor of the present invention, because in refrigerant circuit, stream control gear with refrigeration agent circulation of defrost circuit and this defrost circuit of control, this refrigerant circuit has compressor, gas cooler, decompressor and vaporizer, this compressor has electrodynamic element and driven by this electrodynamic element in seal container first and second compression unit, in the seal container that will discharge by the first compression unit refrigerant compressed gas, compress the middle refrigerant gas of pressing of this discharge again with second compression unit, this gas cooler flows into the refrigeration agent of discharging from second compression unit of above-mentioned compressor, this decompressor is connected with the outlet side of this gas cooler, this vaporizer is connected with the outlet side of this decompressor, therefore, when carrying out the defrosting of vaporizer, can make the refrigeration agent of discharging flow to defrost circuit by the stream control gear, under the state that does not reduce pressure, supply to vaporizer and heat from first compression unit.
Thus, can prevent under the state that not only makes the high-pressure refrigerant decompression of discharging from second compression unit, to supply to the problem that the pressure of the discharge that produces the situation that vaporizer defrosts second compression unit and suction reverses.
Particularly with CO 2In the refrigerant circuit of gas as the refrigeration agent use, can produce significant especially effect.In addition, when generating hot water, can the heat of the hot water of gas cooler be transported to vaporizer, can more promptly carry out the defrosting of vaporizer by refrigeration agent with gas cooler.
Below, according to Figure 37～Figure 39 the rotary compressor 10 of another embodiment of the present invention is described.In each figure, the symbolic representation identical with Fig. 1～Figure 18 has identical and parts same performance.
In each figure, the 10th, with carbon dioxide CO 2The longitudinal type rotary compressor of bosom die mould multistage (two-stage) compression type that uses as refrigeration agent, the seal container cylindraceous 12 that this rotary compressor 10 is made of steel plate, electrodynamic element 14, rotary compressor structure portion 18 constitutes, this revolves compression mechanical part 18 and is made of first rotary compression element 32 (first order) and second rotary compression element 34 (second level), this electrodynamic element 14 is configured in the upside of the inner space of above-mentioned seal container 12, and above-mentioned first rotary compression element 32 (first order) and second rotary compression element 34 (second level) are configured in the downside (side) of this electrodynamic element 14, and drive by the rotating shaft 16 of electrodynamic element 14.It is littler than the discharge volume of first rotary compression element 3 that the discharge volume settings of these second rotary compression elements 34 becomes.
Seal container 12 with its bottom as store oil portion, constitute by the vessel 12A that takes in electrodynamic element 14 and rotary compressor structure portion 18 and roughly bowl-shape end cap (lid) 12B of the upper opening of this vessel of obturation 12A, and, be formed centrally circular mounting hole 12D on this end cap 12B, the wiring terminal parts (omission distribution) 20 that are used for supplying with to electrodynamic element 14 electricity are being installed in this mounting hole 12D.
At this moment, on the end cap 12B around the wiring terminal parts 20, forming the stepped part 12C of regulation curvature annularly by impact briquetting.Wiring terminal parts 20 are made of the glass portion 20A and the metal assembly department 20B of circle, and this glass portion 20A is installed with electrical end 139 with connecting, this assembly department 20B be formed on this glass portion 20A around, and give prominence to below outside tiltedly flange shapely.And, wiring terminal parts 20 face its glass portion 20A from downside insertion mounting hole 12D and with upside, assembly department 20B is welded under with the periphery state of contact of assembly department 20B and mounting hole 12D the mounting hole 12D peripheral portion of end cap 12B, is fixed on thus on the end cap 12B.
Electrodynamic element 14 is made of stator 22 and rotor 24, and this stator 22 is being mounted annularly along the inner peripheral surface of the upper space of seal container 12, and this rotor 24 will be provided with slit G2 and insert on the inboard that is configured in this stator 22 (some gaps).This rotor 24 is fixed on the center of passing along in the rotating shaft 16 of vertical extension.
Stator 22 has duplexer 26 and stator coil 28 (Figure 39), this duplexer 36 is formed by the electromagnetic steel plate of stacked ring-type, this stator coil 28 installs around on 6 26A of tooth portion of this duplexer 26 around (concentrate around) mode (be not distribution that the coil of coiled pencil in advance is installed around, but with the mode of coil on the 26A of tooth portion) with string.In addition, rotor 24 also forms with the same duplexer 30 by electromagnetic steel plate of stator 22, inserts permanent magnet MG at this duplexer 30.
Intermediate clapboard 36 in clamping between above-mentioned first rotary compression element 32 and second rotary compression element 34.Be that above-mentioned first rotary compression element 32 and second rotary compression element 34 are by intermediate clapboard 36, be configured in the upper and lower air cylinders 38 of this intermediate clapboard 36, cylinder 40, at this upper and lower air cylinders 38, have 180 eccentric parts up and down 42 that are located in the rotating shaft 16 by being entrenched in 40 with spending phase differences, on 44 and carry out eccentric rotation roll 46 up and down, 48, roll 46 up and down with this, 48 the contact and will roll 46 up and down, be divided into the not shown blade up and down of low pressure chamber side and hyperbaric chamber side in 48 respectively, the upside opening surface and the lower cylinder 40 open lower side faces of sealing upper cylinder 38 also are also used as the constituting as the upper support member 54 of support member and lower support member 56 of bearing of running shaft 16.
On upper support member 54 and lower support member 56, forming by suction port 161,162 respectively with the suction path 58,60 of the internal communication of upper and lower air cylinders 38,40 and the discharge anechoic chamber 62,64 of depression, two to discharge the opening portion of anechoic chamber 62,64 inaccessible by cover respectively for this.That is, discharge anechoic chamber 62, discharge anechoic chamber 64 by lower cover 68 obturations as cover by upper lid 66 sealings as cover.
At this moment, erect in the central authorities of upper support member 54 and to form bearing 54A, the carbon system lining 122 of tubular is installed on the inner face of this bearing 54A.In addition, connect in the central authorities of lower support member 56 and to form bearing 56A, the carbon system lining 123 of tubular also is installed on bearing 56A inner face.Rotating shaft 16 remains on the bearing 56A of the bearing 54A of upper support member 54 and lower support member 56 by these linings 122,123.
At this moment, lower cover 68 is made of the circular steel plate of annular, by kingbolt 129... from below four positions of its periphery being fixed on the lower support member 56, the lower aperture portion of the discharge anechoic chamber 64 that the pressing chamber 40A of inaccessible lower cylinder 40 inside in first rotary compression element 32 is communicated with.The front end screw thread of this kingbolt 129... is combined on the upper support member 54.The inner circumference edge of lower cover 68 is inwardly being given prominence to the side from the bearing 56A inner face of lower support member 56, and thus, the lower end surface of lining 123 is being kept by lower cover 68, prevents that it from coming off.
Electrodynamic element 14 sides of discharging the upper cap 66 in anechoic chamber 64 and the seal container 12 are being communicated with (Figure 38) by the intercommunicating pore 63 as the hole of perforation upper and lower air cylinders 38,40 intermediate clapboards 36.At this moment, the upright middle discharge tube 121 (refrigeration agent from first rotary compression element 32 is discharged the position) of establishing in the upper end of intercommunicating pore 63, this centre discharge tube 121 points to the clearance G 1 (being the little position of passage resistance) of 28,28 of adjacent stator coils and corresponding with the below of its gap G1 in an embodiment in electrodynamic element 14, this stator coil 28,28 installs around on the stator 22 of electrodynamic element 14 up (Figure 39).
At this moment, stator coil 28 since with string on direction installs around the 26A of tooth portion at stator 22, compare the clearance G 1 bigger (Figure 39) that stator coil is 28,28 around mode with above-mentioned distribution.Except the gap of coil 28,28, also can be the slit G2 between said stator 22 and the rotor 24 as the little position of the passage resistance of the electrodynamic element 14 of discharge tube 121 correspondences in the middle of making.
In addition, the top opening portion of the discharge anechoic chamber 62 of upper cylinder 38 internal communication of upper lid 66 obturations and second rotary compression element 34 will be divided in the seal container 12 and discharge anechoic chamber 62 and electrodynamic element 14 sides.These upper lid 66 its peripheries by 4 kingbolt 78... from being fixed on the upper support member 54.The front end screw thread of this kingbolt 78... is combined on the lower support member 56.
In addition, in rotating shaft 16, in it, be formed centrally the oilhole 80 of vertical and the horizontal oil supply hole 82,84 that is communicated with this oilhole 80 (also being formed on the eccentric part up and down 42,44 of rotating shaft 16).
Connect 42, the 44 mutual joints 90 of eccentric part up and down that are formed in the rotating shaft 16 has rigidity and its shape of cross section is become for example olive shape of non-circular shape greatly than the circular cross section of rotating shaft 16 in order to make its cross-section area with having 180 phase differences of spending.The shape of cross section that promptly connects the joint 90 be located at the eccentric part up and down 42,44 in the rotating shaft 16 its wall thickness on the direction vertical with the eccentric direction of eccentric part 42,44 up and down is big.
Thus, the cross-section area that connects the joint 90 that is located at the eccentric part up and down 42,44 in the rotating shaft 16 integratedly is big, has increased second moment of area, and has increased intensity (rigidity), has improved durability and reliability.Particularly when the high refrigeration agent of secondary compression working pressure, because the pressure difference of high low pressure is big, therefore, the load that is added in the rotating shaft 16 is also big, therefore increases its intensity (rigidity) by the cross-section area that strengthens joint 90, prevents rotating shaft 16 resiliently deformables.
And, as at this moment refrigeration agent considered that the earth environment influence is little, back uses such as combustibility and toxicity be above-mentioned carbon dioxide (CO as an example of the carbonic acid gas of natural refrigeration agent 2), as the lubricant oil use is for example to be the existing oil of mineral oil, alkyl phenyl ring oil, ether oil, ester oil etc.
On the side of the vessel 12A of seal container 12, with the suction path 58,60 of upper support member 54 and lower support member 56, discharge to weld respectively on the corresponding position of the upside (opposite side) of anechoic chamber 62 and electrodynamic element 14 and fixing sleeve pipe 141,142,143 and 144 cylindraceous.Insertion is connecting an end that is used for importing to upper cylinder 38 the refrigeration agent ingress pipe 92 of refrigerant gas in sleeve pipe 141, and an end of this refrigeration agent ingress pipe 92 is communicated with the suction path 58 of upper cylinder 38.This refrigeration agent ingress pipe 92 is through seal containers 12 outer sleeve pipes 144 that arrive, and the other end inserts in the sleeve pipe 144 and to seal container 12 inner openings of electrodynamic element 14 sides.
In addition, insertion is connecting an end that is used for importing to lower cylinder 40 the refrigeration agent ingress pipe 94 of refrigerant gas in sleeve pipe 142, and an end of this refrigeration agent ingress pipe 94 is communicated with the suction path 60 of lower cylinder 40.In addition, insertion is connecting refrigerant discharge leader 96 in lining 143, and an end of this refrigerant discharge leader 96 is communicated with discharge anechoic chamber 62.
Below the action in the above formation is described.In adding heat run, solenoid valve 159 is cutting out.When by wiring terminal parts 20 and not shown distribution during to stator coil 28 energisings of electrodynamic element 14, electrodynamic element 14 startings, rotor 24 rotations.Make to be entrenched in by this rotation and roll 46,48 eccentric rotations in upper and lower air cylinders 38,40 up and down on the eccentric part up and down 42,44 that is provided with integratedly with rotating shaft 16.
So, through refrigeration agent ingress pipe 94 and be formed on suction path 60 on the lower support member 56 be inhaled into from suction port 162 the low pressure chamber side of lower cylinder 40 low pressure (first order suction pressure LP:4MPa) refrigerant gas by roll 48 and the action of blade be compressed and become in the middle of press (MP1:8MPa), be discharged in the seal container 12 from middle discharge tube 121 by access 63 through the discharge anechoic chamber 64 that is formed on the lower support member 56 from the hyperbaric chamber side of lower cylinder 40.
At this moment, middle discharge tube 121 is owing to point to clearance G 1 below of 28,28 of adjacent stator coils on the stator 22 that installs around electrodynamic element 14 up accordingly, therefore refrigerant gas waltzs through in the electrodynamic element 14 by the little clearance G 1 of passage resistance, arrive on the electrodynamic element 14, can will also feed to electrodynamic element 14 directions energetically thus than lower temperature refrigerant gas, electrodynamic element 14 refrigerant gas motion is on every side enlivened cool off electrodynamic element 14, the temperature that suppresses electrodynamic element 14 rises.In addition, thus, press in the middle of becoming in the seal container 12 (MP1).
And, the refrigerant gas of pressing in the middle of in the seal container 12 from the sleeve pipe 144 of electrodynamic element 14 upsides come out (middle discharge press be above-mentioned MP1) enter refrigeration agent ingress pipe 92, enter the suction path 58 that is formed on the upper support member 54 through seal container 12 outer refrigeration agent ingress pipes 92.And be drawn into the low pressure chamber side (second level suck press MP2) of upper cylinder 38 from suction port 161 via this suction path 58.Because refrigeration agent is through being drawn into refrigerant gas in the upper cylinder 38 of second rotary compression element 34 at the refrigeration agent ingress pipe 92 of electrodynamic element 14 upsides to seal container 12 inner openings in this wise, therefore, can in seal container 12, separate oil from the refrigerant gas that middle discharge tube 121 is discharged well.Thus, can reduce being inhaled into second rotary compression element 34 and as described later be discharged to outside oil mass, can prevent possibly that rotary compressor 10 from producing the problem of burn etc.
In addition, be inhaled into upper cylinder 38 the low pressure chamber side in the middle of the refrigerant gas of pressing since roll 46 and the action of blade carry out second level compression, thereby become the refrigerant gas (second level discharge press HP:12MPa) of High Temperature High Pressure, from the hyperbaric chamber side by being formed in discharge anechoic chamber 62 on the upper support member 54, the refrigerant discharge leader 96 inflow gas coolers 154.At this moment refrigerant temperature rises to+and 100 ℃, the water in heat radiation of the refrigerant gas of High Temperature High Pressure and the heating thermal storage water tank like this, thus generate+90 ℃ water approximately.
Carry out cooling refrigeration agent itself in this gas cooler 154 repeatedly, come out from gas cooler 154, and, after by expansion valve 156 decompressions, inflow evaporator 157 and evaporating is inhaled into circulation in first rotary compression element 32 from refrigeration agent ingress pipe 94.
In addition, in the above-described embodiments, sleeve pipe 144 by electrodynamic element 14 upsides makes 92 pairs of seal container 12 inner openings of refrigeration agent ingress pipe, but be not limited to this, even in seal container 12, directly make it be drawn into second rotary compression element 34, also can suck by refrigeration agent ingress pipe in the open lower side of electrodynamic element 14.By such cooling action that can produce electrodynamic element 14 that constitutes.
Like this, because it is corresponding to discharge the little part of position and path in the electrodynamic element from the refrigeration agent of first rotary compression element, the passage resistance little position of therefore can be with the temperature that sprays from first rotary compression element lower refrigerant gas by the electrodynamic element in gap between electrodynamic element stator and rotor and the gap between rotor coil etc. is passed to around the electrodynamic element.
Thus, in the seal container around the electrodynamic element, refrigerant gas moves actively, has improved by the cooling effect of refrigeration agent to electrodynamic element.
In addition, in the seal container owing to a side that will be located at electrodynamic element from the refrigeration agent discharge position of first rotary compression element, the refrigeration agent ingress pipe that will be used to make refrigerant gas suck second rotary compression element is communicated with the seal container of the opposite side of electrodynamic element is interior, therefore, oil from the refrigerant gas that first rotary compression element is discharged is drawn into second rotary compression element by the refrigeration agent ingress pipe after being separated well the process that moves by side to opposite side from one of electrodynamic element.
Thus, the oil mass that is discharged to outside the rotary compressor from second rotary compression element is reduced.In addition, if make little position such as the passage resistance of electrodynamic element in slit between the stator of discharging position and electrodynamic element and rotor and the gap between stator coil etc. corresponding from the refrigeration agent of first rotary compression element, then the refrigerant gas of discharging from first rotary compression element successfully can be sent into the refrigeration agent ingress pipe, refrigerant gas successfully is passed to around the electrodynamic element simultaneously, by the refrigerant gas in the seal container around the electrodynamic element is moved actively, thereby can improve the cooling effect of refrigeration agent to electrodynamic element.
In addition and since with stator coil with string around mode install around in the tooth portion at stator, compare around mode with distributing, the gap between its stator coil is bigger, the circulation of refrigerant gas is better.
Followingly another rotary compressor 10 of the present invention is described according to Figure 40～Figure 44.The symbolic representation identical with Fig. 1～Figure 18 has identical and parts same performance.
In each figure, the 10th, with carbon dioxide CO 2The longitudinal type rotary compressor of bosom die mould multistage (two-stage) compression type that uses as refrigeration agent, the seal container cylindraceous 12 that this rotary compressor 10 is made of steel plate, electrodynamic element 14, rotary compressor structure portion 18 constitutes, this revolves compression mechanical part 18 and is made of first rotary compression element 32 (first order) and second rotary compression element 34 (second level), this electrodynamic element 14 is configured in the upside of the inner space of above-mentioned seal container 12, and above-mentioned first rotary compression element 32 (first order) and second rotary compression element 34 (second level) are configured in the downside of this electrodynamic element 14, and drive by the rotating shaft 16 of electrodynamic element 14.
Seal container 12 with its bottom as store oil portion, constitute by the vessel 12A that takes in electrodynamic element 14 and rotary compressor structure portion 18 and roughly bowl-shape end cap (lid) 12B of the upper opening of this vessel of obturation 12A, and, on this end cap 12B, forming the wiring terminal parts (omission distribution) 20 that are used for supplying with electricity to electrodynamic element 14.
Electrodynamic element 14 is made of stator 22 and rotor 24, and this stator 22 is being mounted annularly along the inner peripheral surface of the upper space of seal container 12, and this rotor 24 will be provided with some inserting with gap and be configured on the inboard of this stator 22.This rotor 24 is fixed on the center of passing along in the rotating shaft 16 of vertical extension.
Stator 22 has duplexer 26 and stator coil 28, and this duplexer 36 is made by the electromagnetic steel plate of stacked ring-type, this stator coil 28 with string on (concentrate around) mode installs around tooth portion at this duplexer 26.In addition, rotor 24 also forms with the same duplexer 30 by electromagnetic steel plate of stator 22, inserts permanent magnet MG at this duplexer 30.
Intermediate clapboard 36 in clamping between above-mentioned first rotary compression element 32 and second rotary compression element 34.Be that above-mentioned first rotary compression element 32 and second rotary compression element 34 are by intermediate clapboard 36, be configured in the cylinder 38 (second cylinder) up and down of this intermediate clapboard 36, cylinder 40 (first cylinder), at this upper and lower air cylinders 38, have 180 eccentric parts up and down 42 that are located in the rotating shaft 16 by being entrenched in 40 with spending phase differences, on 44 and carry out eccentric rotation roll 46 up and down, 48, roll 46 up and down with this, 48 the contact and with upper and lower air cylinders 38, be divided into the blade 50 (blade of downside is not shown) up and down described later of low pressure chamber LR (Figure 44 (f)) side and hyperbaric chamber HR (Figure 44 (f)) side in 40 respectively, the upside opening surface and the lower cylinder 40 open lower side faces of inaccessible upper cylinder 38 and upper support member 54 and the lower support member 56 as the support member that are also used as the bearing of running shaft 16 constitute.
On upper support member 54 and lower support member 56, forming by suction port 161,162 respectively with the suction path 58,60 of the internal communication of upper and lower air cylinders 38,40 and the discharge anechoic chamber 62,64 of depression, this two discharges anechoic chamber 62,64 and openings each cylinder 38,40 opposition side respectively by the cover sealing.That is, discharge anechoic chamber 62, discharge anechoic chamber 64 by lower cover 68 sealings as cover by upper lid 66 sealings as cover.
At this moment, erect in the central authorities of upper support member 54 and to form bearing 54A, the lining 122 of tubular is installed on the inner face of this bearing 54A.In addition, connect in the central authorities of lower support member 56 and to form bearing 56A, following (with the face of lower cylinder 40 opposition sides) of lower support member 56 forms tabular surface, in addition, the lining 123 of tubular is installed also on bearing 56A inner face.This lining 122,123 is made of the good material with carbon element of sliding wear resistance described later, and rotating shaft 16 remains on the bearing 56A of the bearing 54A of upper support member 54 and lower support member 56 by these linings 122,123.
At this moment, lower cover 68 is made of the circular steel plate of annular, from down four positions of its periphery being fixed on the lower support member 56, sealing is with the lower aperture portion of the discharge anechoic chamber 64 of lower cylinder 40 internal communication of the exhaust port not shown in the figures and first rotary compression element 32 by kingbolt 129....The front end screw thread of this kingbolt 129... is combined on the upper support member 54.The inner circumference edge of lower cover 68 is inwardly being given prominence to the side from the bearing 56A inner face of lower support member 56, and thus, the lower end surface of lining 123 (with the end of the opposition side of lower cylinder 40) kept by lower cover 68, prevents that it from coming off.
Electrodynamic element 14 sides of discharging the upper cap 66 in anechoic chamber 64 and the seal container 12 are being communicated with the access not shown in the figures of perforation upper and lower air cylinders 38,40 and intermediate clapboard 36.At this moment, the upright centre discharge tube 121 of establishing in the upper end of access, this centre discharge tube 121 points to the clearance G 1 of 28,28 of adjacent stator coils, and this stator coil 28,28 installs around on the stator 22 of electrodynamic element 14 up.
In addition, upper lid 66 obturations are discharged anechoic chamber 62 and electrodynamic element 14 sides by the top opening portion of the discharge anechoic chamber 62 of upper cylinder 38 internal communication of the exhaust port 184 and second rotary compression element 34 with being divided in the seal container 12.These upper lid 66 its peripheries by 4 kingbolt 78... from being fixed on the upper support member 54.The front end screw thread of this kingbolt 78... is combined on the lower support member 56.
Figure 42 is the plan view of the upper cylinder 38 of expression second rotary compression element 34.In upper cylinder 38, forming accommodation chamber 70, in this accommodation chamber 70, taking in above-mentioned blade 50 and with roll 46 and contacting.And, forming above-mentioned exhaust port 184 in the side (right side among Figure 42) of this blade 50, forming above-mentioned suction port 161 at the opposite side that clips blade 50 opposition sides (left side).And blade 50 will and roll the pressing chamber that constitutes between 46 at upper cylinder 38 and be divided into low pressure chamber LR and hyperbaric chamber HR, and above-mentioned suction port 161 is corresponding with low pressure chamber LR, and exhaust port 184 is corresponding with hyperbaric chamber HR.
On the other hand, the intermediate clapboard 36 of the opening surface of the opening surface of downside of sealing upper cylinder 38 and the upside of lower cylinder 40 roughly circlewise, (faces of upper cylinder 38 sides) are forming oil supply 191 towards radial direction laterally within the limits prescribed from inner peripheral surface as shown in figure 41 in the above.This oil supply 191 with the blade 50 of upper cylinder 38 from Figure 42 with roll 46 position contacting and be formed to the corresponding mode of the downside in the scope α of suction port 161 and edge portions blade 50 opposition sides.In addition, the low pressure chamber LR (suction side) in the external lateral portion of oil supply 191 and the upper cylinder 38 is being communicated with.
In addition, along being formed centrally the oilhole 80 of vertical and the horizontal oil supply hole 82,84 that is communicated with this oilhole 80 (also forming on the eccentric part 42,44 up and down) in the axle, the opening of the inner side surface side of the oil supply 191 of intermediate clapboard 36 is being communicated with oilhole 80 by these oil supply holes 82,84 in rotating shaft 16.Thus, oil supply 191 is communicated with the low pressure chamber LR in oilhole 80 and the upper cylinder 38.
As described later, owing to press in the middle of becoming in the seal container 12, be difficult in the upper cylinder 38 that becomes high pressure in the second level, supply with oil, but by forming the oil supply 191 of intermediate clapboard 36, suct and enter the oil supply 191 of intermediate clapboard 36 from the oily reservoir of seal container 12 inner bottom parts, supply with the low pressure chamber LR side of upper cylinder 38 by its place along the oil that oilhole 80 rises, comes out from oil supply hole 82,84.
Figure 43 represents the pressure oscillation in the upper cylinder 38, and P1 represents the pressure of the inner peripheral surface side of intermediate clapboard 36 among the figure.In the figure as represented by LP, the internal pressure (suction pressure) of the low pressure chamber LR of upper cylinder 38 in suction process because suction pressure loss and lower than the pressure P 1 of the inner peripheral surface side of intermediate clapboard 36.In the meantime, will finish fuel feeding from the oilhole 80 of rotating shaft 16 by the low pressure chamber LR that is ejected in the upper cylinder 38 through 191 of intermediate clapboard 36.
At this, (a)～(i) of Figure 44 is the figure of the refrigeration agent suctions-compression formation in the upper cylinder 38 of such second rotary compression element 34 of explanation.The eccentric part 4 of rotating shaft 16 in (a)～(b) of Figure 44, is closed intakeport 161 by rolling 46 in the drawings when counter clockwise direction is rotated.In (c), open suction port 161, begin to suck refrigeration agent (also carrying out the discharge of refrigeration agent at opposition side).And the suction of refrigeration agent proceeds to (c)～(e).In this interval, oil supply 191 stops up by rolling 46.
Then, in (f), at first oil supply 191 is presented on and rolls 46 downside, by begin to be inhaled into by the blade 56 in the upper cylinder 38 and roll 46 round low pressure chamber LR in and begin fuel feeding (beginning between the drainage area of Figure 43).After, the suction of the oil of the suction of refrigeration agent proceeds to (g)～(i).And in (j), the upside that fuel feeding is performed until oil supply 191 is by till rolling 46 sealings, at this, and fuel cut-off (end in the fuel feeding interval of Figure 43).The suction of refrigeration agent proceeds to later (k)～(l)～(a)～(b), is compressed afterwards and discharges from exhaust port 184.
Connect mutual joint 90 and use it to have rigidity greatly than the circular cross section of rotating shaft 16, and it is for example olive-shaped that its section configuration is formed non-circular shape in order to make its cross-section area with eccentric part up and down 42,44 that 180 phase difference ground and rotating shaft 16 form.The shape of cross section that promptly connects the joint 90 be located at the eccentric part up and down 42,44 in the rotating shaft 16 its wall thickness on the direction vertical with the eccentric direction of eccentric part 42,44 up and down is big.
Thus, the cross-section area that connects the joint 90 that is located at the eccentric part up and down 42,44 in the rotating shaft 16 integratedly is big, has increased second moment of area, and has increased intensity (rigidity), has improved durability and reliability.Particularly when the high refrigeration agent of secondary compression working pressure, because the pressure difference of high low pressure is big, therefore, the load that is added in the rotating shaft 16 is also big, therefore increases its intensity (rigidity) by the cross-section area that strengthens joint 90, prevents rotating shaft 16 resiliently deformables.
And, as at this moment refrigeration agent considered that the earth environment influence is little, back uses such as combustibility and toxicity be above-mentioned carbon dioxide (CO as an example of the carbonic acid gas of natural refrigeration agent 2), as the lubricant oil use is for example to be the existing oil of mineral oil, alkyl phenyl ring oil, ether oil, ester oil etc.
On the side of the vessel 12A of seal container 12, with the suction path 58,60 of upper support member 54 and lower support member 56, discharge to weld respectively on the corresponding position of upside (position roughly corresponding) of anechoic chamber 62 and upper cap 66 and fixing sleeve pipe 141,142,143 and 144 cylindraceous with the lower end of electrodynamic element 14. Sleeve pipe 141 and 142 is neighbouring, and sleeve pipe 143 is in sleeve pipe 141 roughly on the diagonal.In addition, sleeve pipe 144 is in the position of staggering 90 degree with sleeve pipe 141.
Insertion is connecting an end that is used for importing to upper cylinder 38 the refrigeration agent ingress pipe 92 of refrigerant gas in sleeve pipe 141, and an end of this refrigeration agent ingress pipe 92 is communicated with the suction path 58 of upper cylinder 38.This refrigeration agent ingress pipe 92 arrives lining 144 by the upside of seal container 12, the other end insert in the adapter sleeve 144 and with seal container 12 in are communicated with.
In addition, insertion is connecting an end that is used for importing to lower cylinder 40 the refrigeration agent ingress pipe 94 of refrigerant gas in sleeve pipe 142, and an end of this refrigeration agent ingress pipe 94 is communicated with the suction path 60 of lower cylinder 40.In addition, insertion is connecting refrigerant discharge leader 96 in sleeve pipe 143, and an end of this refrigerant discharge leader 96 is communicated with discharge anechoic chamber 62.
And embodiment's rotary compressor 10 also is used in the refrigerant circuit of hot watering supply device shown in Figure 180 153 and is similarly connecting pipe arrangement.Below the action in the above formation is described.In adding heat run, solenoid valve 159 is cutting out.When by wiring terminal part 20 and not shown distribution during to stator coil 28 energisings of electrodynamic element 14, electrodynamic element 14 startings, rotor 24 rotations.Make to be entrenched in by this rotation and roll 46,48 eccentric rotations in upper and lower air cylinders 38,40 up and down on the eccentric part up and down 42,44 that is provided with integratedly with rotating shaft 16.
Thus, through refrigeration agent ingress pipe 94 and be formed on suction path 60 on the lower support member 56 be inhaled into from suction port 162 the low pressure chamber side of lower cylinder 40 low pressure (first order suction pressure LP:4MPa) refrigerant gas by roll 48 and the action of blade be compressed and press (MP1:8MPa) in the middle of becoming, from the hyperbaric chamber side of lower cylinder 40 through exhaust port 41, be discharged in the seal container 12 from middle discharge tube 121 through access 63 from the discharge anechoic chamber 64 that is formed on the lower support member 56.
At this moment, middle discharge tube 121 is owing to point to the gap of 28,28 of adjacent stator coils on the stator 22 that installs around electrodynamic element 14 up, therefore refrigerant gas that can temperature is also lower is supplied in the electrodynamic element 14 energetically, and the temperature that suppresses electrodynamic element 14 energetically rises.In addition, thus, press in the middle of becoming in the seal container 12 (MP1).
And the refrigerant gas of pressing in the middle of in the seal container 12 comes out (middle discharge press be above-mentioned MP1) through refrigeration agent ingress pipe 92 and be formed on suction path 5 on the upper support member 54, be drawn into the low pressure chamber side LR (second level sucks and presses MP2) of upper cylinder 38 from suction port 161 from sleeve pipe 144.The refrigerant gas of pressing in the middle of being inhaled into by roll 46 and the action of blade 50 such second level of carrying out Fig. 5 explanation be collapsed into high-temperature high-pressure refrigerant gas (second level is discharged and pressed HP:12MPa), from hyperbaric chamber HR side by exhaust port 184, through being formed in discharge anechoic chamber 62 on the upper support member 54, the refrigerant discharge leader 96 inflow gas coolers 154.At this moment refrigerant temperature rises to+and 100 ℃, the water in heat radiation of the refrigerant gas of High Temperature High Pressure and the heating thermal storage water tank like this, thus generate+90 ℃ water approximately.
In addition, carry out in gas cooler 154 repeatedly, itself is cooled refrigeration agent, come out from gas cooler 154, then, in expansion valve 156, be depressurized back inflow evaporator 157 and evaporate, suck circulation in first rotary compression element 32 from refrigeration agent ingress pipe 94.
According to the present invention, because first and second rotary compression element that in seal container, has electrodynamic element and drive by this electrodynamic element, to be discharged in the seal container by the gas of first rotary compression element compression, the gas of pressing in the middle of again this being discharged from compresses with second rotary compression element, has first and second cylinder that is used for constituting respectively first and second rotary compression element, be clipped in the intermediate clapboard of separating each rotary compression element between these cylinders, the opening surface of inaccessible respectively each cylinder and have the support member of bearing of the rotating shaft of electrodynamic element, be formed on the oilhole in the rotating shaft, to be formed on the face of second cylinder side of intermediate clapboard with the oil supply that is communicated with the low pressure chamber in this oilhole and second cylinder, therefore, even high situation in the seal container of pressing in the middle of the pressure ratio of the cylinder of second rotary compression element becomes also can utilize the pressure of inspiration(Pi) loss in the breathing process of second rotary compression element positively to supply with oily in cylinder from the oil supply that is formed on the intermediate clapboard.
Thus, the lubricated of second rotary compression element can be positively carried out, the raising with reliability guaranteed of performance can be realized.Particularly can constitute oil supply, therefore, can make simple structureization, can suppress the raising of cost of production owing to only carry out groove processing by face to second cylinder side of intermediate clapboard.
In addition,, be not limited to the rotary compressor of the such bosom die mould multistage compression formula of embodiment as rotary compressor, also effective for the rotary compressor of single cylinder.In addition, in an embodiment, rotary compressor 10 is applied to the refrigerant circuit of hot watering supply device 153, but also is not limited to this, the present invention also can use indoor heating installation etc. effectively.
In addition, in the invention beyond the rotary compressor also to other mode compressor (reciprocating type, scroll compressor etc.) effectively.
Below, use Figure 45～Figure 48 that another the present invention is described.At this moment invention is to liking the refrigerating plant that carbon dioxide is used for refrigeration agent.
As the coolant compressor of the refrigerating plant that carbon dioxide is used as refrigeration agent, well-known rotary two stage compressor (the being designated hereinafter simply as compressor) 500X that bosom die mould for example shown in Figure 48 is arranged.In this compressor 500X, top in seal container 412 is provided with the mechanism portion 418 that is made of stator 414, rotor 416 etc., is provided with the secondary formula rotary compressor 422 that is connected with the rotor 416 of mechanism portion 418 by rotating shaft 420 simultaneously in its underpart.
In the secondary formula rotary compressor 422 of this compressor 500X, setting first compression mechanical part 424 at downside, side is setting second compression mechanical part 426 thereon, first compression mechanical part, 424 compressions with subordinate's side are passed through the gas refrigerant that refrigeration agent ingress pipe 430 imports from storage not shown in the figures, its refrigerant compressed is discharged in the seal container 412 from middle discharge tube 428, it is imported partial second compression mechanical part 426 by extend the refrigeration agent ingress pipe 432 that is provided with from sleeve pipe 429, this sleeve pipe 429 is located in the middle tap hole in the body portion that is opened in seal container 412, high-pressure refrigerant is supplied to the refrigerant circuit of aircondition not shown in the figures in its place's recompression from refrigerant discharge leader 434 for high pressure more.
And in this compressor 500X, refrigerator oil 460 is being deposited in the bottom in seal container 412, seeks the lubricated and bubble-tight raising of the sliding parts of rotary compressor structure portion 42 by sucking its refrigerator oil 460.
For example sucted by the pump mechanism from the underpart that is located at rotating shaft 420, the hollow portion by rotating shaft 420 rises, from the body portion of rotating shaft 420 be located at refrigerator oil 460 that oil supply hole 446,448,450,455 that the peripheral part that rolls 438,440 eccentric part 422,444 is installed discharges and realize the lubricated etc. of sliding partss.
Therefore the compressor 500X of above-mentioned formation is difficult to make the compressor miniaturization owing to be with the structure of refrigerator oil 460 savings in the inside of seal container 412.Therefore, in the car air conditioner that uses the compressor 500X compressed refrigerant construct like that etc., compressor is arranged on the limited automobile hood of volume when inner with the automobile component of motor etc., the problem that is difficult to be provided with is arranged.
Therefore, the inside that need be provided at compressor is not put aside refrigerator oil or is put aside the aircondition that there is the formation in the compressor part in addition in big portion minimal refrigerator oil, refrigerator oil, and it becomes problem to be solved.
Therefore, the present invention under this situation, in order to solve above-mentioned prior art problems, at least be communicated with compressor by refrigerant pipe, radiator, vaporizer and in the refrigeration agent B loop that forms filling in the refrigerating plant of carbon dioxide, be provided to press from both sides in the refrigerant circuit and establishing oil separator, simultaneously connect the store oil portion of its oil separator and first rotary compressor that constitutes of compressor, in above-mentioned first rotary compressor that constitutes, oil separator is located at the outlet side refrigerant circuit of radiator or second rotary compressor that constitutes of evaporator outlet side refrigerant circuit by returning oil pipe.
Below, mainly one embodiment of the invention are described according to Figure 45～Figure 47, be easy understanding, in these figure, with Figure 48 in the part that illustrated have on the part of identical function and annotate with identical symbol.
At this moment refrigerating plant 600 for example as shown in figure 45, connected compressors 500, radiator 501, expansion valve 502, vaporizer 503, oil separator 504 and formed the refrigeration agent loop circuit by refrigerant pipe 510, the carbon dioxide as refrigeration agent in filling in its loop circuit.
In addition, connecting 504A of store oil portion and the compressor 500 that is located at oil separator 504 bottoms by returning oil pipe 512.Promptly, oil separator 504 has the 504A of store oil portion at bottom side as shown in figure 46, and have oil above it and adhere to separation member 504B, have a plurality of balk board 504C more above it, comprise refrigeration agent that refrigerator oil 460 enters the gas in the oil separator interiorly from the refrigerant pipe 510 that is connected with base plate and adhere to separation member 504B, refrigerant pipe 510 discharges of gap by configuration balk board 504C above it again from being connected with top board by oil.
It is the parts that formed by the little wire netting of stacked mesh by for example that oil adheres to separation member 504B, has the formations such as parts in such gap such as metal pot-scouring brush.And, the gas refrigerant that contains refrigerator oil 460 is when adhering to the gap of separation member 504B by oil, gas refrigerant from refrigerant pipe 510 former states that are connected with top board be discharged from, but, the refrigerator oil 460 that density is big adheres to separation member 504B collision with oil and little by little underspeeds, and finally adheres to separation member 504B attached to oil and goes up and stay on its part.
At that time, since oil adhere to separation member 504B above be provided with multi-disc balk board 504C, the effect of the refrigeration agent that the lower side that has reduction to enter oil separator 504 is discharged from top and the flow velocity of refrigerator oil 460 has further improved the centrifugation effect of adhering to separation member 504B from the oil of refrigeration agent separation refrigerator oil 460.
When adhere to the amount increase that separation member 504B upward stays the refrigerator oil 460 on its part attached to oil, when its quality increased, refrigerator oil 460 adhered to separation member 504B from oil and drips, and existed among the oil storage tank 504A of bottom.And owing on the base plate of oil separator 504, connecting and return oil pipe 512, therefore, adhere to separation member 504B from oil and drip and exist the refrigerator oil 460 the oil storage tank 504A of bottom to turn back to compressor 500 by returning oil pipe 512.
In addition, compressor 500 for example is a formation shown in Figure 47.Be that compressor 500 is not the structure at internal reservoir refrigerator oil 450, be connected the terminal part that returns oil pipe 512 with underpart that the 500X of compressor shown in Figure 48 is similarly constituting the rotating shaft 420 of hollow, return oil pipe 512 by it and discharge each sliding parts that supplies to rotary compressor structure portion 422, seek to improve the lubricated and tightness of its part from the never illustrated oil supply hole of refrigerator oil 460 that oil separator 504 returns.
Promptly, in the compressor 500 of formation shown in Figure 47, do not need within it that portion is depositing refrigerator oil 460, therefore can be with little than the existing compressed oil 500X of built-in refrigerator oil 460 in seal container 412 of the seal container 422 of built-in mechanism portion 418 and rotary compressor structure portion 422.
Below, the action of refrigerating plant shown in Figure 45 600 is described.When the electrical power wiring post parts 454 by compressor 500 and distribution not shown in the figures during to the stator coil energising not shown in the figures of mechanism portion 418, mechanism portion 418 startings, its rotor not shown in the figures is rotated.By this rotation, off-centre rotation (with reference to Figure 47) is carried out in not shown in the figures the rolling that is entrenched on the eccentric part that is wholely set with rotating shaft 420 in cylinder.
Therefore, the refrigerant gas of the low pressure that is sucked by refrigeration agent ingress pipe 430 (refrigerant pipe 510) is pressed by first compression mechanical part, 424 compressions of downside and in the middle of becoming, and is discharged in the seal container 412 from middle discharge tube 428 under the state that contains the vaporific refrigerator oil 460 of trace.
At this moment, middle discharge tube 428 for example points upwards mechanism portion 418 install around adjacent stator coil gap each other on stator, the refrigerant gas that temperature is also lower feeds to mechanism portion 418 directions energetically, and the temperature that suppresses mechanism portion 418 thus rises.In addition, thus, press in the middle of becoming in the seal container 412.
And, the seal container 412 interior middle refrigerant gas of pressing that contain the vaporific refrigerator oil 460 of trace are compressed by second compression mechanical part 426 of upside via refrigeration agent ingress pipe 432 backs, become the refrigerant gas of the High Temperature High Pressure that contains vaporific refrigerator oil 460, flow in the radiator 501 through refrigerant discharge leader 434 (refrigerant pipe 510).At this moment refrigerant temperature rises to about 100 ℃, and the refrigerant gas of such High Temperature High Pressure that contains refrigerator oil 460 heat radiation and being cooled is come out from radiator 510 after becoming the supercritical state that contains refrigeration agent oil 460.
Then, after by expansion valve 502 decompressions, inflow evaporator 503 evaporates, when in this vaporizer 503, evaporating, by refrigeration agent from around the heat of vaporization captured, if the refrigerating plant that refrigerating plant 600 automobile refrigeratings are used, then the air in the car is cooled and carries out air-conditioning.In vaporizer 503, low-boiling refrigerant carbon dioxide evaporates selectively, and the refrigerator oil 460 higher than refrigeration agent boiling point can evaporate hardly.
Vaporized refrigeration agent evaporation and refrigerator oil 460 flow into oil separator 504 in vaporizer 503, separate refrigerator oil 460 by said mechanism from refrigeration agent.The refrigeration agent that has been separated the gas of refrigerator oil 460 by separator 414 carries out being drawn into circulation in first compression mechanical part 424 from refrigerant ingress pipe 430 (refrigerant pipe 510) repeatedly, and the refrigerator oil 460 of the liquid that is separated from refrigeration agent by oil separator 414 carries out repeatedly from returning the circulation that oil pipe 512 turns back to compressor 500.
Oil separator 504 also can be located at the outlet side of radiator 501.That is, the refrigerant carbon dioxide that has been dispelled the heat by radiator 504 is in supercritical state, does not become liquid completely.In addition, because refrigerator oil 460 is a liquid completely, even oil separator 504 is arranged on the outlet side of radiator 501, also can be separated into the refrigeration agent of gas and the refrigerator oil 460 of liquid by said mechanism, the refrigerator oil 460 that separates is turned back to compressor 500.
In addition, as compressor 500, its rotary compressor structure portion 422 can be a cylinder type compressor, also can be the inside that the refrigerant vapor of the high pressure that compressed of compression mechanical part is ejected into seal container 412, the high-pressure refrigerant that is ejected into its seal container 412 inside refrigeration agent spraying pipe from the top that is located at seal container 1 etc. is discharged to outside the machine.
As described above, in the refrigeration agent loop circuit that is communicated with compressor at least, radiator, vaporizer by refrigerant pipe and forms in the refrigerating plant of filling carbon dioxide, because folder is being established oil separator on refrigerant circuit, connect the store oil portion of its oil separator and the refrigerating plant of compressor by returning oil pipe, be the refrigerating plant that oil separator is located at the outlet side refrigerant circuit of the outlet side refrigerant circuit of radiator or vaporizer, therefore in compressor, do not need to deposit refrigerator oil.Therefore, the size that can make the seal container of taking in compression mechanical part, mechanism portion is littler than the compressor of built-in refrigerator oil, can make the compressor miniaturization.Therefore, with its compressor during, in the limited hood of volume, when the auto parts of motor etc. are provided with, be provided with easily as the compressor of car air conditioner.

Claims (2)

1. compressor is provided with electrodynamic element, by the compression unit that this electrodynamic element drives in container, it is characterized in that,
Have vessel side carriage, the storage that is located on the described container side, the memory side carriage that this storage is installed,
By this memory side carriage is fixed on the described vessel side carriage, described storage is installed in described container by described two carriages.
2. compressor as claimed in claim 1 is characterized in that, described memory side carriage be installed in the central authorities of described storage or position of centre of gravity or they near.
CN2008101256522A 2001-09-27 2002-09-26 Compressor Expired - Fee Related CN101307765B (en)

Applications Claiming Priority (30)

Application Number Priority Date Filing Date Title
JP296165/2001 2001-09-27
JP2001295859A JP3913507B2 (en) 2001-09-27 2001-09-27 Rotary compressor
JP295678/2001 2001-09-27
JP2001295866A JP2003097472A (en) 2001-09-27 2001-09-27 Rotary compressor
JP296180/2001 2001-09-27
JP2001295654A JP2003097433A (en) 2001-09-27 2001-09-27 Hermetic electric compressor
JP295654/2001 2001-09-27
JP295634/2001 2001-09-27
JP295859/2001 2001-09-27
JP2001295678A JP2003097479A (en) 2001-09-27 2001-09-27 Rotary compressor
JP2001295673A JP2003097478A (en) 2001-09-27 2001-09-27 Rotary compressor
JP2001295663A JP2003097434A (en) 2001-09-27 2001-09-27 Hermetic electric compressor
JP2001296165A JP4236400B2 (en) 2001-09-27 2001-09-27 Defroster for refrigerant circuit
JP2001295634A JP3728227B2 (en) 2001-09-27 2001-09-27 Rotary compressor
JP2001296180A JP3986283B2 (en) 2001-09-27 2001-09-27 Rotary compressor
JP295663/2001 2001-09-27
JP295866/2001 2001-09-27
JP295673/2001 2001-09-27
JP311702/2001 2001-10-09
JP2001311699A JP3963691B2 (en) 2001-10-09 2001-10-09 Hermetic electric compressor
JP311699/2001 2001-10-09
JP315687/2001 2001-10-12
JP319419/2001 2001-10-17
JP319401/2001 2001-10-17
JP323769/2001 2001-10-22
JP323757/2001 2001-10-22
JP327817/2001 2001-10-25
JP327809/2001 2001-10-25
JP332796/2001 2001-10-30
JP366208/2001 2001-11-30

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CNB021435065A Division CN100376799C (en) 2001-09-27 2002-09-26 Compressor and its producing method, frost removing device of coolant loop, and freezing device

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CN101307765B CN101307765B (en) 2012-06-06

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CNA2008101256490A Pending CN101307760A (en) 2001-09-27 2002-09-26 Compressor
CNA2006100743705A Pending CN1847662A (en) 2001-09-27 2002-09-26 Compressor and producing method thereof
CNB2006100743739A Expired - Fee Related CN100501167C (en) 2001-09-27 2002-09-26 Compressor
CN2006100743692A Expired - Fee Related CN1847756B (en) 2001-09-27 2002-09-26 Defroster of refrigerant circuit
CNA2008101256503A Pending CN101307761A (en) 2001-09-27 2002-09-26 Compressor
CNB200610074371XA Expired - Fee Related CN100443728C (en) 2001-09-27 2002-09-26 Compressor
CNB2006100743724A Expired - Fee Related CN100425842C (en) 2001-09-27 2002-09-26 Compressor
CN2008101256522A Expired - Fee Related CN101307765B (en) 2001-09-27 2002-09-26 Compressor
CNA2008101256467A Pending CN101307763A (en) 2001-09-27 2002-09-26 Compressor
CN2008101256471A Expired - Fee Related CN101307764B (en) 2001-09-27 2002-09-26 Compressor
CNA2008101256452A Pending CN101319675A (en) 2001-09-27 2002-09-26 Rotary compressor

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CNA2006100743705A Pending CN1847662A (en) 2001-09-27 2002-09-26 Compressor and producing method thereof
CNB2006100743739A Expired - Fee Related CN100501167C (en) 2001-09-27 2002-09-26 Compressor
CN2006100743692A Expired - Fee Related CN1847756B (en) 2001-09-27 2002-09-26 Defroster of refrigerant circuit
CNA2008101256503A Pending CN101307761A (en) 2001-09-27 2002-09-26 Compressor
CNB200610074371XA Expired - Fee Related CN100443728C (en) 2001-09-27 2002-09-26 Compressor
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CNA2008101256452A Pending CN101319675A (en) 2001-09-27 2002-09-26 Rotary compressor

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CN101307764A (en) 2008-11-19
CN1847659A (en) 2006-10-18
CN101307763A (en) 2008-11-19
CN1847756A (en) 2006-10-18
CN100425842C (en) 2008-10-15
CN100443728C (en) 2008-12-17
JP2003097468A (en) 2003-04-03
CN1847756B (en) 2010-05-12
CN101319675A (en) 2008-12-10
CN100501167C (en) 2009-06-17
CN101307765B (en) 2012-06-06
CN101307764B (en) 2012-06-13
CN1847662A (en) 2006-10-18
CN101307761A (en) 2008-11-19
CN1847661A (en) 2006-10-18
CN1847663A (en) 2006-10-18
CN101307760A (en) 2008-11-19
JP3728227B2 (en) 2005-12-21

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