WO2007099919A1 - 圧縮機の摺動部品、摺動部品基体、スクロール部品及び圧縮機 - Google Patents
圧縮機の摺動部品、摺動部品基体、スクロール部品及び圧縮機 Download PDFInfo
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- WO2007099919A1 WO2007099919A1 PCT/JP2007/053551 JP2007053551W WO2007099919A1 WO 2007099919 A1 WO2007099919 A1 WO 2007099919A1 JP 2007053551 W JP2007053551 W JP 2007053551W WO 2007099919 A1 WO2007099919 A1 WO 2007099919A1
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- Prior art keywords
- scroll
- compressor
- hardness
- base
- sliding
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Classifications
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
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- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C37/00—Cast-iron alloys
- C22C37/10—Cast-iron alloys containing aluminium or silicon
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- 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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- 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
- F04C2230/00—Manufacture
- F04C2230/20—Manufacture essentially without removing material
- F04C2230/21—Manufacture essentially without removing material by casting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
- F05C2201/0436—Iron
- F05C2201/0439—Cast iron
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/06—Silicon
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/08—Ceramics; Oxides
- F05C2203/0865—Oxide ceramics
- F05C2203/0882—Carbon, e.g. graphite
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2251/00—Material properties
- F05C2251/10—Hardness
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2251/00—Material properties
- F05C2251/14—Self lubricating materials; Solid lubricants
Definitions
- the present invention relates to a compressor, and sliding parts of the compressor (scroll parts, cylinder block
- sliding component substrates roll component substrates, cylinder block substrates, piston substrates, roller substrates, etc.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2005-36693
- Patent Document 2 Japanese Utility Model Application Publication No. 4 134686
- the initial tip of the spiral tip is set so as to open in consideration of deformation during operation. This is because when a part of the spiral tip contacts during operation, a large gap is created in other parts of the tip, the thrust bearing surface floats, and it loses its function, and the movable scroll is fixed scroll and others. This is because problems such as damage and performance degradation occur when parts are pinched. However, due to part machining tolerances, geometric tolerances, assembly tolerances, and elevated temperatures inside the volute, tip contact may occur during operation. This contact state is gradually eliminated as the compressor is operated and the tip of the tip on the scroll side in contact with the fixed scroll or the movable scroll is worn away (this phenomenon is “follow-up”.
- the hardness of the movable scroll and fixed scroll is not as high as possible, but it is as hard as possible to "adhere" at the time, and it is necessary to develop sufficient durability during operation. You need to be hard enough to be able to do it.
- movable scroll If the hardness of the fixed scroll is extremely high, seizure resistance is poor and pump-down operation (probable to occur during forgetting to open the shut-off valve during installation or during refrigerant recovery operation during relocation), out of gas operation (refrigerant filling) When it occurs when there is a shortage of piping power or a leak, etc.), the tip of the scroll and the bottom (especially the center) of the scroll compressor lap may be seized, which may cause a failure of the compressor and replacement. There is.
- movable scrolls and fixed scrolls have a hardness that can ensure sufficient machinability when machining is required, and a hardness sufficient to exhibit sufficient durability after completion. It needs to be.
- the hardness of the movable scroll or the fixed scroll is extremely low, the ductility of the movable scroll or the fixed scroll becomes too large, so that the component cutting edge tends to be sharp and the swarf processing ability may be deteriorated. Therefore, this point force also requires appropriate hardness for movable scrolls and fixed scrolls.
- the optimization of the hardness of the cylinder block and the piston is as important as the optimization of the hardness of the scroll parts of the scroll compressor.
- the object of the present invention is to achieve high tensile strength and to exhibit sufficient durability during operation, and as soon as possible to "adapt" as early as possible, it is possible to burn it during abnormal operation. It is an object of the present invention to provide a sliding part in which sticking does not occur and a compressor incorporating such a sliding part. Another object of the present invention is to provide a sliding component base of a compressor which exhibits good machinability.
- the sliding component of the compressor according to the first aspect of the present invention has a carbon content of 2.0 wt% to 2.7 wt%, a ke content of 1. Owt% to 3. Owt%, and the balance is an unavoidable impurity. And at least a portion of the hardness of which graphite is smaller than flake graphite of flake graphite base iron, and is higher than HRB 90 and lower than HRB 100. The hardness is more preferably higher than HRB 90 and lower than HRB 95. Moreover, adjustment of hardness is realizable by the heat processing after shaping
- the “sliding part” is a sliding part of a compressor, and, for example, a movable scroll of a scroll compressor, a fixed scroll, a bearing, a rotating shaft (crankshaft), a rotation preventing member, and Slide bush (slide block), cylinder block of swing compressor and rotary compressor, front head, rear head, middle plate and rotating shaft (crankshaft), piston, roller, etc.
- the “sliding component” is a cylinder block of a swing compressor or a rotary compressor, the hardness of at least the wall portion forming the cylinder hole should be higher than HRB 90 and lower than HRB 100.
- the sliding parts are inferior in wear resistance, and abnormal wear (several tens of ⁇ m order) in short-time abnormal operation (pump down operation, out of gas operation, etc.)
- abnormal wear severe tens of ⁇ m order
- the gap at the tip of the spiral part becomes too large and the performance decreases.
- the performance may be lowered due to the gas leakage and the temperature of the discharge gas may be too high to operate.
- a sliding part force S scroll part there is a possibility that the high tensile strength effect of the spiral part due to the improvement of the tensile strength may not be sufficiently activated.
- the hardness of the sliding part is HRB 100 or more, the sliding part is inferior to seizing resistance, and when the sliding part is a scroll part, swirling occurs during abnormal operation (pump down operation, gas shortage operation, etc.) There is a risk of seizing of parts and failure of the compressor, forcing replacement.
- the area fraction of ferrite in the matrix composition substantially corresponds to the range of 50% to 5%.
- the graphite area ratio almost corresponds to the range of 6% to 2%.
- the range in which the hardness is higher than HR B90 and lower than HRB 95 substantially corresponds to the range in which the ferrite area ratio in the matrix composition is smaller than 50% and larger than 25%.
- the area fraction of the graphite is less than 6% and almost corresponds to the range of more than 3%.
- the sliding parts of such a compressor are formed by subjecting the above-mentioned iron to semi-melt die casting, semi-solid die casting, or die-casting, and then the formed product is quenched to whiten the whole. The hardness is adjusted to the heat treatment after It is built.
- the entire molded product is whitened by heat treatment.
- the tensile strength can be adjusted. And it has been found that the tensile strength of a molded article produced through this heat treatment is in proportion to its hardness. Incidentally, in the range where the hardness is higher than HRB 90 and lower than HRB 100, the tensile strength substantially corresponds to the range of 600 MPa to 900 MPa. In other words, management of tensile strength of molded articles can be substituted by hardness that can be easily measured.
- the sliding part when the sliding part is a scroll part, there is a merit that design freedom of the spiral part is greatly improved and small diameter and large capacity can be achieved. Therefore, the sliding parts of this compressor exhibit higher tensile strength than sliding parts such as flake graphite pig iron. Moreover, according to the experimental results obtained by the present inventor, when the hardness is in a range higher than HRB90 and lower than HRB100, the sliding component can exhibit sufficient durability during compressor operation, and As soon as possible, “familiarization” has occurred, and it has been clarified that seizing does not occur during abnormal operation. In addition, since the sliding parts have an appropriate hardness, there is an advantage that the sliding parts are scratched and the handling becomes easy.
- the sliding parts of this compressor have high tensile strength, can exhibit sufficient durability during operation, and can become “familiar with” as soon as possible. Also, no burn-in occurs during abnormal operation.
- the sliding parts of this compressor are made of iron having the above components semi-solid die-cast, semi-solid die-cast, die-quenched, and then quenched to make the whole as white as possible. And, since it is manufactured by heat treatment after that, it is possible to reduce the thrust loss due to the small diameter and to increase the capacity by reducing the thickness of each part, and to be superior in toughness compared with the FC material. Therefore, it is difficult to cause damage due to sudden increase in internal pressure or foreign object entrapment, and even if it is damaged, fineness and dust are produced. You can enjoy the benefits etc. By the way, it can be said that such a compressor is especially suitable for replacement demand.
- a sliding component of a compressor according to a second aspect of the present invention is a sliding component of the compressor according to the first aspect of the present invention, wherein the sliding component is formed by semi-solid die casting or semi-solid die casting and then quenched. Furthermore, it is heat-treated and manufactured.
- the sliding parts of this compressor are formed by semi-solid die casting or semi-solid die casting and then quenched and then heat treated to be manufactured. For this reason, the sliding component base can be manufactured by Younet. Therefore, the sliding parts of this compressor can reduce machining costs and can be manufactured at lower cost.
- the sliding part of the compressor according to the third aspect of the invention is a sliding part of the compressor according to the first aspect of the present invention, wherein the sliding part is formed by die-clad molding and then quenched and then heat-treated.
- the sliding parts of this compressor are formed by die casting, then quenched, and then heat treated to be manufactured. For this reason, the pressure required during the molding process can be low. Therefore, the pressing device and the heating device necessary for die cast molding are not required, and the cost for equipment can be reduced. As a result, the sliding parts of this compressor have a low molding cost and can be made cheaper.
- the sliding part of the compressor according to the fourth invention is the sliding part of the compressor according to any one of the first invention and the third invention, wherein the ratio of tensile strength to Young's modulus is 0. It is below. In addition, it is preferred that Young's modulus is 175-190GPa! /.
- the tensile strength rises to an unprecedented level, the fatigue damage will occur as before! If the strength in terms of strength only the height (H) and thickness of the spiral part of the scroll part (T The inventors of the present invention have found that other problems occur if the ratio (HZT), which is the ratio to) is determined. That is, the ratio (HZT) is too large just because the strength is secured. If it is too thick, even if there is no problem in terms of strength, the deformation of the spiral part becomes too large when performing cutting, and the machining allowance and cutting feed of the end mill etc. can not be increased, so the time is long. You may notice that during the operation of the compressor, the deformation (deflection) of the spiral part becomes large and the performance declines, or the noise from the contact with the other scroll may increase. .
- the ratio (HZT) of the spiral portion is determined in consideration of the upper limit of the deformation amount of the spiral portion which is also required from the viewpoint of processing time, performance deterioration and noise.
- the tensile strength is also considered to be sufficient, and it is sufficient if heat treatment is carried out to increase the strength excessively.
- the ratio of tensile strength to Young's modulus is determined, in the scroll component according to the present invention, an event of causing excessive increase in strength due to heat treatment over cost and time is avoided. Heat treatment can be performed appropriately.
- the ratio of is preferably at least 0. 0033.
- the length of the spiral portion in a direction orthogonal to the flat plate portion (hereinafter referred to as spiral portion) is 19 or less.
- the height (H) of the spiral portion is divided by the thickness (T) of the spiral portion. It is preferred that the value is 8 or less.
- the rigidity of the spiral portion is increased. It is because the sex (Young's modulus) will run short.
- Such scroll parts are incorporated in a scroll compressor incorporated in a refrigerant circuit of a refrigeration system using carbon dioxide as a refrigerant which preferably has a ratio (HZT) of 10 or more to reduce the thickness of the vortex portion. If the ratio (HZT) is 2 or more, it is preferable to make the spiral part thinner.
- the sliding part of the compressor according to the fifth aspect of the present invention is the sliding part of the compressor according to the first aspect of the present invention as well as the fourth aspect of the present invention. ing.
- the “partial heat treatment” mentioned here is performed using a high frequency heating method, a laser heating method, or the like. If the sliding component is a crankshaft of a compressor incorporated in the refrigerant circuit of a refrigeration system using a high pressure refrigerant such as carbon dioxide or R410A as the refrigerant, partial heat treatment is applied to the eccentric shaft and the main shaft. Is preferred. When a notch is provided between the main shaft and the eccentric shaft in the crankshaft, it is preferable that partial heat treatment be performed on the periphery of the notch.
- a balance weight is integrally formed on the crankshaft.
- the sliding component is an inner drive type movable scroll component of a scroll compressor incorporated in the refrigerant circuit of a refrigeration apparatus using a high pressure refrigerant such as carbon dioxide or R410A as a refrigerant
- the pin shaft portion for the inner drive Partial heat treatment is preferably applied to the
- a scroll compressor rotation preventing member for example, an Oldham ring (Oldham coupling), etc. in which this sliding part is incorporated into the refrigerant circuit of a refrigeration system using a high pressure refrigerant such as carbon dioxide or R410A as a refrigerant.
- the key portion which is the sliding portion
- a partial heat treatment it is preferable to subject the key portion, which is the sliding portion, to a partial heat treatment.
- the sliding component is a cylinder block of a sliding compressor incorporated in the refrigerant circuit of a refrigeration system using a high pressure refrigerant such as carbon dioxide or R410A as the refrigerant
- a partial portion is formed on the wall forming the bush accommodation hole.
- heat treatment is applied.
- the sliding component is a piston of a swing compressor incorporated in the refrigerant circuit of a refrigeration system using a high pressure refrigerant such as carbon dioxide or R410A as the refrigerant
- a high pressure refrigerant such as carbon dioxide or R410A
- Partial heat treatment is preferably applied to the periphery of the notch formed at the base of the blade.
- this sliding component is combined with the refrigerant circuit of the refrigeration system using a high pressure refrigerant such as carbon dioxide or R410A as the refrigerant.
- a high pressure refrigerant such as carbon dioxide or R410A
- the sliding parts of this compressor are partially heat-treated, for example, on a stress concentration portion, a sliding portion and the like. For this reason, sufficient fatigue strength and wear resistance can be imparted to the stress concentration portion, sliding portion and the like of the sliding component of this compressor.
- a sliding component is particularly effective for high pressure refrigerants such as carbon dioxide and the like.
- the strength of the partially heat-treated portion is improved, it is possible to realize a thin and light-weighted portion of the partially heat-treated portion.
- the sliding component of the compressor according to the sixth invention is a sliding component of the compressor according to the fifth invention, wherein the hardness of the portion to which the partial heat treatment is applied is higher than HRC 50 and lower than HRC 65. .
- the hardness at the place where partial heat treatment is applied is higher than HRC 50 and lower than HRC 65.
- a sliding part of this compressor has a portion such as a bearing, which is particularly required to have hardness, if the hardness of that portion is higher than HRC 50 and lower than HRC 65, the wear of that portion Can be sufficiently suppressed.
- the sliding component of the compressor according to the seventh invention is the sliding component of the compressor according to the fifth invention or the sixth invention, and the portion to which the partial heat treatment is performed is a stress concentration portion.
- stress concentration portion refers to a cutout portion formed in the vicinity of the base of the scroll portion of the scroll part, the center of the flat surface of the scroll part on the first plate surface side, and the scroll part. These include the periphery of the base of the bearing.
- the sliding parts of this compressor are subjected to partial heat treatment at the stress concentration portion. For this reason, in the sliding parts of this compressor, good conformability is imparted to the sliding part requiring slidability, and sufficient fatigue strength is imparted to the stress concentration part.
- Such sliding parts are particularly effective for high pressure refrigerants, such as carbon dioxide and the like.
- a sliding part of a compressor according to an eighth invention is a sliding part of the compressor according to any of the first invention and the seventh invention, and is manufactured using a mold having a convex portion. ing.
- the convex portion can be formed to have a thin predetermined portion near the center of the sliding component.
- the sliding part has a thin predetermined part near the center.
- the "predetermined portion” referred to here is, for example, a portion to be opened.
- the sliding parts of the compressor are scroll parts In the case, the "predetermined portion" is, for example, a portion near the center of the mirror plate or a portion scheduled to open the discharge hole near the center.
- the height of the convex portion is preferably set to such a height as to make the thickness of a predetermined portion near the center of the scroll 4 mm or less.
- the bearing part of the solid round bar has a bearing part fitted on the outside of the drive shaft rather than the movable scroll part of the inner drive fitted on the inside of the drive shaft.
- the movable scroll part suppresses the generation of gonorrhs.
- the sliding part is a movable scroll part of an inner drive in which the bearing of the solid round bar is fitted inside the drive shaft, it is preferable that at least a part of the inside of the bearing is scooped out by the projection.
- a thin predetermined portion is formed in the vicinity of the center of the sliding component by semi-fusion molding of a metal material using a mold having a convex portion. For this reason, in the sliding component of this compressor, the occurrence of a gonorrh is suppressed.
- the sliding part of the compressor according to the ninth aspect of the present invention is the sliding part of the compressor according to any one of the first aspect of the present invention and the seventh aspect of the present invention, wherein a predetermined portion near the center is formed thin.
- the "predetermined portion” is, for example, an opening scheduled portion or the like.
- the “predetermined portion” is, for example, a portion near the center of the end plate, a portion scheduled to open the discharge hole near the center, or the like.
- the height of the convex portion is preferably set to such a height that the thickness of a predetermined portion near the center of the scroll is 4 mm or less.
- this sliding part is a movable scroll If the shaft part is a solid round bar, the movable scroll part has a bearing part that fits on the outside of the drive shaft rather than the movable scroll part of the inner drive that fits inside the drive shaft. The occurrence of nests is suppressed.
- the sliding part is a movable scroll part of an inner drive in which the bearing of the solid round bar is fitted inside the drive shaft, it is preferable that at least a part of the inner part of the bearing is scooped out by the projection. .
- a base having a thin predetermined portion is formed near the center by using a mold having a convex portion, and a through hole is formed in the thin predetermined portion of the base. Manufactured by being formed. For this reason, in the sliding parts of this compressor, the occurrence of gonorrhs is suppressed. In addition, even if a through hole is formed at the portion to be opened, there is no possibility that the hollows inside the sliding component will be exposed to the outside, and it is also possible to suppress a decrease in fatigue strength.
- the scroll component of the compressor according to the tenth aspect of the invention has a carbon content of 2.0 wt% to 2.7 wt%, a silicon content of 1. Owt% to 3. Owt%, and the balance is
- a scroll component of a compressor which also includes iron having unavoidable impurities and whose graphite is smaller than the flake graphite of flake graphite pig iron, and includes a flat plate portion and a spiral portion.
- the spiral portion extends from the first plate surface of the flat plate portion in a direction perpendicular to the first plate surface while maintaining a spiral shape.
- the flat portion and the spiral portion have hardness higher than HRB90 and lower than HRB100.
- the hardness of the tip of the spiral portion is particularly included in the above hardness range.
- the hardness is more preferably higher than HRB 90 and lower than HRB 95.
- the area fraction of ferrite in the matrix composition corresponds approximately to the range of 50% to 5%.
- the graphite area ratio almost corresponds to the range of 6% to 2%.
- the range where the hardness is higher than HRB 90 and lower than HRB 95 substantially corresponds to the range where the ferrite area ratio in the matrix composition is smaller than 50% and larger than 25%.
- the area fraction of graphite is less than 6% and almost corresponds to the range of more than 3%.
- the height of the first plate surface force of the spiral portion is not more than twice the width of the groove (valley portion) of the spiral portion. Even if there is a large amount of removal before machine tools, it is a force that can be relatively easily applied to machine calories.
- the scroll component of this compressor is a die-casting iron having a component as described above. After being molded, semi-solid die-cast, die-quenched, and quenched, the whole is whitened, and then heat-treated to produce it. Therefore, the tensile strength of the spiral part can be sufficiently increased. Therefore, the design freedom of the spiral part is significantly improved, and the capacity can be increased if the diameter is reduced. Also, according to the experimental results obtained by the present inventor, when the hardness is in a range higher than HRB90 and lower than HRB100, the scroll component can exhibit sufficient durability during compressor operation, and It has been made clear that seizures occur as soon as possible and seizure does not occur during abnormal operation. For this reason, the scroll parts of this compressor have high tensile strength, can exhibit sufficient durability during operation, and as soon as "nazing" occurs as soon as possible, There is no burn-in during abnormal operation.
- a scroll part of a compressor according to an eleventh aspect of the invention is a scroll part of the compressor according to the tenth aspect of the invention, wherein in the spiral part, the draft for the forming die changes in accordance with the winding angle.
- the wrap shape is not determined according to the strength or the quality, and there is a problem that the material is wasted at the time of manufacturing the scroll.
- the mold is susceptible to stress when separating the scroll from the mold, since the radius of curvature of the wrap is smaller toward the center of the wrap having a spiral shape. For this reason, it is difficult to extend the life of the mold.
- the draft angle of the spiral part with respect to the forming die changes in accordance with the winding angle of the spiral part.
- the shape of the spiral part is determined according to the strength and the quality, and it is possible to eliminate the waste of the material.
- the scroll part of the compressor according to the twelfth aspect of the present invention is the scroll part of the compressor according to the eleventh aspect of the present invention, wherein the spiral part has a draft at the start of winding near the center with respect to the mold. It has a shape larger than the draft of the part.
- the spiral part is preferably set so that the draft gradually and gradually changes from the beginning of winding to the end of winding. The stress applied to the mold in the vicinity of the center of the spiral during mold release is reduced, the life of the mold can be extended, and waste of the material is made more effective. This is because it is possible to It is also preferable that the spiral part be set so that the draft gradually changes from the beginning of winding to the end of winding.
- the stress applied to the mold in the vicinity of the center of the spiral at the time of mold release is reduced, and the life of the mold can be extended, and the draft of the spiral part in each angular range can be easily set. It is also possible to eliminate waste of materials more effectively.
- the spiral portion is preferably set so that the draft angle is larger than the draft angles in other angular ranges in a predetermined angular range between the winding start and the winding end. The stress applied to the mold in the vicinity of the center of the spiral at the time of mold release is reduced, and the life of the mold can be extended, and the negative effect on the entire net of the spiral part is further reduced. It is also possible to do this, and also to make it possible to eliminate waste of material more effectively.
- At least the spiral part of this scroll part is preferably coated with a resin. Processing the coated resin is easier than processing the molded member directly, and therefore processing accuracy can be improved, and clogging of the gap reduces leakage of the compressed medium.
- the elasticity of the resin is a force that can reduce the noise even if the spiral parts are in contact with each other.
- the scroll part of the compressor according to the thirteenth aspect of the invention is the scroll part of the compressor according to the eleventh aspect, wherein the spiral part is a part at the beginning of the winding where the draft at the end of the outer end is close to the center of the draft. It has a spiral shape larger than the draft.
- the spiral part is preferably set so that the draft gradually and gradually changes from the beginning of winding to the end of winding. The stress applied to the mold in the vicinity of the center of the spiral during mold release is reduced, and the life of the mold can be extended, and waste of the material can be more effectively eliminated. is there.
- the spiral part be set so that the draft gradually changes from the beginning of winding to the end of winding.
- the spiral portion is set to have a draft angle larger than that in other angular ranges within a predetermined angular range between the winding start and the winding end.
- the stress applied to the mold in the vicinity of the center of the spiral at the time of mold release is reduced, and the life of the mold can be extended, and the adverse effect on the net weight of the entire spiral portion is further reduced. It is possible to eliminate waste of material more effectively.
- at least the spiral portion of this scroll part is coated with resin. This is because it is possible to reduce the leakage of the medium to be compressed and to reduce the noise.
- the draft at the end of the winding outside of the spiral part is larger than the draft at the beginning of the winding close to the center. Therefore, the thickness of the outer peripheral part of the spiral part is thin. Therefore, this is effective when it is difficult to obtain accuracy in processing, and even if the thickness of the spiral portion is thin, the accuracy of the outer peripheral portion of the spiral portion can be maintained.
- a scroll part of a compressor according to a fourteenth aspect of the present invention is the scroll part of the compressor according to the tenth aspect, wherein the spiral part is a first part on the inner peripheral side of the winding start near portion located near the center.
- the plane is inclined at a first angle with respect to a line perpendicular to the flat portion.
- the inclination angle with respect to the line orthogonal to the flat plate part is smaller than the first angle.
- the first surface of the spiral portion is preferably a surface which does not contact the other's scroll which is involved in relative movement of the fixed scroll and the movable scroll. A large inclination is usually a disadvantage in terms of surface accuracy control.
- the first surface is not in contact with the other scroll and does not affect the degree of sealing of the compression chamber. It does not occur.
- the surface other than the first surface of the spiral part is the inclination angle with respect to the line orthogonal to the flat part. Is preferably substantially 0 °. This is because the surface accuracy of the scroll can be maintained high, and it is possible to reduce the problem that the gas refrigerant leaks to the adjacent chamber during the operation of the scroll compressor.
- the inside is While the first surface on the circumferential side is inclined at the first angle to greatly increase strength and suppress deformation, the portion of the spiral part away from the center has a large capacity as an inclination angle smaller than the first angle. It is avoiding to fall.
- the surface on the outer peripheral side of the winding start vicinity of the spiral part is the surface that performs compression work in contact with the other's scroll, and if a large inclination is made, the contour shape at every height from the flat plate part of the spiral part.
- the refrigerant gas may leak at the contact portion of both scrolls.
- the inclination angle is smaller than the angle.
- the pressure is relatively low for the portions other than the portion near the winding start of the spiral portion, with emphasis given to capacity increase over strength and deformation amount.
- the inclination angle is reduced, and the first surface on the inner peripheral side of the winding start vicinity portion of the spiral part has a relatively high pressure, and the inclination angle is enlarged to emphasize strength increase and suppression of deformation,
- the angle of inclination of the outer peripheral surface of the winding start area is reduced in consideration of the control of surface accuracy and the degree of sealing of the compression chamber.
- the strength is secured by making the first angle slope in the vicinity of the winding start part of the spiral part where the pressure is high. The amount of deformation can be reduced to an acceptable level.
- the first surface located on the inner peripheral side of the winding start vicinity portion close to the center is inclined at a first angle ( ⁇ ) with respect to a line perpendicular to the flat plate portion. For this reason, in this scroll part, the strength of the central part of the spiral is enhanced. Therefore, in the scroll compressor in which such a scroll component is incorporated, the sliding component can withstand the stress increase due to the high differential pressure even when the high pressure refrigerant such as carbon dioxide is compressed. Also, this effect can increase the height of the scroll teeth.
- the capacity of the compression chamber can be increased while the diameter of the spiral portion is reduced.
- the scroll pressure by the small diameter of the scroll When the reduction diameter of the compressor is realized, the diameter of the body portion of the casing is reduced. When the body portion of the casing is reduced in diameter, the casing can exhibit the same compressive strength and a thinner wall thickness than a conventional casing. For this reason, the raw material cost etc. of the casing can be reduced.
- the scroll has a small diameter, the spiral portion can be made smaller to increase the sliding area of the thrust portion which is severe in sliding.
- the scroll has a surface roughness smaller than that obtained by the conventional roving method.
- the scroll part of the compressor according to the fifteenth invention is the scroll part of the fourteenth invention, wherein the winding start vicinity part of the spiral part has a larger thickness at the boundary with the flat plate part than the other parts of the spiral part. .
- the sliding component base of the compressor according to the sixteenth invention has a carbon content of 2.0 wt% to 2.7 wt%, a carbon content of 1. Owt% to 3. Owt%, and the balance is inevitable.
- the hardness is at least partially higher than HRB 90 and lower than HRB 100, at least in part where the iron containing impurities is formed and the graphite is smaller than the flake graphite of flake graphite base iron.
- the hardness is more preferably higher than HRB 90 and lower than HRB 95.
- the term “sliding component base” as used herein means a precursor before machining (finishing) to obtain a sliding component.
- the cutting edge may be easily formed during machining of the sliding component substrate, which may deteriorate chip treatability.
- the hardness of the sliding part substrate is HRB 100 or more, the occurrence of wear and chipping of the cutting tool and the like is suppressed in the machining of the sliding part substrate.
- the machining cost may increase, and the cutting resistance may increase, and the machining cost may also increase due to the limitations of the cutting depth and the cover speed.
- the area fraction of ferrite in the matrix composition substantially corresponds to the range of 50% to 5%.
- the graphite area ratio almost corresponds to the range of 6% to 2%. Further, the range in which the hardness is higher than HRB 90 and lower than HRB 95 substantially corresponds to the range in which the area fraction of ferrite in the matrix composition is smaller than 50% and larger than 25%. In addition, the area fraction of graphite is less than 6% and almost corresponds to the range of more than 3%.
- Molded articles obtained by semi-solid die-casting, semi-solid die-casting, die-quenching forming, quenching by an iron having the components as described above, and quenching the whole as a whole are heat-treated by heat treatment.
- the tensile strength can be adjusted. And it has been found that the tensile strength of a molded article produced through this heat treatment is in proportion to its hardness. By the way, in the range where hardness is higher than HRB90 and lower than HRBIOO, the tensile strength almost corresponds to the range of 600MPa to 900MPa. In other words, management of the tensile strength of a molded article can be substituted by a hardness that is easy to measure.
- the sliding component base is a scroll component base
- design freedom of the spiral part is greatly improved and small diameter and large capacity can be achieved.
- the sliding component substrate of this compressor exhibits higher tensile strength than sliding component substrates such as flake graphite pig iron.
- iron having the above components is subjected to semi-melt die-casting, semi-solid die-casting, mold forming, quenched, and the whole is bleached, Further, in the case where the sliding component base subjected to the heat treatment is machined to complete the sliding component, it is preferable that the hardness of the sliding component base is in the range higher than HRB90 and lower than HRBIOO.
- the sliding component base is ground In this case, the surface roughness is smaller than that of the FC material, so the sliding parts on the other side (if the sliding parts are movable scrolls, do not attack the Oldham ring, seal ring, etc.).
- the sliding component base of this compressor has high tensile strength and exhibits good machinability when machining is required.
- the compressor according to the seventeenth invention has a carbon content of 2.0 wt% to 2.7 wt%, a carbon content of 1. Owt% to 3. Owt%, and the balance is an unavoidable impurity.
- a sliding component is incorporated, in which at least part of the hardness is smaller than HRB 90 and lower than HRB 100, and the hardness of the graphite is smaller than that of flake graphite of flaky graphite base iron.
- the “compressor” is, for example, a scroll compressor, a swing compressor, a rotary compressor or the like.
- the hardness is more preferably higher than HRB90 and lower than HRB95.
- the area fraction of ferrite in the matrix composition substantially corresponds to the range of 50% to 5%.
- the graphite area ratio almost corresponds to the range of 6% to 2%.
- the range in which the hardness is higher than HRB 90 and lower than HRB 95 substantially corresponds to the range in which the area fraction of ferrite in the matrix composition is smaller than 50% and larger than 25%.
- the area fraction of graphite is less than 6% and almost corresponds to the range of more than 3%.
- adjustment of hardness can be realized by heat treatment after molding.
- iron having the above components is subjected to semi-melt die-casting, semi-solid die-casting, die-quenching, and quenching followed by quenching to heat-treat the entire molded article.
- the tensile strength of a molded article produced through this heat treatment is in proportion to its hardness.
- the tensile strength substantially corresponds to the range of 600 MPa to 900 MPa.
- management of tensile strength of molded articles can be substituted by hardness that can be easily measured.
- the sliding part has a carbon content of 2.0 wt% to 2.7 wt%, a carbon content of 1. Owt% to 3. Owt%, and the balance is an unavoidable impurity. Since it is composed of iron and graphite is smaller than flake graphite of flake graphite pig iron, reduction of thickness of each part enables reduction of thrust loss due to small diameter or large capacity, and FC material and In comparison, because of its excellent toughness, damage to sudden internal pressure rise and foreign matter entrapment is likely to occur, and even if it is damaged, fineness and dust are produced. You can enjoy the benefits, etc. By the way, it can be said that such a compressor is particularly suitable for compressors for renewal demand.
- a compressor according to an eighteenth aspect of the present invention is the compressor according to the seventeenth aspect of the present invention, which is a carbon dioxide (CO.sub.2).
- This compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor is compatible with carbon dioxide (CO 2) refrigerants. Because of this, this compressor
- the sliding component of the compressor according to the first aspect of the present invention has high tensile strength, can exhibit sufficient durability during operation, and “follows up” as soon as possible. Soon, there will be no seizure during abnormal operation.
- the sliding parts of this compressor have a carbon content of 2.0 wt% to 2.7 wt%, a carbon content of 1.0 wt% to 3. Owt%, and the balance including unavoidable impurities. Since the iron power and the graphite are smaller than the flake graphite of flake graphite pig iron, the reduction in thickness of each part makes it possible to reduce the thrust loss and large capacity by the small diameter, and compared with the FC material.
- the sliding part base is formed into an ant shape. be able to. Therefore, the sliding parts of this compressor can reduce the machining cost and can be manufactured more inexpensively.
- the sliding part of the compressor according to the third aspect of the present invention requires low pressure during the molding process. Therefore, the pressing device and the heating device required for die cast molding are not required, and the cost for equipment can be reduced. As a result, the sliding parts of this compressor have a lower molding cost and can be made cheaper.
- the ratio of the spiral part taking into consideration the upper limit of the deformation amount of the spiral part required for processing time, performance deterioration, noise and!
- HZT how much tensile strength is sufficient in terms of fatigue strength
- heat treatment may be carried out with an excessive increase in strength due to cost.
- the hardness of that part is higher than HRC50 and lower than HRC65. Can be sufficiently suppressed.
- the occurrence of scum can be suppressed.
- the occurrence of scum is suppressed.
- even if a through hole is formed at the planned opening portion there is a fear that the koji mold inside the sliding component may be exposed to the outside, and it is also possible to suppress a decrease in fatigue strength.
- the scroll component of the compressor according to the tenth aspect of the invention has high tensile strength, can exhibit sufficient durability during operation, and "follows up" as early as possible. Soon, there will be no burn-in during abnormal operation.
- the shape of the spiral part is determined according to the strength and the quality, and it is possible to eliminate the waste of the material.
- the thirteenth invention even if the thickness of the spiral portion is thin, the accuracy of the outer peripheral portion of the spiral portion can be maintained.
- the pressure in the portion other than the winding start vicinity portion of the spiral portion is relatively low, so that the strength of the spiral portion and the scroll portion
- the inclination angle is reduced with emphasis on capacity increase rather than deformation, and for the first surface on the inner peripheral side near the winding start of the spiral part, the pressure is relatively high, so that the strength increase and suppression of deformation are emphasized
- the inclination angle is increased, and the inclination angle is reduced in consideration of the control of the surface accuracy and the degree of sealing of the compression chamber for the surface on the outer peripheral side in the vicinity of the winding start of the spiral part.
- the strength is secured by making the first angle slope in the vicinity of the winding start part of the spiral part where the pressure is high.
- the amount of deformation can also be reduced to an acceptable level.
- the sliding component base of the compressor according to the sixteenth invention has high tensile strength and exhibits good machinability when machining is required.
- the compressor according to the seventeenth aspect of the invention utilizes sliding parts with higher tensile strength than sliding parts such as flake graphite pig iron.
- the sliding component can exhibit sufficient durability during compressor operation, and It has been clarified that "friendship” occurs as soon as possible, and that no burn-in occurs during abnormal operation. For this reason, this compressor has high tensile strength and is sufficient in operation. Durability can be developed, and as soon as possible, "adaptation” can occur as soon as possible, and seizure can be prevented from occurring during abnormal operation.
- the carbon content is 2.0 wt% to 2.7 wt%
- the silicon content is 1.
- the compressor according to the eighteenth aspect of the present invention can contribute to global environmental problems.
- FIG. 1 is a longitudinal sectional view of a high and low pressure dome-type scroll compressor according to a first embodiment.
- FIG. 2 A bottom view of a fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 3 is a cross-sectional view of a fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 4 A top view of a movable scroll incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 5 A VV sectional view of a movable scroll incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 6 is a top view of an Oldham ring incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 7 is a side view of an Oldham ring incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 8 is a bottom view of an Oldham ring incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 9 A sectional view showing a mold for manufacturing a fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the first embodiment and a base of the fixed scroll formed by semi-melt die casting.
- FIG. 10 is an enlarged view of a planned opening portion of a fixed scroll base incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 11 is a longitudinal sectional view of a mold for manufacturing a movable scroll incorporated in the high and low pressure dome-type scroll compressor according to the first embodiment and a movable scroll base formed by semi-molten die casting.
- FIG. 12 is an enlarged view of a central portion of a movable scroll base incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 13 A longitudinal sectional view showing a base of a conventional fixed scroll.
- FIG. 14 A longitudinal sectional view of a base of a conventional movable scroll.
- FIG. 15 is a longitudinal sectional view of a crankshaft incorporated in the high and low pressure dome type scroll compressor according to the first embodiment.
- FIG. 16 (a) A diagram showing a partition wall area in a conventional fixed scroll.
- FIG. 17 (a) A diagram showing a partition wall area in a conventional movable scroll. (B) A diagram showing a compression work area in a conventional movable scroll. (C) A diagram showing a thrust area in a conventional movable scroll. (D) The figure which shows the partition area in the movable scroll which concerns on 1st Embodiment.
- (E) A diagram showing a compression work area in the movable scroll according to the first embodiment.
- FIG. 18 (a) A diagram showing a suction volume formed by a conventional scroll. (B) A diagram showing a suction volume formed by the scroll according to the first embodiment.
- FIG. 19 A schematic view of a test apparatus used for the abrasion resistance test and the seizure resistance test of a molded article produced by a half melt die casting method.
- FIG. 20 Relation between hardness and wear resistance of molded articles produced by semi-melt die-casting method Graph representing the relationship.
- FIG. 21 is a graph showing the relationship between the hardness and the “matching” of the scroll parts manufactured by the semi-melt die casting method.
- FIG. 22 is a graph showing the relationship between hardness and seizure resistance of a molded article produced by the semi-melt die casting method.
- FIG. 23 is a graph showing the relationship between hardness and tensile elongation of a molded article produced by the semi-melt die casting method.
- FIG. 24 is a graph showing the relationship between the cutting depth and the cutting resistance of a molded product produced by semi-melt die casting.
- FIG. 25 A graph showing a comparison of the amount of blade wear of molded articles produced by the semi-melt die-casting method.
- FIG. 26 A simplified process diagram of a die forming process according to a modification of the first embodiment.
- FIG. 27 A magnified view of an opening planned portion of a fixed scroll base according to a modification ( ⁇ ⁇ ) of the first embodiment.
- FIG. 28 An enlarged view of an opening scheduled portion of a fixed scroll base according to a modification ( ⁇ ⁇ ) of the first embodiment.
- FIG. 29 Modification of the first embodiment (L) A sectional view of a movable scroll according to the present invention.
- FIG. 30 is an enlarged view of an opening scheduled portion of a movable scroll according to a modification (L) of the first embodiment.
- FIG. 31 An enlarged view of an opening scheduled portion of a movable scroll according to a modification (L) of the first embodiment.
- FIG. 32 (a) A diagram showing a suction volume formed by a conventional scroll.
- FIG. 33 is a cross-sectional view of the inner drive type movable scroll according to the second embodiment.
- FIG. 34 is a cross-sectional view showing a die for manufacturing the movable scroll according to the second embodiment and a base of the movable scroll molded by semi-melting die casting.
- FIG. 35 is a cross-sectional view of a mold for manufacturing a movable scroll incorporated in the high and low pressure dome type scroll compressor according to the third embodiment and a movable scroll formed by semi-melt die casting.
- FIG. 36 A movable sleeve incorporated in the high and low pressure dome type scroll compressor according to the third embodiment.
- FIG. 37 A top view of a movable closure to be incorporated into the high and low pressure dome type scroll compressor according to the third embodiment.
- a 38 A sectional view of a movable scroll incorporated in a high and low pressure dome-type scroll compressor according to a third embodiment.
- ⁇ 40 A bottom view of a fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the third embodiment.
- FIG. 41 A cross section view of a fixed scroll to be incorporated into the high and low pressure dome type scroll compressor according to the third embodiment.
- FIG. 42 is a graph showing the relationship between the winding angle ex and the draft angle ⁇ ⁇ of the movable scroll according to the modification ( ⁇ ) of the third embodiment.
- FIG. 43 A modified example of the third embodiment ( ⁇ ) A graph showing the relationship between the winding angle ex of the movable scroll and the draft angle ⁇ .
- FIG. 45 A modified example of the third embodiment (D) A sectional view of a movable scroll manufactured by resin-coating the movable scroll.
- a modified example of the third embodiment (F) A longitudinal sectional view of a fixed scroll according to the present invention.
- ⁇ 48 A longitudinal sectional view of a mold for manufacturing a movable scroll incorporated in a high and low pressure dome-type scroll compressor according to a fourth embodiment and a movable scroll base formed by semi-molten die casting.
- FIG. 49 A bottom view of a fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- ⁇ 50 A bottom view of a fixed scroll base according to a fourth embodiment.
- FIG. 52 is a D-D cross-sectional view of a fixed scroll incorporated in the high and low pressure dome-type scroll compressor according to the fourth embodiment.
- FIG. 53 A partially enlarged view of a D-D cross section of the fixed scroll incorporated in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- FIG. 54 is a longitudinal sectional view of a movable scroll incorporated in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- FIG. 55 is a view showing how the gas refrigerant is compressed due to a change in the state of kneading of the wraps of both scrolls in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- FIG. 56 is a view showing how the gas refrigerant is compressed due to a change in a state in which the wraps of both scrolls are mixed in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- FIG. 57 is a view showing how the gas refrigerant is compressed due to a change in a state in which the wraps of both scrolls are mixed in the high and low pressure dome type scroll compressor according to the fourth embodiment.
- FIG. 58A is a view showing the range of the surface on the inner peripheral side of the winding start vicinity portion of the fixed scroll wrap according to the fourth embodiment.
- (B) A diagram showing the range of the surface on the inner peripheral side of the winding start vicinity portion of the wrap of the movable scroll according to the fourth embodiment.
- FIG. 59 is a longitudinal sectional view of a swing compressor according to a fifth embodiment.
- FIG. 60 is a top view of a cylinder block according to a fifth embodiment.
- FIG. 61 is a transverse sectional view of a cylinder chamber of a swing compressor according to a fifth embodiment.
- FIG. 62 is a top view of a piston of a swing compressor according to a fifth embodiment.
- FIG. 63 A top view of a cylinder block of a rotary compressor according to a modification (A) of the fifth embodiment.
- FIG. 64 is a cross-sectional view of a cylinder chamber of a rotary compressor according to a modification (A) of the fifth embodiment.
- SC1 Peripheral part of the base of wrap of fixed scroll (partial heat treatment area, stress concentration area)
- SC5 Notches formed near the design center of the end plate of the bearing of the movable scroll (partial heat treatment area, stress concentration area)
- the high and low pressure dome type compressor according to the first embodiment can withstand a high pressure refrigerant such as a carbon dioxide refrigerant (CO 2) R410A as a refrigerant.
- a high pressure refrigerant such as a carbon dioxide refrigerant (CO 2) R410A as a refrigerant.
- the high and low pressure dome type scroll compressor 1 constitutes a refrigerant circuit together with an evaporator, a condenser, an expansion mechanism and the like, and plays a role of compressing the gas refrigerant in the refrigerant circuit.
- a scroll compression mechanism 15 As shown in FIG. 1, mainly from a cylindrical closed dome type casing 10, a scroll compression mechanism 15, an Oldham ring 39, a drive motor 16, a lower main bearing 60, an intake pipe 19 and a discharge pipe 20. It is configured.
- this high and low pressure dome type scroll pressure The components of the compressor 1 will be described in detail.
- the casing 10 mainly includes a substantially cylindrical trunk portion casing portion 11, a bowl-shaped upper wall portion 12 airtightly welded to the upper end portion of the trunk portion casing portion 11, and a lower end portion of the trunk portion casing portion 11. And the bottom wall 13 of the bowl-like shape which is welded in an airtight manner.
- the casing 10 mainly accommodates the scroll compression mechanism 15 for compressing the gas refrigerant and the drive motor 16 disposed below the scroll compression mechanism 15.
- the scroll compression mechanism 15 and the drive motor 16 are connected by a crank shaft 17 disposed so as to extend in the vertical direction in the casing 10. As a result, a gap space 18 is generated between the scroll compression mechanism 15 and the drive motor 16.
- the scroll compression mechanism 15 mainly includes a housing 23, a fixed scroll 24 closely disposed above the housing 23, and a movable scroll 26 fitted to the fixed scroll 24. It is configured.
- the components of the scroll compression mechanism 15 will be described in detail below.
- the housing 23 is press-fitted and fixed to the body casing 11 along the entire circumferential direction on the outer peripheral surface thereof. That is, the body casing portion 11 and the housing 23 are in close contact along the entire circumference. For this reason, the inside of the casing 10 is divided into a high pressure space 28 below the housing 23 and a low pressure space 29 above the housing 23. Further, the fixed scroll 24 is fastened and fixed to the housing 23 by a bolt 38 so that the upper end surface is in close contact with the lower end surface of the fixed scroll 24. Further, the housing 23 is formed with a housing recess 31 recessed at the center of the upper surface, and a bearing portion 32 extended downward from the center of the lower surface. Further, a bearing hole 33 penetrating in the vertical direction is formed in the bearing portion 32, and the main shaft portion 17 b of the crankshaft 17 is rotatably fitted in the bearing hole 33 via a bearing 34.
- this housing 23 is manufactured by a novel and special manufacturing method. Manufactured. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part” below.
- the fixed scroll 24 mainly comprises an end plate 24a and a spiral (involute) wrap 24b extending downward from the mirror surface 24P of the end plate 24a, as shown in FIGS.
- a discharge hole 41 communicating with a compression chamber 40 described later and an enlarged recess 42 communicating with the discharge hole 41 are formed.
- the discharge hole 41 is formed to extend upward and downward in the central portion of the end plate 24a.
- the enlarged recess 42 is a recess formed to extend in the horizontal direction on the upper surface of the end plate 24a.
- the discharge holes 41 are to be formed thin, it is possible to reduce The occurrence of (see Figure 9) is suppressed.
- the ratio of the height of the thick wrap 24b to the wrap 24b is 15 or more.
- the corners and corners of the wrap 24b are rounded to fit the corners and corners of the wrap 26b of the movable scroll.
- a lid 44 is fastened and fixed to the upper surface of the fixed scroll 24 by a bolt 44 a so as to close the enlarged recess 42.
- a cover 44 covers the enlarged recess 42 to form a muffler space 45 for silencing the operation noise of the scroll compression mechanism 15.
- the fixed scroll 24 and the lid 44 are sealed by bringing them into close contact via a packing (not shown).
- the fixed scroll 24 is manufactured by a novel and special manufacturing method. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part" below.
- the movable scroll 26 is an outer drive type movable scroll, and as shown in FIG. 1, FIG. 4 and FIG. 5, mainly spirals extending upward from the mirror plate 26a and the mirror surface 26P of the mirror plate 26a. And a bearing 26c extending downward from the lower surface of the end plate 26a and fitted on the outside of the crankshaft 17 and grooves 26d (see FIG. 5) formed at both ends of the end plate 26a. There is.
- the movable scroll 26 is supported by the housing 23 by fitting the Oldham ring 39 (see FIG. 1) into the groove 26 d. Further, the eccentric shaft portion 17a of the crankshaft 17 is fitted into the bearing portion 26c.
- the movable scroll 26 revolves the inside of the housing 23 without rotating by rotation of the crankshaft 17 by being thus incorporated into the scroll compression mechanism 15.
- the wrap 26b of the movable scroll 26 is joined to the wrap 24b of the fixed scroll 24, and a compression chamber 40 is formed between the contact portions of the two wraps 24b and 26b (see FIG. 18 (b)). .
- the compression chamber 40 as the movable scroll 26 revolves, it is displaced toward the center, and its volume contracts.
- the gas refrigerant thus entering the compression chamber 40 is compressed.
- the movable scroll 26 is manufactured by a novel and special manufacturing method. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part" below.
- a communication passage 46 is formed between the fixed scroll 24 and the housing 23.
- the communication passage 46 is composed of a scroll side passage 47 cut out in the fixed scroll 24 and a housing side passage 48 cut out in the housing 23.
- the upper end of the communication passage 46 that is, the upper end of the scroll passage 47, is open to the enlarged recess 42
- the lower end of the communication passage 46 that is, the lower end of the housing passage 48 is open to the lower end face of the housing 23. That is, the lower end opening of the housing side passage 48 is a discharge port 49 which allows the refrigerant in the communication passage 46 to flow out to the gap space 18.
- the Oldham ring 39 is a member for preventing the rotational movement of the movable scroll 26, as shown in FIGS. 6 to 8 [Fig. 6 to 8]. , 39b and housing side key parts 39c, 39d.
- the main body 39e is a substantially annular molded body as shown in FIG. 6 and FIG.
- the movable scroll side key portions 39a and 39b are a pair of protrusions which are opposed to each other across the axis of the main body 39e and which extend to the outer peripheral side of the radial direction of the main body 39e.
- the housing side key portions 39c, 39d are opposed to each other with the axis of the main body 39e interposed therebetween, and the protruding portion force extending radially outward of the main body 39e is along the axial direction.
- the movable scroll side key portions 39a and 39c are a pair of protrusions extending on the opposite side, and are disposed at a position inclined approximately 90.degree. From the movable scroll side key portions 39a and 39b about the axis. Then, the movable scroll side key portions 39a, 39b are fitted into the groove portion 26d of the movable scroll 26, and the housing side key portions 39c, 39d are fitted into the Oldham groove (not shown) formed in the housing 23.
- the Oldham's groove is an oval groove, and is disposed in the housing 23 so as to face each other.
- this Oldham ring 39 is manufactured by a new and special manufacturing method. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part" below.
- the drive motor 16 is a direct current motor in the first embodiment, and mainly rotates in an annular stator 51 fixed to the inner wall surface of the casing 10, and a slight gap (a gap gap passage) inside the stator 51. It comprises a rotor 52 housed freely.
- the drive motor 16 is disposed such that the upper end of the coil end 53 formed on the upper side of the stator 51 is at substantially the same height position as the lower end of the bearing portion 32 of the housing 23.
- a copper wire is wound around the teeth of the stator 51, and coil ends 53 are formed on the upper and lower sides. Further, on the outer peripheral surface of the stator 51, core cut portions are formed at a plurality of locations at predetermined intervals in the circumferential direction from the upper end surface to the lower end surface of the stator 51. Then, a motor cooling passage 55 extending in the vertical direction is formed between the body casing 11 and the stator 51 by the core cut portion.
- the rotor 52 is drivably coupled to the movable scroll 26 of the scroll compression mechanism 15 via a crank shaft 17 disposed at the axial center of the body casing portion 11 so as to extend in the vertical direction. Further, a guide plate 58 for guiding the refrigerant flowing out of the discharge port 49 of the communication passage 46 to the motor cooling passage 55 is disposed in the gap space 18.
- the crankshaft 17 is a substantially cylindrical integrally formed part, and mainly comprises an eccentric shaft portion 17a, a main shaft portion 17b, a lance weight portion 17c and a countershaft portion 17d.
- the eccentric shaft portion 17 a is accommodated in the bearing portion 26 c of the movable scroll 26.
- the main shaft portion 17 b is accommodated in the bearing hole 33 of the housing 23 via the bearing 34.
- the countershaft portion 17d is accommodated in the lower main bearing 60.
- crankshaft 17 is manufactured by a novel and special manufacturing method. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part" below.
- the lower main bearing 60 is disposed in the lower space below the drive motor 16.
- the lower main bearing 60 is fixed to the body casing portion 11 and constitutes a lower end side bearing of the crankshaft 17, and accommodates the countershaft portion 17d of the crankshaft 17.
- the lower main bearing 60 is manufactured by a novel and special manufacturing method. This manufacturing method will be described in detail in the section "Method for Manufacturing Sliding Part" below.
- the suction pipe 19 is for guiding the refrigerant of the refrigerant circuit to the scroll compression mechanism 15, and is fitted in the upper wall 12 of the casing 10 in an airtight manner.
- the suction pipe 19 vertically penetrates the low pressure space 29 and has an inner end fitted in the fixed scroll 24.
- the discharge pipe 20 is for discharging the refrigerant in the casing 10 to the outside of the casing 10, and is fitted in the body casing portion 11 of the casing 10 in an airtight manner.
- the discharge pipe 20 has an inner end portion 36 which is formed in a vertically extending cylindrical shape and fixed to the lower end portion of the housing 23. The inner end opening of the discharge pipe 20, that is, the inlet is opened downward.
- crankshaft 17, the housing 23, the fixed scroll 24, the movable scroll 26, the oldham ring 39 and the lower main bearing 60 are sliding parts, and these slides
- the parts are manufactured by the following manufacturing method.
- “billet” means, at one end, a material before final forming, which is formed into a cylindrical shape or the like by a continuous forming apparatus after the iron material of the above component is melted in a melting furnace.
- the contents of C and Si indicate that the tensile strength and the tensile elastic modulus are higher than those of flake graphite pig iron, and the flowability suitable for forming a sliding component base having a complicated shape. It is decided to satisfy both of the provision.
- the content of Ni is determined so as to constitute a metal composition suitable for improving the toughness of the metal structure and preventing surface cracks during molding.
- the sliding component according to the first embodiment is manufactured through a semi-solid die casting process, a heat treatment process, a finishing process and a partial heat treatment process. Each step will be described in detail below.
- the billet is brought into a semi-melted state by high frequency heating.
- the billet in the semi-molten state is poured into a predetermined mold, the billet is formed into a desired shape while applying a predetermined pressure with a die casting machine to obtain a sliding component base.
- the sliding component base is taken out of the mold and rapidly cooled, the metallographic structure of the sliding component base becomes white as a whole.
- the sliding part substrate is slightly larger than the finally obtained sliding part, and this sliding part substrate is removed in the final finishing step from the machining allowance to become the final sliding part.
- the base 124 of the fixed scroll 24 is molded using the mold 70 shown in FIG. 9, and the base 126 of the movable scroll 26 uses the mold 80 shown in FIG. It is molded.
- the mold 70 for semi-melt die-casting the base 124 of the fixed scroll 24 comprises a first mold portion 71 and a second mold portion 72.
- Type 1 part 71 and Type 2 The shape of the space 73 created when the part 72 is combined corresponds to the outer shape of the fixed scroll 24 (ie, the base 124) before cutting.
- a convex portion is formed in order to form an opening planned portion P which is a portion planned to open the discharge hole 41 in the vicinity of the center of the base 124 of the fixed scroll 24.
- 71a and the convex portion 72a are formed to face each other. Since the distance between the convex portion 71a and the convex portion 72a is set to 4 mm or less, the thickness t2 (see FIGS. 9 and 10) of the opening planned portion P becomes thin to 4 mm or less. It is possible to further suppress the occurrence.
- the wall thickness is as thick as the surrounding wall thickness. Accordingly, since the gonorrhoid CN is also generated near the center of the end plate equivalent portion 224a, it is generated in a wide range inside the end plate equivalent portion 224a. For this reason, when the discharge hole 241 (portion surrounded by two imaginary lines in FIG. 13) is formed by the drill calorie in the opening planned portion Q in the vicinity of the center of the base body 224, the Kokasu CN from the discharge hole 241 Exposed to the outside. As a result, the fatigue strength of the fixed scroll after manufacture is significantly reduced.
- the mold 80 for semi-melt die-casting the base 126 of the movable scroll 26 comprises a first mold portion 81 and a second mold portion 82.
- the shape of the space portion 83 formed when the first mold portion 81 and the second mold portion 82 are combined corresponds to the external shape of the movable scroll 26 (ie, the base 126) before cutting.
- the first type portion 81 is formed with a convex portion 8 la which forms an internal space 26 f (see FIG. 5) of the bearing portion 26 c of the movable scroll 26. Since the distance between the convex portion 81a and the second type portion 82 is set to 4 mm or less, the thickness t1 of the center portion of the head plate equivalent portion of the base 126 of the movable scroll 26 (see FIGS. 11 and 12). ) Becomes thinner than 4 mm. Therefore, in this part, the occurrence of CN of CN is suppressed.
- the base 126 of the movable scroll 26 is compared with the movable scroll of the inner drive, that is, the base of the movable scroll in which the bearing portion of the solid round bar is fitted inside the drive shaft. As a result, the thickness of the central portion 26e of the mirror equivalent portion becomes thinner. For this reason, when compared with the movable scroll of the inner drive, this movable scroll 26 is more likely to suppress the occurrence of scab CN.
- the thickness of the central portion 226e is the thickness of the peripheral portion As thick as. Therefore, a large amount of CN is also generated near the center of the mirror equivalent 226a. For this reason, the strength of the movable scroll formed by such a method is reduced.
- the central portion 226e since the central portion 226e generates the largest gas load (or pressure) during operation of the scroll compressor, the end plate may be deformed if the strength of the central portion 226e is reduced. Furthermore, if the end plate is deformed, the sliding condition between the movable scroll and the fixed scroll is deteriorated, which causes wear and seizing.
- the sliding component substrate after the semi-melt die casting step is heat treated.
- the metallographic structure of the sliding component base is changed to a metallographic structure consisting of white graphite, pearlite Z ferrite base and granular graphite.
- the graphitization and pearlization of this whitened structure can be controlled by adjusting the heat treatment temperature, holding time, cooling rate and the like. For example, as described in Honda R & D Technical Review, Vol. 14 No. 1 “Study on semi-solid forming technology of iron”, after holding at 950 ° C. for 60 minutes, 0.5 ° to 0. 0 ° to 10 ° C.
- the tensile strength about 600 MPa to 900 MPa, HB200 (HRB96 (SAE J 417 Converted value from hardness conversion table)) to HB250 (HRB105, HRC26 (converted value from SAE J 417 hardness conversion table, HRB 105 is a reference value because it exceeds the effective practical range of the test type))
- HRB 105 is a reference value because it exceeds the effective practical range of the test type
- the hardness of the sliding component substrate is higher than HRB 90 (value converted from SAE J 417 hardness conversion table) HRB 100 ( Heat treatment is performed under conditions that are lower than HB219 (SAE J 417 hardness conversion table force conversion value).
- HRB 90 value converted from SAE J 417 hardness conversion table
- HRB 100 Heat treatment is performed under conditions that are lower than HB219 (SAE J 417 hardness conversion table force conversion value).
- the hardness of the sliding component base is in proportion to the tensile strength of the sliding component base.
- the tensile strength of the sliding component substrate at this time substantially corresponds to the range of 600 MPa to 900 MPa.
- the hardness of the sliding component substrate is higher than HRB 90 (value converted from SAE J 417 hardness conversion table) HRB 100 (HB 219 (SAE J 417 hardness) Heat treatment is performed under conditions that are lower than the conversion table).
- HRB 90 value converted from SAE J 417 hardness conversion table
- HRB 100 HB 219 (SAE J 417 hardness) Heat treatment is performed under conditions that are lower than the conversion table.
- the hardness of the sliding component base is in proportion to the tensile strength of the sliding component base.
- the tensile strength of the sliding component substrate at this time substantially corresponds to the range of 600 MPa to 900 MPa.
- heat treatment is performed so that the ratio of tensile strength to Young's modulus becomes equal to or less than 0. 0046.
- the ferrite ratio can be kept low enough to ensure wear resistance.
- the ratio of tensile strength to Young's modulus is set so that the component cutting edge is difficult to form during cutting
- Heat treatment is carried out so as to be above. Since the Young's modulus is 175 to 190 GPa regardless of the heat treatment, the heat treatment is performed so that the bow I tensile strength is about 600 MPa to 900 MPa.
- the sliding component substrate is machined to complete the sliding component.
- the discharge hole 41 which is a through hole is formed in the planned opening P and the lap equivalent portion is cut by an end mill etc.
- the height H and the thickness T from the mirror surface 24P to the tip end are made to be dimensions according to predetermined design values.
- the lap equivalent portion is cut by an end mill or the like, and a notch (counterbore) SC5 for stress dispersion of gas load is formed by an end mill or the like.
- a notch (counterbore) SC5 for stress dispersion of gas load is formed by an end mill or the like.
- the height H and the thickness T from the mirror surface 26P to the tip end are made to be dimensions according to predetermined design values.
- the notch (counterbore) SC5 plays the role of dispersing the stress at the root of the wrap 26b where the stress concentrates most.
- the height H and thickness T of the wraps 24b and 26b are the fixed scroll 24 and movable.
- the ratio (H / T) is designed to be in the range of 10-19.
- the height H and thickness T of the wraps 24b, 26b are Is the ratio of the tensile strength to the Young's modulus of the fixed scroll 24 and the movable scroll 26 ⁇ 0. 0033-0. 0046! /, Assuming that it (H / T) force 2 to 8 become Is designed as.
- the tip of the end of the spiral center (end at the beginning of winding) of the wraps 24b and 26b is obtained even when the gas refrigerant carbon dioxide, which is a gas refrigerant, is at the highest pressure in the refrigeration system.
- the amount of deflection falls within the allowable range, there will be no problem in terms of strength.
- high frequency calorific heat treatment is performed on a specific portion of the sliding component, and laser heat treatment is performed to improve the fatigue strength and wear resistance of the specific portion.
- laser heat treatment and the high frequency heat treatment laser light or high frequency is applied so that the surface hardness of the heated portion becomes HRC50: HRC65.
- the laser is applied to the peripheral portion SC3 of the base of the wrap 26b and the peripheral portion SC4 of the base of the bearing 26c where stress is concentrated during operation of the high and low pressure dome type scroll compressor 1.
- the heat treatment is applied, and the notch SC5 formed near the design center of the end plate 26a and the innermost SC6 of the wrap 26b are subjected to high-frequency heat treatment (see FIGS. Are hatched).
- the eccentric shaft portion 17a and the main shaft portion 17b for which wear resistance is required are subjected to high frequency heat treatment, and the eccentric shaft portion 17a and the main shaft where stress is concentrated during operation of the compressor.
- Laser heat treatment is performed on the peripheral portion SC7 of the notch portion existing between the portion 17b and the portion 17b (see FIG. 15. In the figure, the laser heat treatment portion is hatched).
- the operation of the high and low pressure dome type compressor 1 will be briefly described.
- the drive motor 16 is driven, the crankshaft 17 is rotated, and the orbiting operation is performed without the movable scroll 26 rotating.
- the low pressure gas refrigerant is drawn into the compression chamber 40 from the peripheral side of the compression chamber 40 through the suction pipe 19 and is compressed along with the volume change of the compression chamber 40 to become a high pressure gas refrigerant (FIG. 18) see (b)).
- the high-pressure gas refrigerant is discharged from the central portion of the compression chamber 40 through the discharge hole 41 to the muffler space 45, and thereafter, the communication passage 46, the scroll side passage 47, the housing side passage 48, the discharge port 49.
- the fluid flows into the gap space 18 and flows downward between the inner plate 58 and the inner surface of the trunk casing 11 in a downward direction. Then, when the gas refrigerant flows downward between the guide plate 58 and the inner surface of the body casing portion 11, a part of the gas refrigerant is branched and flows between the guide plate 58 and the drive motor 16. It flows in the circumferential direction. At this time, the lubricating oil mixed in the gas refrigerant is separated.
- the other part of the branched gas refrigerant flows downward to the motor cooling passage 55 and flows to the lower space of the motor and then reverses to form an air gap passage between the stator 51 and the rotor 52, or It flows upward through the motor cooling passage 55 on the side (left side in FIG. 1) opposite to the communication passage 46.
- the gas refrigerant that has passed through the guide plate 58 and the gas refrigerant that has flowed through the air gap passage or the motor cooling passage 55 merge at the gap space 18 and the discharge pipe 20 from the inner end 36 of the discharge pipe 20.
- the gas refrigerant discharged out of the casing 10 circulates through the refrigerant circuit, and is again sucked into the scroll compression mechanism 15 through the suction pipe 19 and compressed.
- FIG. 16 to FIG. 18 a conventional fixed scroll 324 using FC 250, a movable scroll 326, and a first
- the fixed scroll 24 and the movable scroll 26 of the compressor 1 according to the embodiment are compared with it.
- the height H of each of the wraps 285, 287, 24b, 26b of the respective scroll holes 324, 326, 24, 26 is the same, and the conventional fixed scroll 324 and movable scroll 326 are designed according to the conventional strength.
- the thickness T of the wraps 24b and 26b is determined on the fixed scroll 24 and the movable scroll 26 based on the above-mentioned design guidelines.
- Fixed scroll 24, movable scroll 26, half-melting die Since the cast molding material is used and the strength is improved as compared with the conventional FC 250, the thickness T of the wrap is thinner than the conventional fixed scroll 324 and the movable scroll 326.
- FIGS. 16 (a), (c) and (e) respectively show the partition wall area, the compression work area and the thrust area in the conventional fixed scroll 324.
- the partition area is the cross-sectional area of the wrap (here, wrap 285).
- the hatched portions in FIGS. 16 (b), (d) and (f) respectively show the partition area, the compression work area and the thrust area in the fixed scroll 24. Comparing FIG. 16 (a) with FIG. 16 (b), the partition wall area is smaller in the fixed scroll 24 as compared with the conventional fixed scroll 324. This is because the ratio (HZT) of the height H and thickness T of the wrap 24b is increased as the strength is increased. Further, referring to FIGS.
- the area force of the compression work area is also 40 square centimeters of the conventional fixed scroll 324 when compared with the effective compression area obtained by subtracting the partition area.
- fixed scroll 24 is about 20% larger! /, 48 square centimeters.
- FIGS. 17 (a), (c) and (e) respectively show the partition wall area, the compression work area, and the thrust area in the conventional movable scroll 326.
- the partition area is the cross-sectional area of the wrap (here, wrap 287).
- the hatched portions in FIGS. 17 (b), (d) and (f) respectively show the partition area, the compression work area and the thrust area in the movable scroll 26. Comparing FIG. 17 (a) with FIG. 17 (b), the wall area of the movable scroll 26 is smaller than that of the conventional movable scroll 326. This is because the ratio (HZT) of the height H and the thickness T of the wrap 26b is increased as the strength is increased. Further, referring to FIGS.
- the area force of the compression work area is also 28 square centimeters of the conventional movable scroll 326 as compared with the effective compression area obtained by subtracting the partition area.
- the movable scroll 26 is about 15% larger and 32 square centimeters.
- the hatched portion in FIG. 18 (a) shows the suction volume formed by the conventional fixed scroll 324 and movable scroll 326 having wraps 285 and 287 with relatively large thickness T
- FIG. The hatched portion in b) is a relatively small (thin) wrap 24b, 26b of thickness T.
- the suction volume formed by the fixed scroll 24 and the movable scroll 26 is shown.
- a pin-shaped test piece 412a and a disc-shaped test piece 412b as shown in FIG. 19 are produced from a material produced by semi-melt die casting, and the heat treatment conditions of the material produced by semi-melt die casting Test pieces 412a and 412b of different hardness were produced by variously changing. Then, each test piece 41 2a, 412b is set in the pin Z disk test apparatus 401 as shown in FIG. 19 and stored in the container 410.
- R 410A refrigerant and ether oil (100 ° C.) The average sliding speed in a mixture solution with water 2.
- the pin-shaped test piece 412a set in the holder 413 under the conditions of OmZs and a constant surface load of 20 MPa.
- the data obtained from this experimental power is also summarized in the bar graph shown in FIG.
- the area to the left of the graph shows the relationship between the hardness and the amount of wear of test pieces manufactured by semi-melt die-casting (hereinafter referred to as semi-melt die-cast test pieces).
- FC250 test piece the hardness and the amount of wear of the test piece of the conventional material FC250 (hereinafter referred to as FC250 test piece) are shown.
- the test piece of this FC 250 has a hardness (HRB 101.0) that exhibits good "adaptability" in a conventional compressor.
- the base texture of the FC 250 test piece showing this hardness contains 95% or more of pearlite texture.
- the hardness of the semi-melt die cast test piece and the amount of wear thereof are approximately proportional to each other.
- each semi-melt die cast molding When comparing the piece and FC250 test piece, the semi-melt die cast test piece with HRB 103.7 hardness wears significantly less than the FC 250 test piece The semi-melt die cast test with HR B98. 0 hardness It can be seen that the piece wears almost the same amount as the FC250 test piece, and the semi-melt die cast test piece with HRB 87.4 hardness wears significantly more than the FC250 test piece.
- the semi-molten die cast test piece of HRB 98.0 has the same "familiarity" with the FC 250 test piece of HRB 100 or more.
- the phenomenon of wear depends not only on hardness but also on the base structure. That is, even if the hardness is equal, if the proportion of the pearlite structure in the base tissue is high, the molded article is inferior in "compliability".
- the hardness which can realize a good "conformability” is empirically a hardness having a wear amount of more than 5 m and less than 13 m. For this reason, in the case of a semi-melt die cast test piece, one having a hardness greater than HRB 90 and less than HRB 100 is excellent in “compliability”. This is also supported by the fit curve of the semi-melt die-cast molded article shown in FIG. As apparent from FIG. 21, the force which requires 100 hours to fully adapt to HRB 100 or more is almost completely familiar within a few hours with HRB 100 or less.
- a pin-shaped test piece 412a and a disc-shaped test piece 412b as shown in FIG. 19 are produced from a material produced by semi-melt die casting, and the heat treatment conditions of the material produced by semi-melt die casting Test pieces 412a and 412b of different hardness were produced by variously changing. Then, each test piece 41 2a, 412b is set in the pin Z disk test apparatus 401 as shown in FIG. 19 and stored in the container 410.
- R 410A refrigerant and ether oil (100 ° C.) Step load (surface pressure) is applied in 15.6 MPa steps under the condition of an average sliding velocity 2.
- FIG. 23 shows the relationship between the hardness and the tensile elongation of a molded product produced by the semi-melt die casting method.
- the tensile elongation was measured according to the test method shown in JIS Z2241.
- the shape of the test piece was the shape of the No. 4 or No. 5 test piece shown in JIS Z2201.
- the hardness and the elongation are in inverse proportion to each other.
- conventional molded products it can be seen that the semi-melt die cast molded product exhibits extremely high ductility as compared to the conventional molded product.
- the semi-melt die-cast molding ideally have a tensile elongation of greater than 8% and less than 14%. Therefore, the hardness of the semi-melted die-cast molded article is ideally larger than HRB90 and smaller than HRB100.
- FIG. 24 shows the relationship between the cutting depth and the cutting depth of the molded product produced by the semi-melt die casting method.
- this machinability test was conducted by a down-cut method using an end mill as a cutting blade, setting the rotational speed of the end mill to 6000 rpm, and the feed rate to 1800 mm Zmin-0.05 Z blade under dry conditions.
- the hardness of the semi-melt die cast molded product is HRB 98
- the hardness of the FC 250 molded product of the reference is HRB 101.
- FIG. 25 shows a comparison of the amount of blade wear of molded articles produced by the semi-melt die casting method.
- an end mill is used as a cutting blade, and under dry conditions, the rotational speed of the end mill is set to 8000 rpm, and the feed rate is set to 1920 mm / min-O.04Z blade. And went down-cut method.
- the data in FIG. 25 is the value when the blade is rotated to the cutting distance, which is described above the rod.
- the hardness of the semi-melt die cast molded article at this time was HRB 93 to 95 and HRB 98 to: LOO, and the hardness of the FC 250 molded article of the reference was HRB 101.
- the semi-melt die-cast molded product with hardness 93 to 95 cuts more than FC250 molded product.
- the wear amount of both tools is almost the same for both the outer peripheral blade and the bottom blade despite the fact that they are long. Therefore, the semi-solid die-cast molded product with hardness 93-95 has the machinability equal to or better than that of the FC250 molded product.
- the hardness of the semi-melt die cast part of hardness 93 to 95 is 98 ⁇ : LOO
- the cutting distance is longer than half-melt die-cast molded products, the amount of wear on the bottom blade is smaller. That is, the semi-solid die cast molded articles having hardness 93 to 95 are significantly superior in machinability to the semi-melt die cast molded articles having hardness 98 to LOO.
- the movable scroll 26 and the fixed scroll 24 are manufactured through a semi-melt die casting molding process and a heat treatment process. For this reason, it is possible to easily obtain a movable scroll or fixed scroll having higher tensile strength and higher hardness than the movable scroll or fixed scroll made of flake graphite pig iron manufactured by the conventional sand-type manufacturing method.
- the movable scroll base and the fixed scroll base are manufactured through the semi-melt die casting molding process and the heat treatment process, and their hardness is adjusted to be higher than HRB 90 and lower than HRB 100.
- the tensile strengths of the movable scroll base and the fixed scroll base substantially correspond to the range of 600 MPa to 900 MPa. Therefore, if the method of manufacturing the sliding parts of the compressor is adopted, the movable scroll 26 and the end plates 24a and 26a and the spiral portions 24b and 26b of the fixed scroll 24 can be thinned. Therefore, the scroll compressor 1 can be reduced in diameter, and in turn, the thrust loss can be reduced and the large capacity can be reduced.
- the movable scroll base and the fixed scroll base are repeatedly replaced several times.
- machining such movable scroll substrates or fixed scroll substrates having such high tensile strength there is no need to worry about processing distortion. Therefore, if this manufacturing method is adopted, the cost of replacement is reduced.
- the tensile strength of the sliding component is in proportion to its hardness. Therefore, with the sliding component according to the first embodiment, the tensile strength can be ensured only by measuring the hardness.
- the heat treatment is performed such that the hardness of the movable scroll base and the fixed scroll base is higher than HRB 90 and lower than HRB 100. For this reason, when the method of manufacturing sliding parts of this compressor is adopted, it is possible to develop sufficient durability during compressor operation, and "familiarization" may occur as soon as possible. Movable scrolls 26 and fixed scrolls 24 can be manufactured so that they do not burn during abnormal operation. When the hardness is in this range, the machinability of the movable scroll base and the fixed scroll base is improved and the movable scroll base and the fixed scroll base are scratched.
- the fixed scroll 24 is a semi-molten die cast metal material using the mold 70 having the convex portions 71 a and 72 a capable of forming the opening planned portion P near the center of the base 124 thin. It is manufactured by forming the discharge hole 41 in the thin opening planned portion P after being molded by molding.
- the projections 71a and 72a make it possible to form the planned opening portion P of the discharge hole 41 in the vicinity of the center of the end plate equivalent portion of the base 124 of the fixed scroll 24 to 4 mm or less. For this reason, the generation of scab CN in the base 124 of the fixed scroll 24 is suppressed.
- the fixed scroll 24 In addition, the small cage CN is only divided and present in the surrounding area other than near the center of the inside of the end plate 24a. As a result, even if the discharge hole 41 is formed in the opening planned portion P of the base 124, there is no possibility that the hollow CN of the inside of the base 124 is exposed to the outside, and a decrease in fatigue strength can be suppressed.
- the movable scroll 26 is a semi-molten die cast metal material using a mold 80 having a convex portion 8 la capable of forming a predetermined portion near the center of the base 126 to 4 mm or less. Manufactured by molding. For this reason, the generation of the scab CN in the base 126 of the movable scroll 26 is suppressed. Therefore, in the movable scroll 26, only small knuckle CNs are separated and present in the peripheral portion other than the vicinity of the center inside the end plate 26a.
- the high and low pressure dome type scroll compressor 1 employs components with very few defects. Therefore, the high and low pressure dome type compressor 1 can also compress high pressure refrigerant such as carbon dioxide.
- scrolls are made using ordinary pig iron such as FC 250 because there is a problem that ductile iron and high carbon steel, which are high strength materials, are difficult to use and their corrosion properties are poor. There are many things that are manufactured.
- the fixed scroll 124 and the movable scroll 126 have high strength by molding using a semi-melt die casting method.
- the compressor 1 achieves a significant capacity increase with almost no change in the outer diameter.
- FC250 Compared to FC250 and other conventional materials, it is produced by die-casting (here, semi-melt die-casting), in which the iron material in a semi-solid (semi-solidified) state is pressed into the mold to produce a glaze.
- Die-casting here, semi-melt die-casting
- the iron material in a semi-solid (semi-solidified) state is pressed into the mold to produce a glaze.
- Products have high strength without special heat treatment, but they also The tensile strength can be improved by heat treatment such as holding at a constant temperature or adjusting the cooling rate.
- the tensile strength rises to an unprecedented level, whether the fatigue damage will occur as before or not !, the lap height (H) and thickness (T) only from the viewpoint of vaginal strength.
- the ratio (HZT) which is the ratio to the ratio, is determined, other problems occur. That is, if the ratio (HZT) is made too large to ensure strength, even if there is no problem in terms of strength, the deformation of the wrap 24b. 26b becomes too large when cutting is performed. The machining time of the end mill etc. can not be increased and the machining time becomes long, or the deformation (deflection) of the wraps 24b and 26b becomes large during the operation of the compressor 1 and the performance declines. And contact with the other scroll may cause loud noise.
- scrolls 24 and 26 have spiral wraps 24b and 26b, if the strength is greatly increased by heat treatment, distortion may occur. In addition, if the hardness is too high, the processing speed at the time of cutting is reduced, which leads to an increase in cost.
- the compressor 1 takes into consideration the upper limit of the amount of deformation of the wraps 24b and 26b, which is necessary from the viewpoints of processing time, performance deterioration, noise, etc.
- the ratio of tensile strength to Young's modulus of scrolls 24 and 26 is determined. Specifically, as described above, the degree of increase in strength due to heat treatment is suppressed so that the ratio of tensile strength to Young's modulus becomes equal to or less than 0.00.
- the balance with the Young's modulus is taken without increasing the strength excessively, so that the laps 24b and 26b are satisfied while the strength is satisfied. It is possible to suppress problems during operation such as performance degradation and noise increase due to the deflection of the shaft. Further, since the deflection of the wraps 24b, 26b at the time of cutting is also suppressed, the manufacturing cost can be reduced by shortening the processing time.
- the tensile strength of the scrolls 24 and 26 can be set to be 100 MPa or more.
- the degree of strength increase due to the heat treatment is suppressed.
- it takes time to heat treatment in order to suppress the strength low it is a fall at the end of the metal structure. Since the higher the ferrite ratio, the lower the wear resistance and the lower the wear resistance, the compressor 1 is heat-treated so that the ratio of the tensile strength to the Young's modulus is not less than 0.0003.
- crankshaft 17, the movable scroll 26, the fixed scroll 24, and the oldham ring 39 are manufactured through a semi-melt die casting process and a heat treatment process.
- the raw material cost, the machining cost and the tool consumables cost can be kept low, and the wastes such as grinding wastes and processing wastes can be reduced.
- crank shaft made of flake graphite pig iron manufactured by conventional sand-type manufacturing method, movable scroll, fixed scroll and crankshaft with higher hardness and hardness than fixed ring and oldham ring 17, movable scroll 24, fixed scroll 26 And Oldham Ring 39 can be easily obtained.
- the crankshaft base, the movable scroll base, the fixed scroll base and the Oldham ring base are manufactured through the semi-melt die casting molding process and the heat treatment process, and the hardness thereof is higher than HRB 90 and lower than HRB 100.
- the tensile strengths of the crankshaft base, the movable scroll base, the fixed scroll base and the oldham ring base substantially correspond to the range of 600 MPa to 900 MPa. Therefore, if the method of manufacturing sliding parts of this compressor is adopted, the movable scroll 26 and the end plates 24a and 26a of the fixed scroll 24 and the spiral portions 24b and 26b are thin-walled, and the Oldham ring 39 is thinned.
- crankshaft 17 can be reduced in diameter. Therefore, the scroll compressor 1 can be reduced in diameter, thereby reducing thrust loss and large capacity.
- the stress generated in the swirl is greater than that during normal operation (full throttle), but the strength is high.
- the possibility of damage to the spiral can be reduced.
- such a crankshaft 17 or The dynamic scroll 26, fixed scroll 24, and Oldham ring 39 are superior in toughness compared to FC materials, so damage to sudden internal pressure rise and foreign matter intrusion is unlikely to occur. Even if it is damaged, it may be damaged. ⁇ It becomes unnecessary to clean the piping.
- crankshaft base such as flake graphite pig iron manufactured by a sand-type manufacturing method
- a movable scroll base, a fixed scroll base, and an Oldham ring base are machined to obtain a final crankshaft 17 or
- the crankshaft base, movable scroll base, fixed scroll base and oldham ring base are gripped several times to remove distortion caused by processing. It is substituted.
- this manufacturing method is adopted, the cost for replacement can be reduced.
- the tensile strength of the sliding component is in proportion to its hardness. Therefore, with the sliding component according to the first embodiment, the tensile strength can be ensured only by measuring the hardness.
- the heat treatment is performed such that the hardness of the crankshaft base, the movable scroll base, the fixed scroll base, and the oldham ring base is higher than HRB 90 and lower than HRB 100. For this reason, when the method of manufacturing sliding parts of this compressor is adopted, sufficient durability can be exhibited during compressor operation, and "adaptation" may occur as soon as possible.
- the crankshaft 17, the movable scroll 26, the fixed scroll 24 and the Oldham ring 39 can be manufactured so that seizing does not occur during abnormal operation.
- a partial heat treatment is performed on the stress concentrated portion (the peripheral portion SC1 of the base of the wrap 24b and the innermost SC2 of the wrap 24b) of the fixed scroll 24. For this reason, in the fixed scroll 24, it is possible to impart a sufficient fatigue strength to the stress concentrated portion while maintaining a good compatibility with the sliding portion requiring the slidability.
- the stress concentrated portion of the movable scroll 26 (the peripheral portion SC3 of the base of the wrap 26b, the notch SC5 formed near the design center of the end plate 26a, the root of the bearing 26c Partial heat treatment is applied to peripheral SC4 and innermost SC6) of wrap 26b.
- the movable scroll 26 it is possible to impart sufficient fatigue strength to the stress concentration portion while maintaining good conformability to the sliding portion requiring the slidability.
- the eccentric shaft portion 17a and the main shaft portion 17b of the crankshaft 17 are subjected to high frequency heat treatment. Therefore, sufficient wear resistance can be imparted to the eccentric shaft 17a and the main shaft 17b. Therefore, the life of the crankshaft 17 can be extended.
- the laser heating process is performed on the peripheral portion SC7 of the notch portion existing between the eccentric shaft portion 17a and the main shaft portion 17b of the crankshaft 17. Therefore, sufficient fatigue strength can be given to the stress concentrated portion of the crank axis 17.
- the norrance weight portion 17 c is a crankshaft 1. It is molded integrally with 7. For this reason, it is not necessary to provide a separate ring as a lance weight. Therefore, the material cost for the balance weight can be reduced. Also, conventionally, in the manufacture of balance weights, after processing the balance light into a large shape and then processing such as processing and adjusting the balance, it is necessary to use the crankshaft 17 according to the present invention. Since it is manufactured by the semi-solid die-casting method, it can be formed to a shape very close to the final shape, and the number of steps of manufacturing the compressor can be reduced. Therefore, the crankshaft 17 of this compressor can reduce the manufacturing cost of the compressor.
- the movable scroll side key parts 39a, 39b and the know side key parts 39c, 39d of the Oldham ring 39 are subjected to high frequency heat treatment.
- sufficient body wear can be imparted to the movable scroll side key portions 39a, 39b and the housing side key portions 39c, 39d. Therefore, the service life of Oldham Ring 39 can be extended.
- the high- and low-pressure dome-type scroll compressor 1 of a closed type is adopted, but the compressor may be a high-pressure dome-type compressor or a low-pressure dome-type compressor. Also, it may be a semi-hermetic compressor or an open compressor.
- the force compression mechanism in which the scroll compression mechanism 15 is adopted may be a rotary compression mechanism, a reciprocating compression mechanism, a screw compression mechanism, or the like.
- the scroll compression mechanism 15 may be a scroll of a double rotation type.
- the Oldham ring 39 is adopted as a rotation preventing mechanism, but any mechanism such as a pin, a ball coupling, a crank or the like may be adopted as a rotation preventing mechanism.
- the scroll compressor 1 in the case where the scroll compressor 1 is used in a refrigerant circuit, for example, a compressor or a fan used in a single unit or incorporated in a system can be used for a power application. , A supercharger, a pump or the like.
- Lubricating oil was present in the scroll compressor 1 according to the first embodiment, but it may be oil-less or oil-free (with or without oil) type compressors, blowers, superchargers and pumps. It may be.
- the high and low pressure dome type scroll compressor 1 according to the first embodiment is an outer drive type scroll compressor.
- the scroll compressor according to the present invention may be an inner drive type scroll compressor.
- the inner drive pin shaft portion of the movable scroll is selectively heated by a prescription such as high frequency heating to make its surface hardness higher than HRC 50 and lower than HRC 65. Yo! In this way, the wear resistance of the inner drive pin shaft portion can be greatly improved.
- the sliding component base is subjected to the final finishing process as the final sliding component, the semi-solid die-casting process and the near-finished product are almost completed. If possible, the finishing step may be omitted.
- the sliding component according to the first embodiment is manufactured through a semi-solid die casting process, a heat treatment process, a finishing process and a partial heat treatment process, but such a sliding component is a mold forming process, a heat treatment process, It may be manufactured through a finishing process and a partial heat treatment process.
- the raw materials are the same.
- the raw material made liquid by applying a high temperature to the mold space 303 constituted by the fixed mold 302 and the movable mold 301 is obtained. It is washed away. Then, after this, the liquid raw material in the bowl-shaped space 303 is rapidly cooled through the fixed mold 302 and the movable mold 301. Then, the liquid raw material in the bowl-shaped space 303 is solidified to form a solid molding 310. At this time, the molding 310 is thermally shrunk. Therefore, the molded product 310 can be easily released.
- the molded product 310 obtained by cutting is referred to as a preform 301a).
- the preform 301a is heat treated, and its hardness is adjusted to be higher than HRB 90 and lower than HRB 100.
- the target hardness may be in the range of HRB90 to HRB95.
- the preform 30 la which has undergone the heat treatment step is precision machined to form a final product 310 b.
- the heat treatment step and the final finishing step are performed in the same manner as the heat treatment step and the final finishing step according to the first embodiment.
- the end plate 24a in forming the base body 124 of the fixed scroll 24, as shown in FIGS. 9 and 10, is recessed from the upper and lower sides by the opposing convex portions 71a and the convex portions 72a to reduce the thickness of the end plate 24a. It is molded to reduce the thickness.
- the present invention is not limited to this.
- the mirror equivalent portion is recessed only from the upper surface side, or as shown in FIG. 28, the mirror equivalent portion is recessed only in the lower surface side.
- the wall thickness of the mirror plate equivalent portion must be a specified thickness t2 (for example, 4 mm or less). In these cases where molding is performed so as to make them thin, as in the first embodiment, the generation of CN's CN is suppressed.
- the distance between the convex portion 81a forming the inner space 26f of the bearing portion 26c and the second mold portion 82 By setting the distance d to a predetermined interval (for example, 4 mm or less), the thickness tl at the central portion of the end plate equivalent portion is formed to a predetermined thickness (for example, 4 mm or less).
- a predetermined interval for example, 4 mm or less
- the present invention is not limited to this.
- the mold for manufacturing the base 126 of the movable scroll 26 as well as the mold 70 for manufacturing the base 124 of the fixed scroll 24.
- the first mold portion 81 and the second mold portion 82 of the 80 are provided with convex portions facing each other, and semi-molten die cast molding is performed using a mold 80 having such convex portions facing each other.
- the base 126 of the movable scroll 26 having a thin portion R to be opened near the center of the mirror plate as shown in FIG. 30 or 31 is molded. Also in this case, the generation of the scabies CN is suppressed, and there is no risk that the scaly CN inside the base 126 will be exposed to the outside even if the discharge holes are formed in the opening planned portion R by the drill key.
- the height of the bottom of the inner space 26f of the bearing portion 26c is made to be recessed from the upper side of the mirror equivalent portion and also below the mirror equivalent portion.
- the opening scheduled portion R is made thinner.
- the occurrence of CN is suppressed.
- the height of the bottom of the inner space 26f is set to the same level as that of the existing movable scroll, and the dent from the upper side of the portion equivalent to the mirror plate is large. By doing this, the portion R to be opened is made thinner. As a result, the occurrence of scabies C N is suppressed.
- the notch SC5 is formed by an end mill or the like, but a notch is formed on the upper surface of the center portion of the mirror plate 26a of the movable scroll 26 shown in FIGS. Bored portion SC5 may be formed in advance in a semi-melt die casting process.
- the notch portion (counterbore portion) SC5 and the internal space 26f of the bearing portion 26c are simultaneously formed, which further reduces the thickness of the central portion of the head plate equivalent portion. Occurrence of CN is further suppressed.
- the notch portion (counterbore portion) SC5 by cutting with an end mill or the like as in the method of manufacturing the movable scroll 26 according to the first embodiment. As well as reducing the number of man-hours, no cutting waste is generated.
- an iron material is used as the raw material of the sliding part, but metal materials other than iron may not be used unless they impair the purpose of the present invention.
- a fixed scroll 24 and a movable scroll 26 employing wraps 24b and 26b thinner than the conventional fixed scroll 324 and movable scroll 326 are used. Therefore, it is also possible to thin only the wrap of one of the scrolls, which increases the suction volume by about 1.5 times.
- the suction volume is increased by about 1.25 times compared to the conventional one. It will be.
- a high and low pressure dome type scroll compressor will be described as an example of a compressor using a sliding component according to the second embodiment.
- the water drive type movable scroll 26 of the high and low pressure dome type scroll compressor 1 according to the first embodiment is placed on the inner drive type movable scroll. It has been replaced. Therefore, hereinafter, only the movable scroll will be described.
- movable scrollable 96 mainly includes mirror 96a and mirror 96a of mirror 96a. It comprises a wrap (involute) wrap 96b extending upward from 6P, a bearing 96c extending downward from the lower surface of the end plate 96a, and grooves 96d formed at both ends of the end plate 96a.
- Movable scroll 96 is an inner drive type movable scroll. That is, the movable scroll 96 has a bearing portion 96 c fitted inside the recess formed at the tip of the crankshaft 17.
- the thickness t3 of the central portion of the end plate 96a is thinner than the thickness of the other portion (for example, the portion near the periphery of the end plate 96a). That is, the inside of the bearing portion 96c is formed with a dented recess 96f that has been punched out during semi-solid die casting. Therefore, in the base 196, the occurrence of the diamond CN (see FIG. 34) in the portion equivalent to the end plate is suppressed. In the base 196, the thickness t3 of the central portion of the bearing equivalent portion is set to 4 mm or less.
- the thickness of the bearing portion 96c is such that the thickness t4 becomes very thick if there is no ridge removal recess 96f, and the presence of a force removal recess 96f which makes it easy to generate a void CN within the bearing portion 96c.
- the thickness t5 of the part 96c is thin. Therefore, the generation of the cages CN in the inside of the bearing portion 96c is suppressed, and the strength reduction of the bearing portion 96c is suppressed.
- the thickness t5 of the bearing portion 96c is set to 4 mm or less.
- a mold 90 for semi-melt die-casting the base 196 of the movable scroll 96 comprises a first mold portion 91 and a second mold portion 92.
- the shape of the space 93 formed when the first mold portion 91 and the second mold portion 92 are combined corresponds to the outer shape of the base 196 of the movable scroll 96 to be formed.
- a convex portion 91a is formed which forms the dented recess 96f of the bearing portion 96c of the movable scroll 96. Since the distance between the convex portion 91a and the second type portion 92 is set to 4 mm or less, the thickness t3 of the central portion 96e of the end plate 96a is reduced to 4 mm or less.
- the substrate 196 of the scroll 96 can be manufactured.
- the ridged recess 96 f is formed in at least a part of the inside of the bearing 96 c using the convex portion 91 a of the mold 90.
- the central portion of the end plate equivalent portion of the base 196 of the movable scroll 96 is formed to be 4 mm or less.
- the weight of the movable scroll 96 can be greatly reduced, and the weight of the movable scroll 96 can be reduced.
- the force equivalent to the bearing equivalent mm or less is formed.
- the generation of the hollow CN in the inside of the bearing portion 96c is suppressed, and the strength reduction of the bearing portion 96c is suppressed.
- a high and low pressure dome type scroll compressor will be described as an example of a compressor using a sliding component according to the third embodiment.
- the difference between the high and low pressure dome type scroll compressor according to the third embodiment and the high and low pressure dome type scroll compressor 1 according to the first embodiment is only the wrap shape of the fixed scroll and the movable scroll. Therefore, only the fixed scroll and the movable scroll will be described below.
- the base 626 of the movable scroll 526 according to the third embodiment is formed by, for example, semi-molten die casting using a mold 180 shown in FIG.
- a mold 180 for semi-melt die-casting the base 626 of the movable scroll 526 comprises a first mold portion 181 and a second mold portion 182.
- the shape of the space portion 183 formed when the first mold portion 1 81 and the second mold portion 182 are combined is formed It corresponds to the external shape of the base 626 of the movable scroll 526.
- the mold 180 is provided with a wrap molding portion 182a.
- the wrap forming portion 182a has an outer shape set such that the draft angle of the winding start portion QO close to the center of the wrap equivalent portion of the base 626 of the movable scroll 526 is larger than the draft angle of the outer winding end portion Q4. (See the drafts of the movable scroll 26 in Fig. 36: 0 1, ⁇ 2).
- the side 182 b and the side 182 c of the wrap-formed portion 182 a have a portion Q 1 which is the portion Q 1 between the portion Q 1 and the portion Q 3 of the wrap equivalent portion. Since it is closer to the center than 3, the draft angle 0 1 of the part Q 1 is set to be larger than the draft angle 0 3 of the outer part Q 3, and so on.
- the base 626 becomes a movable scroll 526 through a finishing process.
- the wrap shape of the movable scroll 526 will be described in detail.
- the spiral shape of the wrap 526b is larger in draft angle at the winding start portion Q10 closer to the center than at the outer winding end portion Q14. It is set so that the draft gradually and gradually changes from the beginning of winding to the end of winding.
- the winding start portion Q 10 of the wrap 526 b is set to the maximum draft (for example, 2 degrees), and the draft angle in the middle portion (Q ll to Q 13) changes the winding angle ex. Is set to be continuously smaller, and the draft of the winding end portion 14 is set to the minimum (for example, 0.5 degrees). That is, as shown in the graph of FIG.
- the relationship between the wrap angle a of the wrap and the draft angle ⁇ is that the draft angle 2 is 2 degrees of the maximum value when the wrap angle a is the winding start angle, and The draft ⁇ decreases in proportion to the increase of the angle a, and when the winding angle a is the end of winding, the minimum value is 0.5 degree.
- the fixed scroll 524 is also manufactured in the same manner as the movable scroll 526.
- the wrap shape of the movable scroll after the finishing process will be described in detail.
- the spiral shape of the wrap 524b is such that the draft at the beginning of winding portion PO closer to the center is higher than the draft of the portion P4 at the end of outer winding end. It is large, and the draft is set to change continuously and gradually from the beginning to the end of winding.
- the wrap 524b starts winding
- the partial PO of the is set to the maximum draft (for example, 2 degrees), and the draft in the middle part (P1 to P3) is set to be continuously smaller as the winding angle ⁇ changes,
- the draft angle of the end of winding ⁇ 4 is set to the minimum (eg, 0.5 degrees).
- the relationship between the wrap angle a of the wrap and the draft angle ⁇ is as shown in the graph of FIG. 39, and the draft angle distribution ⁇ is a maximum value of 2 degrees when the wrap angle a is the winding start angle.
- the draft angle ⁇ decreases in proportion to the increase of the winding angle a, and when the winding angle a is the winding end angle, the minimum value is 0.5 degrees.
- the wrap shape is determined according to the strength and the quality. And waste of material can be eliminated.
- the base 626 of the movable scroll 526 in the third embodiment has a draft angle in the winding start portion QO close to the center of the spiral shape force equivalent portion of the wrap equivalent portion larger than that of the outer winding end portion Q4. Also, the force is set so that the draft gradually and gradually changes from the start of winding to the end of winding in the lap equivalent portion. Therefore, when the base 626 of the fixed scroll 524 is formed by semi-melt die casting, the stress on the mold near the center of the spiral during mold release is reduced. As a result, it is possible to suppress specified cracks and to prolong the life of the mold. Therefore, the cost for the mold can be reduced, and the manufacturing cost of the fixed scroll 24 and the movable scroll 26 can be reduced accordingly.
- the draft angle at the beginning of winding portion QO close to the center of the lap equivalent portion of the base 626 of the movable scroll 526 is larger than the draft angle of the portion Q4 at the outer winding end. For this reason, even if the draft angle at the central portion of the lap equivalent portion is increased, it is possible to reduce the adverse effect on -net meshing (that is, shaping close to the final shape) in the entire wrap. That is, if the draft angle is increased for the entire portion corresponding to the wrap, the stress exerted on the mold in the entire portion corresponding to the wrap at the time of mold release is reduced, while the negative effect on the formation of the open net increases.
- the draft near the center of the wrap equivalent portion greater than the draft of the outer end portion of the wrap, the negative effect on the mesh meshing is reduced.
- the shape of the lap equivalent portion is set so that the draft gradually and continuously changes gradually from the winding start to the winding end. It is not limited to this.
- the change in draft ⁇ ⁇ ⁇ ⁇ with respect to the wrap angle OC of the wrap equivalent portion is set so that the degree of decrease in draft ⁇ becomes large in the range near the beginning of winding, and the range near the end of winding
- the degree of decrease in draft ⁇ may be set small (note that the maximum value of draft ⁇ is 2 degrees, the minimum is 0.5 degrees).
- the base 626 of the movable scroll 526 is formed by semi-fusion die casting, the stress applied to the mold in the vicinity of the center of the spiral during mold release is reduced, and the life of the mold is extended.
- the graph of FIG. 39 (draft ⁇ is linear in proportion to increase in wrap angle ⁇ . In the area other than the winding start and the winding end, the draft ⁇ is set smaller than in the case of the change (in which the It is possible to make it smaller.
- the shape of the lap equivalent portion is set so that the draft gradually and continuously changes gradually from the winding start to the winding end. It is not limited to this. As shown in the graph of FIG. 43, the change in draft D with respect to the wrap angle OC of the wrap equivalent portion may be set so as to gradually decrease the draft D from the winding start to the winding end ( The maximum value of draft ⁇ is 2 degrees, and the minimum value is 0.5 degrees).
- the maximum value of draft ⁇ is 2 degrees, and the minimum value is 0.5 degrees.
- the shape of the lap equivalent portion is set so that the draft gradually and continuously changes gradually from the winding start to the winding end. It is not limited to this. As shown in the graph in FIG. 44, the change in draft ⁇ ⁇ ⁇ ⁇ with respect to the wrap angle OC of the wrap equivalent portion is set to the maximum value (2 degrees) of draft ⁇ in the range of the predetermined turning angle ex near the winding start. And the draft angle ⁇ at other angle ranges is set to the minimum value (0.5 degrees).
- the surface of the scroll may be coated with a resin.
- a resin for example, as shown in FIG. 45, if the entire surface of the movable scroll 536 is coated with a resin RS, the leakage of the gas refrigerant compressed by the compressor can be reduced and the noise can be reduced. If at least the wrap 536b of the movable scroll 536 is coated with resin RS, it is possible to reduce the leakage of gas refrigerant and reduce the noise.
- the scroll is coated with resin, it is possible to improve the strength of the scroll inside the resin coating only at the necessary site by increasing the draft of the winding start portion near the center of the wrap 536b. Become.
- the movable scroll 536 can be corroded with a predetermined outer shape with high accuracy.
- the fixed scroll may also be coated with a resin RS. Also in this case, at least the wrap of fixed scroll is coated with resin RS If this is done, it is possible to reduce leakage and noise of the gas refrigerant.
- the force of manufacturing the scroll of the compressor by a semi-solid forming method such as semi-melt die casting or the like.
- the present invention is not limited to this. If it is a scroll of a molded compressor, it is possible to extend the life of the mold. For example, even in the case of a scroll fabricated by injecting a high temperature hot water of metal material into a mold, the draft at the beginning of the roll near the center of the scroll wrap is the draft at the end of the outer wrap end. By making the size larger, it is possible to extend the life of the mold.
- the draft angle at the winding start portion QO close to the center of the lap equivalent portion is larger than the drafting gradient of the outer winding end portion Q4.
- the invention is not limited to this, and the outside draft may be increased.
- the draft at the end of the outer winding end portion P23, Q24 of the lap equivalent portion is closer to the center of the winding It may be larger than the draft of parts P21 and Q21.
- the lap equivalent portion has a gradual change in the extraction gradient from the winding start to the winding end continuously (ie, the partial force of the winding start near the center, the outer end) It is set to continuously increase the size of the part) In this case, it is possible to eliminate waste of material more effectively.
- the lap equivalent gradually changes in draft from the winding start to the winding end (that is, the partial force of the winding close to the center is also the end of the outer winding It may be set so that In this case, it is possible to more effectively eliminate waste of material.
- the wrap equivalent portion is in a predetermined angular range between the winding start and the winding end (ie, a predetermined range near the winding end portion).
- the draft may be set to be larger than the draft in other angular ranges. In this case, it is possible to more effectively eliminate waste of material.
- At least a portion corresponding to the wrap may be coated with a resin. In this case, it is possible to reduce leakage and noise of the gas refrigerant.
- a high and low pressure dome type scroll compressor will be described as an example of a compressor using a sliding component according to the fourth embodiment.
- the difference between the high and low pressure dome type scroll compressor according to the fourth embodiment and the high and low pressure dome type scroll compressor 1 according to the first embodiment is only the wrap shape of the fixed scroll and the movable scroll. Therefore, only the fixed scroll and the movable scroll will be described below.
- the movable scroll base 726 according to the fourth embodiment is formed by, for example, semi-molten die casting using a mold 280 shown in FIG.
- a mold 280 for semi-melt die-casting the movable scroll base 726 comprises a first mold portion 281 and a second mold portion 282.
- the shape of the space formed when the first mold portion 281 and the second mold portion 282 are combined corresponds to the outer shape of the movable scroll base 726 to be formed.
- the outer shape of the second die portion 282 of the mold 280 is set to secure the draft when the movable scroll base 726 is separated from the mold 280.
- the shape of the lap equivalent portion of the second-type portion 282 is determined such that the entire surface of the lap equivalent portion 87 is inclined at a first angle ⁇ ⁇ ⁇ ⁇ with respect to the line orthogonal to the mirror equivalent portion 86a. ing.
- the movable scroll The lap equivalent portion 87 of the intermediate 726 has a thickness force t + tl + tl at the boundary with the mirror equivalent portion 86a with respect to the thickness t of the tip.
- the fixed scroll base 724 is also manufactured in the same manner as the movable scroll base 726.
- the fixed scroll base 724 and the movable scroll base 726 which are formed by the semi-molten die cast forming method become the final fixed scroll 734 and the movable scroll 736 incorporated into the compressor by further cutting.
- the fixed scroll 734 shown in FIG. 49 is manufactured by subjecting the fixed scroll base 724 shown in FIGS. 50 and 51 to mechanical force. Of the machining processes including the drilling holes of the discharge holes 741, here, the cutting process for forming the wrap 85 into the wrap 185 will be described.
- the wrap 85 is a face which can be close to the wrap 187 of the movable scroll 736 which is the rival, and can be the end of the compression chamber 740 OS 85a, IS 85b, OS 85b, and the movable scroll 736 which is the rival IJ divided into the inner surface of the inner periphery J of the winding start near portion 85a (in the lap 85 ', which is close to the lap 85) and not close to the wrap 187 and cut the former surface OS85a, IS85b, OS85b While processing, the latter surface IS85a is not cut.
- the surfaces OS85a, IS85b, and OS85b are the surface OS85a on the outer circumference side of the winding start near portion 85a and the surface IS85b on the inner circumference side of the portion 85b closer to the end of winding than the winding start near portion 85a and the surface OS85b of the circumference is there.
- Faces OS85a, IS85b, OS85b [Corner, end, minole] This cutting process is applied, and the slope shown in Figure 50 and Figure 51 is eliminated, and the faces shown in Figure 49 and 52 are faces S185a, IS 185b, It becomes OS 185b.
- FIG. 52 the surface indicated by!
- the point, and the line OS85a, IS85b, and OS85b, and the surface indicated by a solid line is finished to be OS185a, IS185b, and OS185b.
- the inclination angle with respect to a line orthogonal to the mirror surface 184a of these surfaces OS185a, IS185b, and OS185b is 0 degree.
- the surface IS 85 a on the inner peripheral side of the winding start vicinity portion 85 a of the wrap 85 is left as it is as the surface on the inner peripheral side of the winding start vicinity portion 185 a also in the final wrap 185.
- An enlarged view of the winding start vicinity portion 185a in FIG. 52 is shown in FIG.
- the winding start near portion 185a of the wrap 185 has the outer surface OS 185a perpendicular to the mirror surface 184a, while the inner surface IS85a has a first angle with respect to the line orthogonal to the mirror surface 184a. It is inclined.
- the winding start vicinity portion 85a of the wrap 185 The thickness ta at the boundary with the mirror surface 184a is larger than that of the other portion 85b.
- the portion 85b other than the winding start vicinity portion 85a of the wrap 185 is cut so as to have the same thickness from the boundary with the mirror surface 184a to the tip, and the thickness is the winding start vicinity portion 85a shown in FIG.
- the thickness of the tip of t is the same as t.
- the movable scroll 736 shown in FIG. 54 is manufactured by machining the movable scroll base 726 shown in FIG. Among the machining processes, the cutting process for forming the lap 87 into the lap 187 will be described here.
- the wrap 87 is a face which can be close to the end of the compression chamber 740 with the wrap 185 of the fixed scroll 734 which is the other party to be engaged OS87a, IS87b, OS87b and the fixed scroll 734 which is the other party to be mixed up
- the inner edge of the winding J is divided into the surface of the winding J near the beginning of the winding portion 87a (in the lap 87 ', close to the winding start) which does not closely contact with the wrap 185 and IJ, and cutting the former surface OS87a, IS87b, OS87b While machining, the latter surface IS87a is not cut.
- the surfaces OS87a, IS87b, and OS87b are the surface OS87a on the outer peripheral side of the winding start near portion 87a, and the surface IS87b on the inner peripheral side of the portion 87b closer to the end of winding than the winding start near portion 87a and the surface OS87b of the outer circumference is there.
- Surfaces OS87a, IS87b, OS87b [Correction, end, minole [Cut cutting process is applied, and the inclination shown in Fig. 48 is eliminated, resulting in the surfaces OS187a, IS 187b, OS 187b shown in Fig. 54.
- the surfaces OS87a, IS87b, and OS87b indicated by dotted lines in FIG.
- the inclination angle with respect to a line orthogonal to the mirror surface 186a of these surfaces OS187a, IS187b, and OS187b is 0 degree.
- the surface IS87a on the inner peripheral side of the winding start vicinity portion 87a of the wrap 87 is left as it is as the surface on the inner peripheral side of the winding start vicinity portion 187a even in the final wrap 187.
- the winding start near portion 187a of the wrap 18 7 has the outer surface OS 187a orthogonal to the mirror surface 186a, while the inner surface IS87a has a first angle ⁇ with respect to a line orthogonal to the mirror 186a.
- the winding start vicinity portion 87a of the wrap 187 has a larger thickness ta at the boundary with the mirror surface 186a than the other portion 87b of the wrap 187.
- the portion 87b other than the winding start vicinity portion 87a of the wrap 187 is cut so as to have the same thickness from the boundary with the mirror surface 186a to the tip, and the thickness is, as shown in FIG. The thickness is smaller than t.
- FIGS. 55 to 57 show how the gas refrigerant is compressed as the volume of the compression chamber 740 changes.
- FIGS. 55 to 57 are cross-sectional views of a portion where the wrap 185 of the fixed scroll 734 and the wrap 187 of the movable scroll are in cross section, and the movable scroll 736 turns with respect to the fixed scroll 734. By doing this, the state changes in the order of FIG. 55 (a), FIG. 55 (b), FIG. 56 (a), FIG. 56 (b), FIG. 57 (a) and FIG. 57 (b).
- the surfaces on the inner peripheral side of the winding start vicinity portions 185a, 187a of the wraps 185, 187 IS85a, IS87a faces shown by thick lines in the figure; see FIG. 58). It does not constitute the end of the compression chamber 740 that can not touch the other's lap, and does not contribute to the compression work. Therefore, the sloped force of the first angle ⁇ The surface accuracy of these surfaces IS85a, IS87a does not affect the degree of sealing of the compression chamber 740! /.
- scrolls are made using ordinary pig iron such as FC 250 because there is a problem that ductile iron and high carbon steel, which are high strength materials, are difficult to use and their corrosion properties are poor. There are many things that are manufactured.
- the fixed scroll base 724 and the movable scroll base 726 are formed by using a semi-melt die casting method, thereby achieving high strength 'Takaoka IJ property.
- the final fixed scroll 734 and the movable scroll 736 are formed into an ant shape.
- the stiffness (Young's modulus) is constant and can not be adjusted. If so, the amount of deformation (warp) of the wraps 185 and 187 may increase during operation, which may cause noise and wear. If the gap between the two wraps 185 and 187 is set large to allow a large amount of deformation in order to avoid this noise and wear, the degree of sealing of the compression chamber is reduced and the compression performance is degraded.
- the thickness of the root portion of the mirror plate 184, 186 on the side of the mirror plate 184, 186 is reduced rather than merely thinning the wrap 185, 187, thereby making the entire wrap 185, 187 rigid. If it is possible to increase the thickness of the root part, the volume of the compression chamber will be reduced. In addition, leaving a slope on the side of the lap 185, 187, which requires high accuracy, makes quality control (control of the quality of the surface) difficult, which may result in poor performance.
- the surfaces IS85a, IS87a on the inner peripheral side of the winding start near portions 185a, 187a of the wraps 185, 187 where the pressure received from the refrigerant gas compressed near the center becomes large. While the first angle ⁇ is inclined to greatly increase strength and suppress deformation, the slopes of portions 185b and 187b of the wraps 185 and 187 away from the center are eliminated to prevent the capacity from decreasing. ing.
- OS 185a and OS 187a on the outer circumference side of the winding start portion 185a and 187a of wraps 185 and 187 are surfaces that perform compression work in contact with the other scroll, and if a large inclination is given, management of surface accuracy The slope is eliminated because there is a risk that refrigerant gas leakage may increase at the contact area of the scrolls 734 and 736.
- the first angle ⁇ of the inner surface of the wrap 185, 187 near the winding start portion 185a, 187a IS 85a, IS 87a
- the surface IS85a, IS 87a is in contact with the other's scroll and the compression chamber 740 There is no disadvantage because it does not affect the degree of sealing.
- the pressure is relatively low for the portions 185 b and 187 b other than the winding start vicinity portions 185 a and 187 a of the wraps 185 and 187, the strength and the amount of deformation are greater.
- the inclination angle is set to zero, and the surfaces on the inner peripheral side of the wrap 185, 187 near part 185a, 187a on the inner peripheral side IS85a, IS87a have relatively high pressure, so the strength increases or deformation
- the angle of inclination is set with an emphasis on volume control (1st angle)), the surface on the outer circumference side of the wrap start near part 185a, 187a of the wraps 185, 187 OS 185a, OS 187a, surface accuracy management and compression chamber 740
- the first angle ⁇ is inclined to the winding start near portions 185a and 187a of the wraps 185 and 187 having high pressure.
- the inclination angle is all zero, management of the face accuracy of these faces becomes easy, and during operation of the compressor. It is possible to reduce the problem that the gas refrigerant leaks to the outer compression chamber 740 from the portion where the wraps 185 and 187 of the scrolls 124 and 126 overlap.
- the surfaces on the inner peripheral side of the winding start vicinity portions 185a and 187a of the wraps 185 and 187 are surfaces in which the IS85a and IS87a are not in contact with the mating wraps 187 and 185 with each other.
- cutting on these surfaces IS85a and IS87a is omitted. As a result, costs can be reduced and the time required for cutting can be shortened.
- the draft at the time of removing the mold is present in the base members 724 and 726 of the scrolls 734 and 736 before cutting, and the draft thereof is the same as that of the wrap 185 and 187.
- the winding start near portions 185a and 187a of the wraps 185 and 187 are surfaces orthogonal to the outer surface OS 185a and the OS 187a force mirror surfaces 184a and 186a. On the other hand, it is inclined at a first angle ⁇ ⁇ ⁇ ⁇ with respect to a line perpendicular to the inner surface IS85a, IS87a force mirror 184a, 186a. As a result, the winding start vicinity portion 85a, 87a of the wrap 185, 187 has a larger thickness ta at the boundary with the mirror surface 184a, 186a than the other portions 85b, 87b of the wrap 185, 187.
- the scrolls 734 and 736 can withstand the stress increase due to the high differential pressure even when the high pressure refrigerant such as carbon dioxide is compressed. Also, this effect makes it possible to increase the height of the teeth of the scrolls 734 and 736. That is, the capacity of the compression chamber 740 can be increased while reducing the diameter of the wraps 185 and 187. Then, when the compressor can be reduced in diameter in this manner, the body casing portion 11 is reduced in diameter.
- the small diameter meshed monthly casing portion 11 can exhibit the same pressure resistance and a thinner wall thickness as compared with the conventional body casing. For this reason, the raw material cost etc. of the fuselage casing part 11 can be reduced. In addition, scrolls 734 and 736 wraps 185 and 187 can be reduced in diameter. For this reason, it is possible to increase the sliding area of the thrust portion where the sliding is severe.
- the scrolls 734 and 736 are manufactured by a semi-melt forming method. Because of this, the scrolls 734, 736 have less surface roughness than those obtained by the conventional tumbling method. For this reason, in this compressor, even when high-pressure refrigerant such as carbon dioxide is compressed, cracks from the surfaces of the scrolls 734 and 736 are unlikely to occur.
- the present invention is not limited to this, which produces the substrates 724, 726 of the scrolls 734, 736 of the compressor by the semi-melt forming method such as the semi-melt die casting method.
- the semi-melt forming method such as the semi-melt die casting method.
- the swing compressor 801 is a two-cylinder type swing compressor and mainly includes a cylindrical closed dome-shaped casing 810 and a swing compression mechanism 815. , A drive motor 816, a suction pipe 819, a discharge pipe 820 and a muffler 860. In the swing compressor 801, an casing (gas-liquid separator) 895 is attached to a casing 810.
- a casing gas-liquid separator
- the casing 810 has a substantially cylindrical body casing portion 811, a bowl-shaped upper wall portion 812 which is airtightly welded to the upper end portion of the body casing portion 811, and a lower end portion of the body casing portion 811 airtight. And a bottom wall 813 having a bowl shape to be welded.
- the casing 810 mainly houses a swing compression mechanism 815 for compressing a gas refrigerant and a drive motor 816 disposed above the swing compression mechanism 815.
- the swing compression mechanism 815 and the drive motor 816 are connected by a crankshaft 817 disposed to extend in the vertical direction in the casing 810.
- the swing compression mechanism 815 mainly includes a crankshaft 817, a piston 821, a bush 822, a front head 823, a first cylinder block 824, and a mid plate 825. , A second cylinder block 826, and a rear head 827.
- the front head 823, the first cylinder block 824, the middle plate 825, the second cylinder block 826 and the jack head 827 are integrally fastened by a plurality of Bonore plates 890.
- the swing compression mechanism 815 is immersed in the lubricating oil L stored at the bottom of the casing 810, and the lubricating oil L is differentially supplied to the swing compression mechanism 815. It is supposed to be. The components of the swing compression mechanism 815 will be described in detail below. /.
- the first cylinder block 824 is formed with a cylinder hole 824a, a suction hole 824b, a discharge passage 824c, a bush accommodation hole 824d and a blade accommodation hole 824e.
- the cylinder bore 824a is a cylindrical bore penetrating along the thickness direction as shown in FIGS.
- the suction hole 824 b also penetrates through the cylinder hole 824 a on the outer peripheral wall surface.
- the discharge passage 824c is formed by cutting out a part of the inner peripheral side of the cylindrical portion forming the cylinder hole 824a.
- the bush accommodating hole 824 d is a hole penetrating along the thickness direction, and is disposed between the suction hole 824 b and the discharge path 824 c when viewed along the thickness direction.
- the blade accommodation hole 824 e is a hole penetrating along the thickness direction and is in communication with the bush accommodation hole 824 d.
- the eccentric shaft portion 817a of the crankshaft 817 and the roller portion 821a of the piston 821 are accommodated in the cylinder hole 824a, and the blade portion 821b of the piston 821 and the bush are accommodated in the bush accommodation hole 824d.
- the discharge path 824c is fitted to the front head 823 and the middle plate 825 so that the discharge path 824c faces the front head 823 side. See Figure 61).
- a first cylinder chamber Rcl is formed in the swing compression mechanism 815, and the first cylinder chamber Rcl is divided into a suction chamber communicating with the suction hole 824b by the piston 821 and a discharge chamber communicating with the discharge passage 824c. It will be done.
- the second cylinder block 826 is formed with a cylinder hole 826a, a suction hole 826b, a discharge passage 826c, a bush accommodation hole 826d and a blade accommodation hole 826e.
- the cylinder bore 126a is a cylindrical bore penetrating along the thickness direction as shown in FIGS.
- the suction hole 826b passes from the outer peripheral wall surface to the cylinder hole 826a.
- the discharge passage 826c is formed by cutting out a part of the inner peripheral side of the cylindrical portion that forms the cylinder hole 826a.
- the bush accommodating hole 826 d is a hole penetrating along the thickness direction, and is disposed between the intake hole 826 b and the discharge path 826 c when viewed along the thickness direction.
- the blade accommodation hole 826e is a hole penetrating along the thickness direction, and is in communication with the bush accommodation hole 826d.
- the second cylinder block 826 is an eccentric shaft of the crankshaft 817 in the cylinder hole 826 a.
- the discharge is performed in a state in which the portion 817b and the roller portion 821a of the piston 821 are accommodated, the blade portion 821b and the bush 822 of the piston 821 are accommodated in the bush accommodation hole 826d, and the blade portion 821b of the piston 821 is accommodated in the blade accommodation hole 826e.
- the rear head 827 and the middle plate 825 are fitted so that the path 826c faces the rear head 827 (see FIG. 61).
- a second cylinder chamber Rc2 is formed in the swing compression mechanism 815, and the second cylinder chamber Rc2 is divided into a suction chamber communicating with the suction hole 826b by the piston 821 and a discharge chamber communicating with the discharge passage 826c. It will be done.
- the crankshaft 817 is provided with two eccentric shaft portions 817a and 817b at one end.
- the two eccentric shaft portions 817a and 817b are formed such that their eccentric shafts face each other across the central axis of the crankshaft 817.
- the crankshaft 817 is fixed to the rotor 852 of the drive motor 816 on the side where the eccentric shafts 81 7 a and 817 b are not provided.
- the piston 821 as shown in FIGS. 59 and 62, has a substantially cylindrical roller portion 821a, and a blade portion 821b protruding radially outward of the roller portion 821a.
- the roller part 821a is fitted to the eccentric shaft parts 817a and 817b of the crankshaft 817, the cylinders of the cylinder blocks 824 and 826:? 824a, 826a [This is being inserted. [This is because, when the crankshaft 817 rotates, the mouth ⁇ a 21a performs a revolving motion around the rotation axis of the crankshaft 817.
- the blade portion 821 b is accommodated in the bush accommodation holes 824 d and 826 d and the blade accommodation holes 824 e and 826 e. As a result, the blade portion 821b swings and moves back and forth along the longitudinal direction.
- the bush 822 is a substantially semi-cylindrical member, and is accommodated in the bush accommodation holes 824 d and 826 d so as to sandwich the blade portion 821 b of the piston 821.
- the front head 823 is a member that covers the discharge passage 824c side of the first cylinder block 824, and is fitted to the casing 810.
- a bearing portion 823a is formed on the front head 823, and a crankshaft 817 is inserted into the bearing portion 823a.
- this front The head 823 is formed with an opening 823 b for guiding the refrigerant gas flowing through the discharge passage 824 c formed in the first cylinder block 824 to the discharge pipe 820. Then, the opening 823 b is closed or opened by a discharge valve (not shown) for preventing the backflow of the refrigerant gas.
- a bearing portion 827a is formed on the rear head 827.
- a crankshaft 817 is inserted into the bearing portion 827a.
- the rear head 827 is formed with an opening (not shown) for guiding the refrigerant gas flowing through the discharge passage 8 26 c formed in the second cylinder block 826 to the discharge pipe 820. The opening is closed or opened by a discharge valve (not shown) for preventing backflow of the refrigerant gas.
- the middle plate 825 is disposed between the first cylinder block 824 and the second cylinder block 826, and divides the first cylinder chamber Rcl and the second cylinder chamber Rc2.
- the drive motor 816 is a direct current motor in the fifth embodiment and mainly rotates with an annular stator 851 fixed to the inner wall surface of the casing 810 and a slight gap (air gap passage) inside the stator 851. It is composed of a rotor 852 housed freely.
- a tooth portion (not shown) and a copper wire are wound around the stator 851 and a coil end 853 is formed on the upper and lower sides. Further, a core cut portion (not shown) is provided on the outer peripheral surface of the stator 851 so as to be cut out at a plurality of locations at predetermined intervals in the circumferential direction along the upper end surface force lower surface of the stator 851. It is.
- a crankshaft 817 is fixed to the rotor 852 along the rotation axis.
- the suction pipe 819 is provided so as to penetrate the casing 810, and one end thereof is fitted in the suction holes 824b and 826b formed in the first cylinder block 824 and the second cylinder block 826, and the other end is Accumulator 895 is fitted.
- the discharge pipe 820 is provided to penetrate the upper wall portion 812 of the casing 810.
- the muffler 860 is for muffling the discharge noise of the refrigerant gas, and is attached to the front head 823.
- the cylinder blocks 824 and 826, the screw tons 821 and the crankshaft 817 are manufactured by the same manufacturing method as the method of manufacturing the sliding component of the first embodiment.
- the piston 821 and the crankshaft 817 are heat treated under conditions such that the hardness is higher than HRB 90 and lower than HRB 100.
- a high frequency heater is inserted in the bush accommodation holes 824d, 826d of the cylinder blocks 824, 826, and the hardness around the bush accommodation holes 824d, 826d is higher than HRC 50.
- the cylinder blocks 824, 826 are subjected to high frequency heat treatment so as to be lower than them.
- the cylinder blocks 824 and 826 before the high frequency heat treatment are heat treated under conditions such that the hardness is higher than HRB 90 and lower than HRB 100.
- high-frequency heat treatment is applied to portions of the main shaft portion and the sub shaft portion accommodated in the front head 823 and the rear head 827.
- the cylinder blocks 824, 826 and the piston 821 are manufactured through a semi-melt die casting molding process and a heat treatment process. For this reason, it is possible to easily obtain a cylinder block or piston having high tensile strength and high rigidity as compared with a cylinder block or piston made of flake graphite pig iron manufactured by a conventional sand-type manufacturing method (heat treatment is performed Higher strength and rigidity than FC 250).
- the cylinder blocks 824 and 826 and the pistons 821 are manufactured through the half-melt die casting molding process and the heat treatment process, and the hardness thereof is adjusted to be higher than HRB 90 and lower than HRB 100.
- the cylinder blocks 824 and 826 and the piston 821 substantially correspond to the range of 600 MPa to 900 MPa.
- the cylinder blocks 824 and 826 and the piston 821 can be thinned if the method of manufacturing sliding parts of this compressor is adopted. Therefore, the swing compressor 801 can be reduced in diameter, which reduces the wear of the cylinder blocks 824 and 826 and the piston 821 and increases the compression capacity.
- heat treatment is performed such that the hardness of the cylinder block base and the piston base is higher than HRB 90 and lower than HRB 100. For this reason, when the method of manufacturing sliding parts of this compressor is adopted, sufficient durability can be exhibited during operation of the compressor, and "adaptation" occurs as early as possible. As soon as possible, no burn-in can occur during abnormal operation!
- the cylinder blocks 824, 826 and the piston 82 1 can be manufactured. Further, when the hardness is in this range, the machinability of the cylinder block base and the piston base is improved and the cylinder block base and the piston base are scratched.
- a high frequency heater is further inserted into the bush accommodation holes 824 d and 826 d, and the periphery of the bush accommodation holes 824 d and 826 d
- the hardening treatment is applied so that the hardness of the part of H is higher than HRC 50 and lower than HRC 65. Because of this, natural refrigerants such as CO
- high-frequency heat treatment is applied to the portion of the main shaft portion, the sub-shaft portion, and the eccentric shaft portion to which the piston 821 is fitted, of the crankshaft 817 accommodated in the front head 823 and rear head 827. Therefore, sufficient wear resistance can be provided to the main shaft portion, the sub shaft portion and the eccentric shaft portion. Therefore, the life of the crankshaft 817 can be extended.
- partial heat treatment is performed on the peripheral portion SC8 of the base of the blade portion 821b of the piston 821 where stress is easily concentrated. For this reason, the piston 121 is unlikely to be broken even if a slightly large load is applied to the blade portion 121b.
- the bush is accommodated.
- a high frequency heater was inserted into the holes 824d and 826d, and quenching was performed so that the hardness around the bush accommodation holes 824d and 826d was higher than HRC 50 and lower than HRC 65.
- such a hardness adjusting technique may be applied to the cylinder block 924 and the roller 921 of the rotary compressor 901 as shown in FIG.
- a high frequency heater is inserted into the vane housing hole 924d.
- the hardness of the part around the bay accommodation hole 924d is higher than HRC50 and lower than HRC65.
- the cylinder block 924 may be quenched (see Figure 63).
- vanes 922 may be manufactured in a similar manner. In FIGS.
- reference numeral 924a denotes a cylinder hole
- reference numeral 924c denotes a discharge passage
- reference numeral 924b denotes a suction hole
- reference numeral 917 denotes a crankshaft
- reference numeral 917a denotes an eccentric shaft portion of the crankshaft.
- 923 indicates a spring
- Rc 3 indicates a cylinder chamber.
- the roller 921 and the cylinder block 924 may be manufactured according to the manufacturing method described in the modification (H) of the first embodiment.
- the swing compressor 801 is a two-cylinder type swing compressor.
- the force compressor may be a single-cylinder type swing compressor! /.
- the cylinder blocks 824, 826 and pistons 821 are manufactured through the semi-molten die casting molding process and the heat treatment process, but additionally the crank shaft 817, the front head 823, the rear head Sliding parts such as 827 and middle plate 825 may be manufactured through the same process.
- the sliding parts of the compressor according to the present invention have high tensile strength, can exhibit sufficient durability during operation, and “adaptation” occurs as early as possible. Immediately, since seizure does not occur during abnormal operation, it is useful as a compressor for renewal demand.
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- Engineering & Computer Science (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
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Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07714944.1A EP1992821B1 (en) | 2006-02-28 | 2007-02-26 | Sliding component of compressor, sliding component base, scroll component, and compressor |
AU2007219764A AU2007219764B2 (en) | 2006-02-28 | 2007-02-26 | Compressor slider, slider preform, scroll part and compressor |
CN2007800071109A CN101395377B (zh) | 2006-02-28 | 2007-02-26 | 压缩机的滑动部件、滑动部件基体、涡旋部件以及压缩机 |
KR1020087023389A KR101122533B1 (ko) | 2006-02-28 | 2007-02-26 | 압축기의 접동 부품, 접동 부품 기체, 스크롤 부품 및 압축기 |
BRPI0708364-5A BRPI0708364A2 (pt) | 2006-02-28 | 2007-02-26 | componente deslizante de compressor, base de componente deslizante, componente de rolamento, e compressor |
US12/280,927 US8366425B2 (en) | 2006-02-28 | 2007-02-26 | Compressor slider, slider preform, scroll part, and compressor |
ES07714944.1T ES2536506T3 (es) | 2006-02-28 | 2007-02-26 | Parte de deslizamiento del compresor, preforma de la parte de deslizamiento, parte de la espiral y compresor |
Applications Claiming Priority (18)
Application Number | Priority Date | Filing Date | Title |
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JP2006053141 | 2006-02-28 | ||
JP2006-053141 | 2006-02-28 | ||
JP2006055129 | 2006-03-01 | ||
JP2006-055129 | 2006-03-01 | ||
JP2006056276 | 2006-03-02 | ||
JP2006-056276 | 2006-03-02 | ||
JP2006-069141 | 2006-03-14 | ||
JP2006069141 | 2006-03-14 | ||
JP2006-074692 | 2006-03-17 | ||
JP2006074692A JP5329744B2 (ja) | 2006-03-17 | 2006-03-17 | スクロール圧縮機のスクロール部材 |
JP2006114819 | 2006-04-18 | ||
JP2006-114819 | 2006-04-18 | ||
JP2006250058A JP4821526B2 (ja) | 2006-03-02 | 2006-09-14 | 圧縮機のスクロール部材およびそれを用いた圧縮機 |
JP2006-250058 | 2006-09-14 | ||
JP2006251427 | 2006-09-15 | ||
JP2006-251427 | 2006-09-15 | ||
JP2006269128A JP2008088860A (ja) | 2006-09-29 | 2006-09-29 | 圧縮機の摺動部品、スクロール部品、クランク軸部品、自転防止部材、およびスイング圧縮機のピストン部品 |
JP2006-269128 | 2006-09-29 |
Publications (1)
Publication Number | Publication Date |
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WO2007099919A1 true WO2007099919A1 (ja) | 2007-09-07 |
Family
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2007/053551 WO2007099919A1 (ja) | 2006-02-28 | 2007-02-26 | 圧縮機の摺動部品、摺動部品基体、スクロール部品及び圧縮機 |
Country Status (8)
Country | Link |
---|---|
US (1) | US8366425B2 (ja) |
EP (1) | EP1992821B1 (ja) |
KR (1) | KR101122533B1 (ja) |
CN (1) | CN101395377B (ja) |
AU (1) | AU2007219764B2 (ja) |
BR (1) | BRPI0708364A2 (ja) |
ES (1) | ES2536506T3 (ja) |
WO (1) | WO2007099919A1 (ja) |
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CN105736321A (zh) * | 2016-04-18 | 2016-07-06 | 瑞智(青岛)精密机电有限公司 | 一种可提高脉冲次数的新型压缩机顶盖 |
KR102487906B1 (ko) | 2016-04-26 | 2023-01-12 | 엘지전자 주식회사 | 스크롤 압축기 |
KR102489482B1 (ko) * | 2016-04-26 | 2023-01-17 | 엘지전자 주식회사 | 스크롤 압축기 |
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- 2007-02-26 KR KR1020087023389A patent/KR101122533B1/ko active IP Right Grant
- 2007-02-26 CN CN2007800071109A patent/CN101395377B/zh active Active
- 2007-02-26 BR BRPI0708364-5A patent/BRPI0708364A2/pt not_active Application Discontinuation
- 2007-02-26 WO PCT/JP2007/053551 patent/WO2007099919A1/ja active Application Filing
- 2007-02-26 AU AU2007219764A patent/AU2007219764B2/en not_active Ceased
- 2007-02-26 US US12/280,927 patent/US8366425B2/en active Active
- 2007-02-26 ES ES07714944.1T patent/ES2536506T3/es active Active
- 2007-02-26 EP EP07714944.1A patent/EP1992821B1/en active Active
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Also Published As
Publication number | Publication date |
---|---|
KR20080092480A (ko) | 2008-10-15 |
CN101395377A (zh) | 2009-03-25 |
BRPI0708364A2 (pt) | 2011-05-24 |
US20100061871A1 (en) | 2010-03-11 |
KR101122533B1 (ko) | 2012-03-15 |
EP1992821A4 (en) | 2014-01-01 |
AU2007219764B2 (en) | 2010-09-02 |
EP1992821B1 (en) | 2015-04-01 |
CN101395377B (zh) | 2011-09-07 |
EP1992821A1 (en) | 2008-11-19 |
ES2536506T3 (es) | 2015-05-26 |
US8366425B2 (en) | 2013-02-05 |
AU2007219764A1 (en) | 2007-09-07 |
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