JP2009052564A - Compression mechanism and scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent seizure, while enhancing strength and rigidity of a compression mechanism. <P>SOLUTION: This scroll compressor 1 has the compression mechanism 15. The compression mechanism 15 has a fixed scroll 24 and a movable scroll 26, and compresses a refrigerant. A construction material is mutually differently used in the fixed scroll and the movable scroll. Actually, any one of the fixed scroll 24 and the movable scroll 26 is a mold of molding cast iron by a half-melting die-cast method. The other is a gray case iron product. The ratio h1/d1 and h2/d2 of the height h1 and h2 to the thickness d1 and d2 of a compression member belonging to the mold is set to 13 to 19. A material having tensile strength of 250N/mm<SP>2</SP>to 300N/mm<SP>2</SP>can be adopted for the gray cast iron product. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a compressor and a scroll compressor, and particularly to a material used for a compression mechanism.

  The scroll-type compressor includes a compression mechanism that compresses the refrigerant. The compression mechanism includes a fixed scroll and a movable scroll having a compression member extending in a spiral shape that meshes with each other.

  Conventionally, the same material is often used for the fixed scroll and the movable scroll. It has been proposed to employ, for example, a gray cast iron product or a molded product obtained by molding cast iron by a semi-molten die casting method.

In addition, the technique relevant to this invention is shown below.
JP 2005-36693 A

  However, when the same material is used for the fixed scroll and the movable scroll, there are the following problems.

  That is, even if the strength and rigidity of the compression mechanism can be increased, seizure between the fixed scroll and the movable scroll tends to occur. When seizure occurs, the compression mechanism cannot be driven. Such a problem is remarkable when a molded product obtained by a semi-molten die casting method is employed.

  Moreover, even if the seizure could be made difficult to occur, the strength and rigidity of the compression mechanism remained low. In order to reduce the size of the compression mechanism while ensuring the same suction volume, it is necessary to reduce the thickness of the spiral compression member and increase its height. However, if the strength and rigidity are low, the compression member may be deformed or broken during driving. Such a problem is remarkable when a gray cast iron product is employed.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to prevent seizure while increasing the strength and rigidity of the compression mechanism.

  A compression mechanism according to a first invention is a compression mechanism used for a scroll compressor, and includes a fixed scroll and a movable scroll. The fixed scroll has a first compression member and a first fixed member. The first compression member extends in a spiral shape. The first fixing member fixes the first compression member. The movable scroll has a second compression member and a second fixed member. The second compression member extends in a spiral shape and meshes with the first compression member. The second fixing member fixes the second compression member. One of the fixed scroll and the movable scroll is a molded product obtained by molding cast iron by a semi-molten die casting method, and the other is a gray cast iron product. Further, the ratio of the height to the thickness of the compression member belonging to the molded product is 13 or more and 19 or less.

  The compression mechanism according to the second invention is the compression mechanism according to the first invention, wherein the sum of the area ratio of graphite on the surface of the molded product and the area ratio of graphite on the surface of the gray cast iron product is 10%. It is 20% or less.

  The compression mechanism according to the third invention is the compression mechanism according to the second invention, wherein the area ratio of graphite of the molded product is 2% or more and 6% or less.

A compression mechanism according to a fourth invention is the compression mechanism according to any one of the first to third inventions, and the tensile strength of the gray cast iron product is 250 N / mm ² or more and less than 300 N / mm ² . is there.

  A compression mechanism according to a fifth invention is the compression mechanism according to any one of the first to fourth inventions, wherein the fixed scroll is a gray cast iron product and the movable scroll is a molded product.

  A compression mechanism according to a sixth aspect of the present invention is the compression mechanism according to the fifth aspect of the present invention, and the movable scroll is arranged to be pressed against the fixed scroll side.

  A compression mechanism according to a seventh aspect is the compression mechanism according to the fifth or sixth aspect, wherein the first fixed member of the fixed scroll has a hole communicating the first space and the second space. Is provided. The first space is formed by the first compression member of the fixed scroll and extends in a spiral shape. The second space is located on the side opposite to the movable scroll. The second compression member of the movable scroll can block the entrance on the first space side of the hole.

  A compression mechanism according to an eighth aspect of the present invention is the compression mechanism according to the seventh aspect of the present invention, wherein the hole when viewed from the movable scroll side partially overlaps the first compression member of the fixed scroll.

  A compression mechanism according to a ninth aspect is the compression mechanism according to any one of the fifth to eighth aspects, wherein the movable scroll further includes an extension member. The extension member is a member that extends from the outer peripheral end of the second compression member of the movable scroll, and does not mesh with the first compression member of the fixed scroll.

  A compression mechanism according to a tenth invention is the compression mechanism according to any one of the first to ninth inventions, and is a gray cast iron product having a thickness of a compression member belonging to a molded product among a fixed scroll and a movable scroll. Is equal to a value calculated based on the ratio of the Young's modulus of the molded product to the Young's modulus of the gray cast iron product.

  A compression mechanism according to an eleventh aspect of the invention is the compression mechanism according to the tenth aspect of the invention, wherein the thickness ratio is equal to or less than the reciprocal of the Young's modulus ratio.

  A compression mechanism according to a twelfth invention is the compression mechanism according to the tenth or eleventh invention, wherein the Young's modulus of the molded product is 175 GPa or more and 190 GPa or less.

  A scroll compressor according to a thirteenth aspect includes the compression mechanism according to any one of the first to twelfth aspects.

  A scroll compressor according to a fourteenth invention is a scroll compressor according to the thirteenth invention, and compresses a refrigerant containing carbon dioxide as a main component.

  According to the compression mechanism of the first invention, since either the fixed scroll or the movable scroll is a molded product by a semi-molten die cast method and the other is a gray cast iron product, both are by a semi-molten die cast method. Compared to a molded product, the fixed scroll and the movable scroll are less likely to seize.

  Moreover, since the molded product by the semi-molten die casting method has higher strength and rigidity than the gray cast iron product, in the fixed scroll and the movable scroll having the compression members extending in a spiral shape that mesh with each other, both the fixed scroll and the movable scroll are used. The thickness of the compression member can be made smaller than when a gray cast iron product is used. Therefore, the compression mechanism can be reduced in size while ensuring the same suction volume. When the same size compression mechanism is employed, the suction volume can be increased.

  Furthermore, since the molded product by the semi-molten die casting method has higher rigidity than the gray cast iron product, it is possible to prevent the compression mechanism from being deformed by the pressure during compression. Therefore, the compressed gas hardly leaks from the compression mechanism, thereby preventing the compressor efficiency from being lowered.

  According to the compression mechanism of the second invention, since the sum of the area ratios of graphite is large, it is easy to prevent seizure between the fixed scroll and the movable scroll.

  According to the compression mechanism according to the third invention, it is possible to ensure the graphite area ratio necessary for preventing seizure in the molded product. Therefore, the fixed scroll and the movable scroll are not easily seized.

  According to the compression mechanism of the fourth invention, it is possible to ensure the strength and rigidity necessary to prevent deformation and breakage.

  According to the compression mechanism according to the fifth aspect of the present invention, since the molded article by the semi-molten die casting method has high strength and rigidity, the fixed scroll and the movable scroll having the compression members extending in a spiral shape that mesh with each other. The thickness of the compression member can be made smaller than when a gray cast iron product is used for both scrolls. Therefore, the compression mechanism can be reduced in size while ensuring the same suction volume. When the same size compression mechanism is employed, the suction volume can be increased. In addition, the movable scroll can be lightened, and thus the torque required for driving the movable scroll can be reduced. Furthermore, an increase in cost due to the use of a molded product by a semi-molten die casting method can be suppressed.

  According to the compression mechanism according to the sixth aspect of the invention, it is possible to prevent a gap from being generated between the fixed scroll and the second compression member of the movable scroll, thereby preventing a reduction in compressor efficiency. In addition, the movable scroll is a molded product by the semi-molten die casting method and has high strength and rigidity, so that it is not easily deformed even when pressed against the fixed scroll.

  According to the compression mechanism concerning 7th invention, the fall of the compressor efficiency by having provided the hole can be prevented. This is because when the second compression member of the movable scroll crosses the hole, the entrance of the hole does not open on both sides of the second compression member. That is, the first space partitioned by the first compression member does not communicate through the hole.

  According to the compression mechanism of the eighth invention, the area of the outlet on the second space side can be made larger than the area of the inlet on the first space side. Therefore, the escape of compressed gas can be improved.

  According to the compression mechanism of the ninth aspect, by providing the second portion, the strength and rigidity of the end of the first portion on the side opposite to the center of the spiral is increased. Therefore, deformation at the time of processing the first portion can be prevented.

  According to the compression mechanism according to the tenth aspect of the present invention, by calculating the thickness ratio based on the Young's modulus ratio, the amount of bending of the compression member of the molded product and the bending of the compression member of the gray cast iron product are calculated. The amount can be made approximately equal. Therefore, it is possible to prevent a decrease in compressor efficiency due to the compression member being bent.

  According to the compression mechanism according to the eleventh invention, the thickness of the compression member of the molded product can be reduced, so that the compression mechanism can be reduced in size.

  According to the compression mechanism according to the twelfth aspect of the invention, the compressor efficiency is hardly lowered due to the bending of the molded product.

  According to the scroll compressor according to the thirteenth aspect of the present invention, seizure between the fixed scroll and the movable scroll is prevented in the compression mechanism. Therefore, the scroll compressor is unlikely to break down.

  According to the scroll compressor according to the fourteenth aspect of the present invention, the compressor efficiency of the scroll compressor can be improved even when carbon dioxide is used as the refrigerant.

  FIG. 1 is a diagram conceptually showing a scroll compressor 1 according to an embodiment of the present invention. Note that FIG. 1 shows a direction 91, and in the following, the tip side of the arrow in the direction 91 is referred to as “upper side” and the opposite side is referred to as “lower side”.

  The scroll compressor 1 includes a case 11 and a compression mechanism 15. The case 11 is cylindrical and extends along the direction 91. The compression mechanism 15 is accommodated in the case 11.

  FIG. 2 is a view showing a cross section of the compression mechanism 15 at the position II-II shown in FIG. The compression mechanism 15 includes a fixed scroll 24 and a movable scroll 26, and compresses the refrigerant (FIGS. 1 and 2). As the refrigerant, for example, a refrigerant containing carbon dioxide as a main component can be adopted.

  The fixed scroll 24 includes an end plate 24a and a compression member 24b. The end plate 24a is fixed to the inner wall 11a of the case 11, and the compression member 24b is connected to the lower side of the end plate 24a (FIG. 1). The compression member 24b extends in a spiral shape, and a groove 24c is formed between the spirals (FIG. 2). The end plate 24a can be understood as a fixing member that fixes the compression member 24b.

  The movable scroll 26 includes an end plate 26a and a compression member 26b. The compression member 26b is connected to the upper side of the end plate 26a (FIG. 1) and extends in a spiral shape (FIG. 2). The end plate 26a can be understood as a fixing member that fixes the compression member 26b.

  The compression member 26b fits in the groove 24c of the fixed scroll 24 (FIG. 2). In the compression mechanism 15, the space 40 between the compression member 24b and the compression member 26b is sealed with the end plates 24a and 26a, thereby being used as a compression chamber (FIG. 1).

  Hereinafter, regarding the compression mechanism 15, the materials used for the fixed scroll 24 and the movable scroll 26, the shapes of the compression members 24 b and 26 b, and the relief holes provided in the fixed scroll 24 are respectively described in the first to third embodiments. explain.

First embodiment.
In the compression mechanism 15 according to the present embodiment, the materials used for the fixed scroll 24 and the movable scroll 26 are different from each other.

Specifically, one of the fixed scroll 24 and the movable scroll 26 is a molded product (hereinafter referred to as “semi-molten die cast molded product”) formed of cast iron by a semi-molten die casting method. A semi-molten die-cast molded product having a tensile strength of 600 N / mm ² or more and 900 N / mm ² or less can be used.

The other is a gray cast iron product. A gray cast iron product having a tensile strength of 250 N / mm ² or more and less than 300 N / mm ² can be used. This is because the strength and rigidity necessary to prevent deformation and breakage can be ensured. A gray cast iron product having a tensile strength of 250 N / mm ² or more and less than 300 N / mm ² is standardized as FC250 by JIS (Japanese Industrial Standards).

  FIG. 3 is a table showing values of seizure-resistant surface pressure (MPa), graphite area ratio (%), and hardness (HRB) of the compression mechanism 15. Here, the surface pressure against seizure is the surface pressure at which seizure occurs in the seizure resistance test. In the seizure resistance test, a pin-shaped product (hereinafter referred to as “pin”) is slid under a predetermined condition on the surface of a disk-shaped product (hereinafter referred to as “disk”). To do. The predetermined condition is that the pin is slid at an average speed of 2.0 (m / s) in a state where the disk and the pin are immersed in a mixed solution of R410A refrigerant and ether oil (100 ° C.). Then, the surface pressure between the pins and the disk is changed to measure the surface pressure at which seizure occurs. The graphite area ratio is the ratio of the area occupied by graphite per unit area.

  In FIG. 3, one of the fixed scroll 24 and the movable scroll 26 is represented as a sliding member A and the other is represented as a sliding member B, and the graphite area ratio (%) and hardness (HRB) are also shown. . Hereinafter, the sum of the graphite area ratio of the sliding member A and the graphite area ratio of the sliding member B is simply referred to as “graphite area ratio”.

  FIG. 3 shows a result of a seizure resistance test using a pin-shaped semi-molten die cast product and a disk-shaped gray cast iron product (FC250) (in FIG. 3, “semi-molten die cast molding”). Product / FC250 ”). For comparison with this result, a result of a seizure resistance test using the same material for the pin and the disk is also shown.

In the case of using the same material, FIG.
1. When using pins and discs of gray cast iron (FC250) (represented as “FC250s” in FIG. 3),
2. The case where a pin and a disk molded by the semi-molten die casting method are used (represented as “half-molten die cast molded products” in FIG. 3) is exemplified.

  As shown in FIG. 3, in the “semi-molten die cast product / FC250”, the surface pressure against seizure is 152 (MPa). The graphite area ratio is 10 to 20 (%), the graphite area ratio of the sliding member A is 2 to 6 (%), and the graphite area ratio of the sliding member B is 8 to 14 (%). The hardness of the sliding member A is HRB90 to HRB100, and the sliding member B is HRB90 to HRB100. FIG. 3 shows values when the sliding member A is a semi-molten die cast product and the sliding member B is a gray cast iron product (FC250).

  On the other hand, the surface pressure against seizure is 169 (MPa) in “FC250 to each other”. The graphite area ratio is 28 (%), and the graphite area ratio of each of the sliding members A and B is 14 (%). The hardness of each of the sliding members A and B is HRB93.

  In “half-molten die-cast molded products”, the surface pressure against seizure is 140 (MPa). The graphite area ratio is 8 (%), and the respective graphite area ratios of the sliding members A and B are 4.0 (%). The hardness of each of the sliding members A and B is HRB98.

  According to the test results shown in FIG. 3, the “semi-molten die cast molded product / FC250” is larger than the “half-molten die cast molded product” with respect to the seizure-resistant surface pressure. The reason will be described below.

  FIG. 4 is a graph showing the relationship between the graphite area ratio and the surface pressure against seizure. According to the graph shown in FIG. 4, it can be seen that the surface pressure against seizure increases as the graphite area ratio increases. That is, since the area ratio of graphite is higher in “semi-molten die cast molded product / FC250” than in “semi-molten die cast molded products”, the surface pressure against seizure is also increased.

  In “Semi-molten die cast product / FC250”, the graphite area ratio of the gray cast iron product (FC 250) is 8 to 14 (%) and the graphite area ratio is 2 to 6 (%). Is significantly larger than It can be considered that the remarkable difference in the graphite area ratio between the pin and the disk is one factor that increases the surface pressure against seizure. In order to prevent seizure in the molded product, a graphite area ratio of at least about 2 (%) is required.

  As described above, according to the compression mechanism 15 according to the present embodiment, the fixed scroll 24 and the movable scroll 26 are baked more than when the semi-molten die cast product is used for both the fixed scroll 24 and the movable scroll 26. Sticking can be prevented.

  In addition, the hardness is higher and the strength and rigidity are higher than when the gray cast iron product (FC250) is used for both the fixed scroll 24 and the movable scroll 26. Therefore, the thickness d2 (d1) of the compression member 26b (24b) is reduced (FIG. 2) and the height of the scroll member of the fixed scroll 24 and the movable scroll 26 which is the semi-molten die cast product. Therefore, the compression mechanism 15 can be reduced in size without reducing the compressor efficiency. When the compression mechanism 15 having the same size is employed, the suction volume can be increased.

  In the compression mechanism 15, the graphite area ratio of the semi-molten die cast product is preferably 4 to 6 (%). This is because the hardness of the semi-molten die cast product is close to that of HRB90 (HRB90 to HRB95), so that the workability of the semi-molten die cast product is improved.

  In the compression mechanism 15, it is preferable to employ a gray cast iron product (FC 250) for the fixed scroll 24 and a semi-molten die cast molded product for the movable scroll 26. This is because the semi-molten die-cast molded product has high strength and rigidity, and by applying this to the movable scroll 26, the thickness of the compression member 26b and the thickness of the end plate 26a can be reduced.

  Thereby, the compression mechanism 15 can be reduced in size while ensuring the same suction volume. In the compression mechanism 15 having the same size, the suction volume can be increased. In addition, the movable scroll 26 can be lightened, and thus the torque required for driving the movable scroll 26 can be reduced. Furthermore, an increase in cost due to the use of a semi-molten die cast product can be suppressed.

  The movable scroll 26 is disposed to be pressed against the fixed scroll 24 side. This is to prevent a gap from being generated between the fixed scroll 24 and the compression member 26b of the movable scroll 26, that is, to prevent a reduction in compressor efficiency.

  In the mode of being arranged by pressing, a semi-molten die-cast molded product is adopted for the movable scroll 26. This is because the strength and rigidity of the movable scroll 26 are increased, so that even when the movable scroll 26 is pressed against the fixed scroll 24, the compression member 26b is not deformed.

Second embodiment.
In the present embodiment, the shape of the compression mechanism 15 described in the first embodiment will be described.

<Thickness of compression member>
As described in the first embodiment, by using a semi-molten die cast molded product for either one of the fixed scroll 24 and the movable scroll 26, the strength and rigidity of the scroll member of the semi-molten die cast molded product can be increased. Increase. Thereby, the scroll member of the semi-molten die-cast molded product is hardly broken and hardly bent.

  On the other hand, when the strength and rigidity of the scroll member are increased, the thickness d2 (d1) of the compression member 26b (24b) of the semi-molten die cast molded product can be reduced. However, the strength of the semi-molten die cast molded product is 2.4 to 3.6 times the strength of FC250 (600 to 900 MPa / 250 MPa), whereas the stiffness is 1.6 to 1. It is only about 7 times (175 to 190 GPa / 110 GPa). For this reason, if thickness d2 (d1) which does not produce a fracture | rupture is determined based on intensity | strength, the compression member 26b (24b) will become easy to bend.

  Therefore, of the fixed scroll 24 and the movable scroll 26, the thickness d2 (d1) of the compression member 26b (24b) of the semi-molten die cast molded product and the thickness d1 of the compression member 24b (26b) of the gray cast iron product. The ratio d2 / d1 (d1 / d2) to (d2) is calculated based on the ratio α of the Young's modulus of the semi-molten die cast product to the Young's modulus of the gray cast iron product.

  For example, when a gray cast iron product is used for the fixed scroll 24 and a semi-molten die cast product is used for the movable scroll 26, the ratio d2 / d1 of the thickness d2 of the compression member 26b to the thickness d1 of the compression member 24b is set to Young It is made equal to the value calculated based on the ratio α.

  A value of about 1.6 is adopted as the Young's modulus ratio α. Further, from the viewpoint of preventing reduction in compressor efficiency due to bending of the semi-molten die cast product, the Young's modulus of the semi-molten die cast product is preferably 175 (GPa) or more and 190 (GPa) or less. .

  By determining the thicknesses d1 and d2 so as to be a ratio d2 / d1 (d1 / d2) calculated based on the ratio of Young's modulus, the amount of bending of the compression member 24b and the amount of bending of the compression member 26b are substantially equal. can do. Therefore, in the compression mechanism 15, it is possible to prevent the compressor efficiency from being lowered due to the bending of the compression members 24b and 26b.

  When priority is given to downsizing and large capacity of the compression mechanism 15, from the viewpoint of reducing the thickness d2 (d1) of the scroll member of the semi-molten die cast molded product, the thickness ratio d2 / d1 (d1 / d2) ) Is less than or equal to the reciprocal number (= 1 / α) of the Young's modulus ratio α.

  When a semi-molten die-cast molded product is used for the fixed scroll 24 and a gray cast iron product is used for the movable scroll 26, the ratio d1 / d2 of the thickness d1 of the compression member 24b to the thickness d2 of the compression member 26b is determined by Young's modulus. Is calculated based on the ratio α. Also in this aspect, the amount of bending of each of the compression members 24b and 26b can be made substantially equal as described above.

<Shape of compression member>
FIG. 5 is a view showing a compression mechanism 15 that has a shape different from the shape shown in FIG. FIG. 5 shows a cross section at a position II-II shown in FIG.

  As described in the first embodiment, the thickness d2 (d1) of the compression member 26b (24b) is reduced for the scroll member of the semi-molten die-cast molded product among the fixed scroll 24 and the movable scroll 26. Can do. In consideration of the bending of the compression member 26b (24b) when the compression mechanism 15 is driven, the thickness d2 (d1) of the height h2 (h1) of the compression member 26b (24b) from the end plate 26a (24a). ) Ratio h2 / d2 (h1 / d1) is preferably 13 or more and 19 or less.

  In the fixed scroll 24, the outer peripheral end 24 b 2 of the compression member 24 b is supported by another member 24 d belonging to the fixed scroll 24. For this reason, even if a semi-molten die-cast molded product is adopted for the fixed scroll 24 and the thickness d1 is reduced, it is difficult to process the compression member 24b.

  On the other hand, in the movable scroll 26, the outer peripheral end 26 b 2 of the compression member 26 b is not fixed like the fixed scroll 24. For this reason, when the compression member 26b is processed, particularly when the end 26b2 on the outer peripheral side is processed, bending occurs, so that the compression member 26b is difficult to process.

  Further, the strength of the semi-molten die-cast product is 2.4 to 3.6 times the strength of FC250 (600 to 900 MPa / 250 MPa), whereas the stiffness is 1.6 to 1. It is only about 7 times (175 to 190 GPa / 110 GPa). For this reason, if thickness d2 (d1) which does not produce a fracture | rupture is determined based on intensity | strength, the compression member 26b (24b) will become easy to bend.

  Therefore, for the movable scroll 26 in which the semi-molten die cast product is adopted, the thickness of the portion near the outer peripheral end 26b of the compression member 26b is made larger than the thickness of the other portion. Thereby, the compression member 26b can be processed with high accuracy.

  6 to 8 are diagrams showing the shape of the compression member 26b before processing. 6 to 8, only the portion near the outer end 26b2 of the compression member 26b of the movable scroll 26 is shown.

  In FIG. 6, the portion near the end 26b2 is thicker toward the outside than the other portion of the compression member 26b (thickness d12). In this case, the processing in the vicinity of the end 26b2 is performed as follows.

  That is, finishing is performed on the inner surface. At this time, the portion in the vicinity of the end 26b2 is thicker toward the outside, so that it hardly bends even if the inner surface is finished. Therefore, finishing is easy.

  Thereafter, the thickened portion is shaved to finish the portion near the end 26b2. In FIG. 6, the compressed member 26b after processing is indicated by a broken line.

  In FIG. 7, the portion near the end 26b2 is thicker inward than the other portion of the compression member 26b (thickness d13). In this case, the processing in the vicinity of the end 26b2 is performed as follows.

  That is, finishing is performed on the outer surface. At this time, the portion in the vicinity of the end 26b2 is thicker toward the inner side, so that it hardly bends even if the outer surface is finished. Therefore, finishing is easy.

  Thereafter, the thickened portion is shaved to finish the portion near the end 26b2. In FIG. 7, the processed compression member 26b is indicated by a broken line.

  In FIG. 8, the portion in the vicinity of the end 26b2 is thicker toward both the outer side and the inner side than the other portion of the compression member 26b (thickness d14). In this case, the processing in the vicinity of the end 26b2 is performed as follows.

  That is, roughing and finishing are performed in this order on the outer or inner surface. For example, when roughing and finishing are performed on the inner surface, the portion in the vicinity of the end 26b2 is thicker toward the outer side, so that even if these processes are performed on the inner surface, the inner surface hardly bends. Therefore, the processing of the inner surface is easy.

  After that, the outer thick part is shaved and finished. The same applies when roughing and finishing are performed on the outer surface. In FIG. 8, the compressed member 26b after processing is indicated by a broken line.

  For example, as shown in FIG. 9, the end 26b2 may be formed longer. Specifically, the movable scroll 26 further includes an extension member 26b4. The extension member 26b4 is a member extending from the outer peripheral end 26b2 of the compression member 26b and does not engage with the compression member 24b of the fixed scroll 24.

  According to the movable scroll 26 shown in FIG. 9, by providing the extension member 26b4, the strength and rigidity of the end 26b2 on the outer peripheral side of the compression member 26b are increased. Therefore, deformation at the time of processing of the compression member 26b can be prevented.

  After the compression member 26b is processed, the extension member 26b4 may be left as it is or may be scraped off. However, when the extension member 26b4 is left as it is, there are the following problems.

  That is, as shown in FIGS. 10 and 11, in the vicinity of the outer peripheral end of the compression member 26 b, a hole 41 b for sucking refrigerant into the end plate 24 a of the fixed scroll 24 (hereinafter referred to as “suction hole”). Is provided). For this reason, if the extension member 26b4 is covered with the suction hole 41b when the compression mechanism 15 is driven, a suction pressure loss may occur, and the compressor efficiency may be lowered.

  Therefore, the extension member 26b4 is designed not to cover the suction hole 41b during driving. Then, as shown in FIGS. 10 and 11, when the side surface of the extending member 26b4 exhibits an arc having a radius r, the design is as follows.

  That is, when the compression mechanism 15 is driven, the distance d3 between the extension member 26b4 and the suction hole 41b when the extension member 26b4 comes closest to the suction hole 41b is set to a radius r or more (FIG. 10).

  Then, the side surface of the extending member 26b4 having an arc shape is positioned away from the seal point SP of the fixed scroll 24 with the compression member 26b of the movable scroll 26 by a distance d4 that is equal to or greater than the radius r (FIG. 11).

  FIG. 12 shows the relationship between the ratio ΔS / d2 of the deflection amount ΔS of the compression member 26b at the seal point SP to the thickness d2, and the ratio L2 / d2 of the length L2 of the extension member 26b4 to the thickness d2 of the compression member 26b. FIG.

  The ratio ΔS / d2 is desirably 10 or less. This is because a gap can be provided between the compression member 24b of the fixed scroll 24 and the compression member 26b of the movable scroll 26 so as not to reduce the compressor efficiency. By providing such a gap, interference between the compression members 24b and 26b can be reduced, and noise and breakage can be reduced.

  Therefore, the length L2 of the extension member 26b4 is preferably such that the ratio L2 / d2 of the length L2 to the thickness d2 is 0.3 or more in relation to the thickness d2 of the compression member 26b. This is particularly desirable when the lower limit (13) is adopted for the ratio h2 / d2 in the above-described range of the ratio h2 / d2 (13 to 19) (FIG. 12). When the upper limit (19) is adopted for the ratio h2 / d2, the ratio L2 / d2 is preferably 2.6 or more (FIG. 12).

  The height of the extension member 26b4 may be smaller than the height h2 of the compression member 26b.

Third embodiment.
In the present embodiment, the relief holes provided in the fixed scroll will be described with respect to the compression mechanism 15 that employs a gray cast iron product (FC250) for the fixed scroll 24 and a semi-molten die cast product for the movable scroll 26, respectively.

  First, a conventional example of the relief hole will be described with reference to FIG. The relief hole 242 is provided in the fixed scroll 24. Specifically, it is provided on the end plate 24a at a position between the compression members 24b having a spiral shape. The relief hole 242 allows the compression chamber (space 40) to communicate with the space 45 (FIG. 1) described in an embodiment described later. The space 45 is located on the opposite side of the movable scroll 26 with respect to the end plate 24a of the fixed scroll 24 (FIG. 1).

  Conventionally, for example, a gray cast iron product (FC250) is used for both the fixed scroll 24 and the movable scroll 26, and the thickness d1 of the compression member 24b is substantially the same as the thickness d2 of the compression member 26b. When using gray cast iron products (FC250), it is necessary to increase the thicknesses d1 and d2 in order to increase the strength and rigidity of the compression members 24b and 26b.

  In order to prevent the compression chambers (spaces 40) on both sides of the compression member 26b of the movable scroll 26 from communicating with each other via the relief hole 242, the diameter of the relief hole 242 needs to be equal to or less than the thickness d2 of the compression member 26b. there were. However, since the thickness d2 is large, the diameter of the relief hole 242 can be increased, so that the refrigerant can easily pass through the relief hole 242.

  However, as shown in FIG. 14, when the thickness d2 of the compression member 26b belonging to the movable scroll 26, which is a semi-molten die cast product, is reduced, the sectional area of the relief hole 241 becomes that of the conventional relief hole 242 (FIG. 13). If the cross-sectional area remains the same, the two parts formed by partitioning the compression chamber (space 40) of the compression mechanism 15 with the compression member 24b communicate with each other, and the compressor efficiency decreases.

  Further, as shown in FIG. 15, if the sectional area of the relief hole 241 is simply reduced, it is difficult for the refrigerant to pass through the relief hole 241.

  FIG. 16 is a diagram conceptually showing a relief hole 241 that can be applied to the compression mechanism 15 described in the first and second embodiments. In FIG. 16, a cross section along the direction 91 is shown for the compression mechanism 15.

  In the relief hole 241, the diameter r1 at the entrance from the compression chamber (space 40) is equal to or less than the thickness d2 of the compression member 26b belonging to the movable scroll 26 (FIG. 16). The sectional area S2 on the space 45 side of the relief hole 241 is larger than the sectional area S1 near the entrance (FIG. 16).

  According to the relief hole 241, even if the thickness d2 of the compression member 26b belonging to the movable scroll 26 is small, one and the other of the spaces 40 partitioned by the compression member 26b do not communicate with each other via the relief hole 241. . Therefore, it can prevent that compressor efficiency falls.

  Moreover, since the sectional area S2 of the relief hole 241 on the space 45 side is large, the refrigerant that has entered the relief hole 241 tends to flow into the space 45. That is, the escape of compressed gas is improved.

  The relief hole 241 shown in FIG. 16 is a combination of two holes having different cross-sectional areas. For example, the relief hole 241 shown in FIGS. 17 to 21 may be used.

  FIG. 17 is a view showing a cross section of the compression mechanism 15 along the direction 91. In FIG. 17, the relief hole 241 has a cross-sectional area that increases from the entrance to the space 45. In this case, the same effect as the relief hole 241 shown in FIG. 16 can be obtained.

  18 is a view showing a cross section of the compression mechanism 15 at the position II-II shown in FIG. FIG. 19 is a view showing a cross section along the direction 91 of the compression mechanism 15 shown in FIG. 18 and 19, a relief hole 241 having substantially the same size as the conventional relief hole 242 (FIG. 13) is employed. However, a part of the relief hole 241 is closed by the compression member 24b belonging to the fixed scroll 24 (FIG. 18). In other words, the relief hole 241 when viewed from the movable scroll 26 side partially overlaps the compression member 24 b of the fixed scroll 24.

  According to the relief hole 241, the sectional area S1 at the entrance of the relief hole 241 is small, and the sectional area S2 on the space 45 side is large (FIG. 19). Therefore, the same effect as the relief hole 241 shown in FIG. 16 can be obtained.

  20 and 21, a plurality of relief holes 241 having a diameter r1 smaller than the thickness d2 of the compression member 26b are provided in the end plate 24a. For example, an elliptical relief hole may be provided in the end plate 24a.

  In FIG. 21, the discharge hole 41 employed in the embodiment of the present invention is indicated by a solid line, and the conventional discharge hole 41a is indicated by a broken line. The discharge hole 41 has a smaller cross-sectional area than the conventional discharge hole 41a. This is a design change caused by reducing the thickness d2 of the compression member 26b.

  When the cross-sectional area of the discharge hole 41 is small, the amount of refrigerant discharged from the hole 41 is small. However, since a plurality of relief holes 241 are provided in FIG. 21, a decrease in the discharge amount can be prevented by using these as auxiliary holes for discharging the compressed refrigerant.

  Specifically, the space in which the refrigerant is discharged through the relief hole 241 is made the same as the space in which the refrigerant is discharged through the discharge hole 41. In the present embodiment, all of the refrigerant discharged from the relief hole 241 and the discharge hole 41 is guided to the space 45 (FIGS. 1 and 19). Thereby, the refrigerant discharged from the relief hole 241 can be used as the refrigerant compressed by the compression mechanism 15.

<Structure of scroll compressor>
The structure of the scroll compressor 1 will be described in more detail with reference to FIG. In addition to the case 11 and the compression mechanism 15, the compressor 1 includes an Oldham ring 2, a fixing member 12, a motor 16, a crankshaft 17, a suction pipe 19, a discharge pipe 20, and a bearing 60.

  The case 11 is cylindrical and extends along the direction 91. The Oldham ring 2, the fixing member 12, the motor 16, the crankshaft 17, and the bearing 60 are housed in the case 11.

  The motor 16 has a stator 51 and a rotor 52. The stator 51 is annular and is fixed to the inner wall 11 a of the case 11. The rotor 52 is provided on the inner peripheral side of the stator 51 and faces the stator 51 through an air gap.

  The crankshaft 17 extends along the direction 91 and includes a main shaft 17a and an eccentric portion 17b. The main shaft 17 a is a portion that rotates about the rotation shaft 90 and is connected to the rotor 52. The eccentric portion 17b is a portion arranged so as to be offset from the rotating shaft 90, and is connected to the upper side of the main shaft 17a. The lower end of the crankshaft 17 is slidably supported by a bearing 60.

  The fixing member 12 is specifically a housing in FIG. 1 and is fitted to the inner wall 11a of the case 11 without a gap. For example, the fixing member 12 is fitted to the inner wall 11a by a method such as press fitting or shrink fitting. The fixing member 12 may be fitted to the inner wall 11a via a seal.

  Since the fixing member 12 is fitted to the inner wall 11a without a gap, the space 28 positioned on the lower side of the fixing member 12 and the space 29 positioned on the upper side are partitioned without a gap. Therefore, the fixing member 12 can maintain the pressure difference generated between the space 28 and the space 29. The pressure in the space 28 is high and the pressure in the space 29 is low.

  The fixing member 12 is provided with a recess 31 that opens upward in the vicinity of the rotary shaft 90. The eccentric portion 17 b of the crankshaft 17 is accommodated in the recess 31. Further, the fixing member 12 has a bearing 32 and a hole 33. With the main shaft 17a of the crankshaft 17 passing through the hole 33, the bearing 32 supports the main shaft 17a.

  The upper surface of the fixed scroll 24 has a concave shape. A space 45 surrounded by a concave portion 42 of the surface is closed with a lid 44. The lid 44 partitions the two spaces having different pressures, that is, the space 45 and the space 29 above the space 45.

  The movable scroll 26 further includes a bearing 26c. The bearing 26c is connected to the lower side of the end plate 26a and slidably supports the eccentric portion 17b of the crankshaft 17.

<Flow of refrigerant>
The flow of the refrigerant in the scroll compressor 1 will be described with reference to FIG. In FIG. 1, the flow of the refrigerant is indicated by arrows. The refrigerant is sucked from the suction pipe 19 and guided to the compression chamber (space 40) of the compression mechanism 15. The refrigerant compressed in the compression chamber (space 40) is discharged into the space 45 from a discharge hole 41 provided near the center of the fixed scroll 24. Therefore, the pressure in the space 45 is high. On the other hand, the pressure in the space 29 partitioned from the space 45 by the lid 44 remains small.

  The refrigerant in the space 45 flows through the hole 46 provided in the fixed scroll 26 and the hole 48 provided in the fixed member 12 in this order to the space 28 below the fixed member 12. In the space 28, the refrigerant is guided to the gap 55 by the guide plate 58. Here, the gap 55 is provided between a part of the side surface of the stator 51 and the case 11.

  Then, the refrigerant that has flowed to the lower side of the motor 16 through the gap 55 flows to the discharge pipe 20 through the air gap or the gap 56 of the motor 16. Here, the gap 56 is provided between the case 11 and another part of the side surface of the stator 51.

It is sectional drawing which shows notionally the scroll compressor concerning embodiment of this invention. It is a figure which shows the cross section of the compression mechanism 15 in the position II-II shown by FIG. It is a figure which shows each value of surface pressure which is seizure-proof, a graphite area ratio, and hardness. It is the figure which showed the relationship between the graphite area ratio and the surface pressure with seizure resistance in a graph. It is a figure which shows the compression mechanism 15 which exhibits the shape different from the shape shown by FIG. It is a figure which shows notionally the compression member with the large thickness of the edge part of an outer peripheral side. It is a figure which shows notionally the compression member with the large thickness of the edge part of an outer peripheral side. It is a figure which shows notionally the compression member with the large thickness of the edge part of an outer peripheral side. It is a figure which shows notionally the movable scroll which provided the extending member. It is a figure which shows notionally the movable scroll which provided the extending member. It is a figure which shows notionally the movable scroll which provided the extending member. It is a figure which shows the relationship between ratio with respect to thickness d2 of deflection amount (DELTA) S, and ratio with respect to thickness d2 of length L2. It is a figure which shows the conventional example of a relief hole. It is a figure which shows the aspect which made thickness of the compression member small in a prior art example. It is a figure which shows the aspect which made the relief hole thin in the prior art example. 3 is a diagram conceptually showing a relief hole 241 applicable to the compression mechanism 15. FIG. 3 is a diagram conceptually showing a relief hole 241 applicable to the compression mechanism 15. FIG. 3 is a diagram conceptually showing a relief hole 241 applicable to the compression mechanism 15. FIG. It is a figure which shows the cross section which follows the direction 91 about a relief hole. It is a figure which shows the compression mechanism which provided the relief hole 241 in multiple numbers in the end plate 24a. It is a figure which shows the compression mechanism which provided the relief hole 241 in multiple numbers in the end plate 24a.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Scroll compressor 15 Compression mechanism 24 Fixed scroll 26 Movable scroll 24a, 26a End plate (fixed member)
24b, 26b Compression member 26b2 End 26b4 Extension member 40, 45 Space 241 Relief hole d1, d2 Thickness d1 / d2, d2 / d1 ratio

Claims (14)

A compression mechanism (15) used in the scroll compressor (1),
A fixed scroll (24) having a first compression member (24b) extending in a spiral shape and a first fixing member (24a) for fixing the first compression member;
A movable scroll (26) having a second compression member (26b) extending in a spiral shape meshing with the first compression member, and a second fixing member (26a) for fixing the second compression member;
Either one of the fixed scroll and the movable scroll is a molded product obtained by molding cast iron by a semi-molten die casting method, and the other is a gray cast iron product,
A compression mechanism in which a ratio (h1 / d1, h2 / d2) of a height (h1, h2) to a thickness (d1, d2) of the compression member belonging to the molded product is 13 or more and 19 or less.   The compression mechanism according to claim 1, wherein the sum of the area ratio of graphite on the surface of the molded product and the area ratio of graphite on the surface of the gray cast iron product is 10% or more and 20% or less.   The compression mechanism according to claim 2, wherein the area ratio of the graphite of the molded product is 2% or more and 6% or less. The compression mechanism according to any one of claims 1 to 3, wherein the tensile strength of the gray cast iron product is 250 N / mm ² or more and less than 300 N / mm ² .   The compression mechanism according to any one of claims 1 to 4, wherein the fixed scroll (24) is the gray cast iron product and the movable scroll (26) is the molded product.   The compression mechanism according to claim 5, wherein the movable scroll (26) is arranged to be pressed against the fixed scroll (24). The first fixed member of the fixed scroll includes a first space (40) extending in a spiral shape formed by the first compression member of the fixed scroll, and a second space opposite to the movable scroll. A hole (241) communicating with the space (45) is provided;
The compression mechanism according to claim 5 or 6, wherein the second compression member (26b) of the movable scroll can block an entrance of the hole on the first space side.   The compression mechanism according to claim 7, wherein a part of the hole when viewed from the movable scroll side overlaps the first compression member (24b) of the fixed scroll (24).   The movable scroll has a member extending from an outer peripheral end (26b2) of the second compression member (26b) belonging to the movable scroll, and an extension member (26b4) that does not engage with the first compression member of the fixed scroll. The compression mechanism according to any one of claims 5 to 8, further comprising:   Of the fixed scroll and the movable scroll, the thickness (d1; d2) of the compression member (24b; 26b) belonging to the molded product, the thickness (d2;) of the compression member (26b; 24b) belonging to the gray cast iron product. The ratio (d1 / d2; d2 / d1) to d1) is equal to a value calculated based on a ratio (α) of Young's modulus of the molded product to Young's modulus of the gray cast iron product. Item 10. The compression mechanism according to any one of Items 9.   The compression mechanism according to claim 10, wherein the ratio (d1 / d2; d2 / d1) of the thickness is equal to or less than a reciprocal of the ratio (α) of the Young's modulus.   The compression mechanism according to claim 10 or 11, wherein the Young's modulus of the molded product is 175 GPa or more and 190 GPa or less.   A scroll compressor comprising the compression mechanism (15) according to any one of claims 1 to 12.   The scroll compressor of Claim 13 which compresses the refrigerant | coolant which contains a carbon dioxide as a main component.

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