JP2013024071A - Rotary fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress fluid leakage generated from a corner structure of an end plate and a tooth, and to suppress increase in part costs.SOLUTION: In a rotary compressor, a cylinder member (31) and a piston member (32) perform eccentric rotation relative to each other. On fronts of an end plate (32a) of the piston member (32) and an end plate (31a) of the cylinder member (31), and on at least a part of the fronts where the piston member (32) and the cylinder member (31) are in sliding contact with each other, a seat member (60) of which surface becomes the same surface with the end face (30b) of a cylinder chamber (30a), and the opposing member (31, 32) slides and contacts the surface is provided. The seat member (60) is provided at a divided part (3b) of the tooth (32b) on the front of the end plate (32a) of the piston member (32).

Description

    The present invention relates to a rotary fluid machine, and particularly relates to a corner portion structure of an end plate and a tooth portion.

    Conventionally, a rotary fluid machine includes a rotary compressor in which an annular piston of a piston member is arranged in an annular cylinder chamber of a cylinder member and a plurality of compression chambers are formed in a compression mechanism (for example, Patent Document 1, 2). In the compressor of Patent Document 1, two compression chambers are formed inside and outside the annular piston. Moreover, the compressor of patent document 2 has three compression chambers formed.

JP 2007-113493 A JP 2006-307762 A

    However, in the conventional rotary compressor, the cylinder member and the piston member are formed integrally with the end plate and the tooth portion, so that a circular arc surface that is a corner R is formed at the corner portion between the end plate and the tooth portion, There was a problem of fluid leakage.

    That is, as shown in FIG. 10, in the cylinder member (a) and the piston member (b), tooth portions (d, f) are formed to project from the end plate (c, e). The cylinder member (a) is formed of a relatively soft casting, while the piston member (b) is formed of a relatively difficult steel material. Therefore, although the corners of the end plate (c) and the tooth portion (d) in the cylinder member (a) are formed at 45 ° corners, the end plate (e) and the teeth in the piston member (b) are formed. A circular arc surface (g) is formed at the corner with the part (f).

    Therefore, the tooth portion (d) of the cylinder member (a) is chamfered at 45 ° at the tip corner portion to form a cut surface (h).

    However, when the cut surface (h) is formed, there is a problem that fluid leaks from the high pressure compression chamber to the low pressure compression chamber.

    Further, when the cut surface (h) is short in length, for example, as shown in FIG. 11, when the cut surface (h) is not formed, the tip of the tooth portion (d) of the cylinder member (a) is Riding on the circular arc surface (g), between the tooth part (d) of the cylinder member (a) and the end plate (e) of the piston member (b), and the tooth part (h) of the piston member (b) and the above There was a problem that a gap was generated between the end plate (c) of the cylinder member (a) and fluid leaked from the high pressure compression chamber to the low pressure compression chamber.

    In particular, when the fluid is carbon dioxide (CO2), there is a problem that the differential pressure between the high pressure and the low pressure is large, the influence of leakage becomes large, and the compressor efficiency is lowered. Furthermore, in the case of the rotary compressor, the high pressure compression chamber and the low pressure compression chamber are adjacent to each other.

    On the other hand, if the arcuate surface (g) of the piston member (b) is not formed, there is a problem that the life of the machining tool is shortened and the part cost is increased.

    The present invention has been made in view of such a point, and an object of the present invention is to suppress fluid leakage caused by the corner portion structure of the end plate and the tooth portion and to suppress an increase in component cost.

    1st invention has the end plate (31a) and the tooth | gear part (31b, 31c) protrudingly formed from the front surface of this end plate (31a), and at least 1 cyclic | annular cylinder chamber (30a) was formed. A piston member (31) having a cylinder member (31), an end plate (32a), and a toothed portion (32b) of an annular piston that protrudes from the front surface of the end plate (32a) and is disposed in the cylinder chamber (30a). 32), the cylinder member (31) and the piston member (32) are arranged with the front surfaces of the end plates (31a, 32a) facing each other, and the cylinder member (31) and the piston member (32) This is a rotary fluid machine in which the cylinder member (31) and the piston member (32) rotate relatively eccentrically with each other as a counterpart member (32, 31).

    The cylinder member (31) penetrates the dividing portion (3b) formed in the tooth portion (32b) so as to divide the tooth portion (32b) of the piston member (32) from the inside to the outside. And a blade (33) that divides the cylinder chamber (30a) into a high-pressure side and a low-pressure side, and the blade (33) that can be swung freely by the piston member (32). And a supporting member (34) for supporting.

    Further, at least one of the front surface of the end plate (32a) of the piston member (32) and the end plate (31a) of the cylinder member (31) and the front surface where the piston member (32) and the cylinder member (31) are in sliding contact with each other. The part is provided with a sheet member (60) whose surface is flush with the end face (30b) of the cylinder chamber (30a) and whose counterpart member (31, 32) is in sliding contact with the surface.

    In the said 1st invention, since the sheet | seat member (60) is provided in the end plate (32a, 31a), the circular arc which arises in the corner | angular part of this end plate (32a, 31a) and a tooth | gear part (32b, 31b, 31c) The surface is covered, and the corners of the sheet member (60) and the tooth portions (32b, 31b, 31c) are 45 ° corners. As a result, fluid leakage due to the arc surface is suppressed.

    According to a second aspect of the present invention, in the first aspect, the seat member (60) is provided on the divided portion (3b) of the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). It is a fluid machine.

    In the second aspect of the invention, since the entire end surface of the support member (34) is in contact with the seat member (60) at the dividing portion (3b), the dividing between the outer working chamber and the inner working chamber of the cylinder chamber (30a) is performed. Fluid leakage from the part (3b) is suppressed.

    A third invention is the rotary fluid according to the first or second invention, wherein the sheet member (60) is provided outside the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). It is a machine.

    In the third aspect of the invention, since the entire end surface of the tooth portion (31b) of the cylinder member (31) is in contact with the seat member (60), fluid leakage between the high pressure side and the low pressure side of the cylinder chamber (30a) is suppressed. Is done.

    According to a fourth invention, in any one of the first to third inventions, the sheet member (60) is provided inside the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). Rotary fluid machine.

    In the fourth aspect of the invention, since the entire end surface of the tooth portion (31c) of the cylinder member (31) is in contact with the seat member (60), fluid leakage between the high pressure side and the low pressure side of the cylinder chamber (30a) is suppressed. Is done.

    In a fifth aspect based on the first aspect, the sheet member (60) is provided on the dividing portion (3b) of the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). A rotary type in which the member (63), the outer sheet member (61) provided outside the tooth part (32b) and the inner sheet member (62) provided inside the tooth part (32b) are integrally formed. It is a fluid machine.

    In the fifth aspect of the invention, the entire end surface of the support member (34) and the entire end surface of the teeth (31b, 31c) of the cylinder member (31) are in contact with the seat member (60). Fluid leakage at the dividing portion (3b) between the chamber and the inner working chamber and fluid leakage between the high pressure side and the low pressure side of the cylinder chamber (30a) are suppressed.

    A sixth invention is the rotary fluid machine according to any one of the first to fifth inventions, wherein the sheet member (60) is provided on the front surface of the end plate (31a) of the cylinder member (31).

    In the sixth aspect of the invention, since the entire end surface of the tooth portion (32b) of the piston member (32) is in contact with the seat member (60), fluid leakage between the high pressure side and the low pressure side of the cylinder chamber (30a) is suppressed. Is done.

    A seventh aspect of the invention is the rotary fluid according to any one of the first to sixth aspects of the invention, wherein the back corner portion of the sheet member (60) is formed on the cut surface (65) cut in a straight line. It is a machine.

    In the seventh aspect of the invention, the arc member and the sheet member (60) generated at the corners of the end plate (32a, 31a) and the teeth (32b, 31b, 31c) by the cut surface (65) of the sheet member (60). Interference with is avoided.

    According to the present invention, since the sheet member (60) is provided on at least a part of the front surface of the end plate (32a) of the piston member (32) and the front surface of the end plate (31a) of the cylinder member (31), It is possible to suppress refrigerant leakage caused by the circular arc surface (70) formed at the corners of the teeth 32a, 31a) and the teeth (32b, 31b, 31c).

    That is, for example, conventionally, when 45 ° chamfering is performed on the tip corner portion of the tooth portion (d) of the cylinder member (a) to form the cut surface (h), refrigerant leakage from the cut surface (h) occurs. It was happening. However, in the present invention, since the sheet member (60) is provided, it is not necessary to form a cut surface on the tooth portions (31b, 31c) of the cylinder member (31), so that refrigerant leakage can be suppressed. .

    For example, conventionally, the tip of the tooth part (d) of the cylinder member (a) rides on the arc surface (g), and the tooth part (d) of the cylinder member (a) and the end plate (e) of the piston member (b). And a gap is formed between the tooth portion (h) of the piston member (b) and the end plate (c) of the cylinder member (a), and fluid leaks from the high pressure compression chamber to the low pressure compression chamber. It was. However, in the present invention, since the sheet member (60) is provided, the tooth portions (31b, 31c) are always in contact with the sheet member (60), so that it is possible to suppress refrigerant leakage.

    In particular, when the refrigerant is carbon dioxide (CO2), the differential pressure between the high pressure and the low pressure is large, and the influence of leakage is increased, but since this leakage can be suppressed, a decrease in compressor efficiency can be suppressed. .

    In the case of the rotary compressor, since the high pressure chamber and the low pressure chamber are adjacent to each other, the influence of the refrigerant leakage is increased, but this leakage can be suppressed.

    Moreover, since formation of the said circular arc surface (70) can be accept | permitted, the lifetime of a processing tool becomes long and the raise of component cost can be suppressed.

    According to the second aspect of the invention, the seat member (60) is provided on the dividing portion (3b) of the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). Refrigerant leakage between the working chamber and the inner working chamber can be reliably suppressed.

    Further, according to the fifth invention, since the dividing sheet member (63), the outer sheet member (61), and the inner sheet member (62) are integrally formed, the refrigerant leakage is more reliably suppressed. In addition, the structure can be simplified.

    According to the sixth invention, when the cylinder member (31) is provided with the cylinder seat member (64), when the cylinder member (31) is formed of a relatively difficult steel material, fluid leakage is reliably suppressed. can do.

    According to the seventh invention, since the cut surface (65) is formed on the sheet member (60), the corner portions of the end plate (32a, 31a) and the tooth portions (32b, 31b, 31c) are formed. Interference between the generated arc surface and the sheet member (60) can be avoided.

FIG. 1 is a longitudinal sectional view of a rotary compressor. FIG. 2 is a cross-sectional view of the first compression mechanism (second compression mechanism). FIG. 3 is an enlarged view of the compressor section of FIG. FIG. 4 is a perspective view of the dividing sheet member and the piston member. FIG. 5 is a perspective view of the outer sheet member and the piston member. FIG. 6 is a perspective view of the inner sheet member and the piston member. FIG. 7 is a perspective view of the cylinder seat member and the cylinder member. FIG. 8 is a perspective view of the members when the outer sheet member, the dividing sheet member, and the inner sheet member are made close together. FIG. 9 is a partially enlarged sectional view of the sheet member. FIG. 10 is an enlarged cross-sectional view of a conventional cylinder member and piston member. FIG. 11 is an enlarged cross-sectional view of another conventional cylinder member and piston member.

    Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

    As shown in FIG. 1, the rotary compressor (10) of the present embodiment is a rotary fluid machine, and is provided in a refrigerant circuit of an air conditioner, for example, and compresses refrigerant sucked from an evaporator. It is discharged to the condenser.

    The rotary compressor (10) includes a vertically long sealed container-like casing (11). The casing (11) includes a body portion (12) formed in a vertically long cylindrical shape, and a pair of end plates (13, 13) provided at both ends of the body portion (12). The casing (11) includes a motor (20), a low-stage first compression mechanism (30), and a high-stage second compression mechanism (40), and compresses the refrigerant in two stages. Part (50).

    The body (12) of the casing (11) includes a first suction pipe (14) and a first discharge pipe (15) connected to the first compression mechanism (30) on the lower stage side, and a higher stage side. A second suction pipe (16) connected to the second compression mechanism (40) is provided through the body (12). Although not shown, the first discharge pipe (15) and the second suction pipe (16) are connected to the outside of the casing (11).

    In the rotary compressor (10), the refrigerant compressed in the second compression mechanism (40) on the higher stage side is discharged into the internal space (S10) of the casing (11), and is passed through the second discharge pipe (17). Thus, it is configured to be discharged to the outside of the casing (11), and is configured as a so-called high pressure dome type compressor.

    A drive shaft (23) extending in parallel with the body (12) is provided inside the casing (11). The electric motor (20) and the compressor section (50) are connected via the drive shaft (23). An oil sump (18) for storing lubricating oil supplied to each sliding part of the compressor part (50) is formed at the bottom of the casing (11).

    The drive shaft (23) includes a main shaft portion (24), an upper eccentric portion (25), and a lower eccentric portion (26). Both the eccentric parts (25, 26) are formed in a columnar shape having a diameter larger than that of the main shaft part (24), and the respective shaft centers are eccentric from the axis of the main shaft part (24). Further, the upper eccentric part (25) and the lower eccentric part (26) are formed so that their phases are shifted from each other by 180 ° around the axis of the main shaft part (24).

    An oil supply pump (28) immersed in an oil reservoir (18) is provided at the lower end of the drive shaft (23). In addition, an oil supply passage (not shown) is formed in the drive shaft (23), which extends in the axial direction and through which the lubricating oil sucked up by the oil supply pump (28) flows.

    The electric motor (20) includes a stator (21) and a rotor (22). The stator (21) is fixed to the body (12) of the casing (11). On the other hand, the rotor (22) is arranged inside the stator (21) and is connected to the main shaft portion (24) of the drive shaft (23).

    The compressor section (50) is disposed below the electric motor (20), and is provided between the first compression mechanism (30), the second compression mechanism (40), and both compression mechanisms (30, 40). And a middle plate (51).

    As shown in FIGS. 2 to 7, the first compression mechanism (30) includes a first cylinder member (31) forming one annular first cylinder chamber (30a), and the first cylinder chamber (30a). 1st piston member (32) which has a tooth | gear part (32b) located in this, and divides this 1st cylinder chamber (30a) into the outer side compression chamber (S11) which is a working chamber, and an inner side compression chamber (S12) And. The first cylinder member (31) includes a first blade that partitions the outer compression chamber (S11) and the inner compression chamber (S12) into a high pressure chamber (S11H, S12H) and a low pressure chamber (S11L, S12L). 33). The first cylinder member (31) and the first piston member (32) are mating members and are configured to relatively eccentrically rotate. In the present embodiment, the first cylinder member (31) constitutes a fixed member of the first compression mechanism (30), and the first piston member (32) constitutes a movable member of the first compression mechanism (30). doing.

    The first cylinder member (31) includes a flat end plate (31a) having a bearing portion formed in the center, and a cylindrical shape formed so as to protrude upward from the front surface (upper surface) of the end plate (31a). An outer tooth portion (31b) and an inner tooth portion (31c) are provided. As for the said 1st cylinder member (31), the end plate (31a) and the outer side tooth part (31b) are being fixed to the inner surface of the trunk | drum (12) of a casing (11). The main shaft portion (24) of the drive shaft (23) is inserted through the bearing portion of the end plate (31a).

    The end plate (31a) of the first cylinder member (31) is formed with a first suction port (14a) extending radially inward from the outer peripheral surface. One end of the first suction port (14a) is inserted into the outer compression chamber (S11) and the inner compression chamber (S12), and the first suction pipe (14) is connected to the other end.

    Further, the end plate (31a) of the first cylinder member (31) is formed with a first discharge port (15a) extending radially inward from the outer peripheral surface. One end of the first discharge port (15a) communicates with the outer compression chamber (S11) and the inner compression chamber (S12), and the other end is connected to the first discharge pipe (15). Specifically, the discharge ports (35, 36) of the outer compression chamber (S11) and the inner compression chamber (S12) are opened in the first discharge port (15a), and both the discharge ports (35, 36) are opened. Discharge valves (37, 38) are provided.

    The inner peripheral surface of the outer tooth portion (31b) and the outer peripheral surface of the inner tooth portion (31c) are formed on cylindrical surfaces disposed on the same center. An outer compression chamber (S11) is formed between the outer peripheral surface of the tooth portion (32b) of the first piston member (32) and the inner peripheral surface of the outer tooth portion (31b) of the first cylinder member (31). An inner compression chamber (S12) between the inner peripheral surface of the tooth portion (32b) of the first piston member (32) and the outer peripheral surface of the inner tooth portion (31c) of the first cylinder member (31). Is formed.

    The first piston member (32) includes a plate-shaped end plate (32a), a tooth portion (32b) of an annular piston formed by discharging downward from the front surface (lower surface) of the end plate (32a), and the tooth portion ( 32b) and a cylindrical bearing portion (32c) formed on the inner side. As shown in FIG. 4 etc., the said tooth | gear part (32b) is formed in the C-shape by which a part of annular ring was parted, and the part part (3b) is formed. A lower eccentric portion (26) of the drive shaft (23) is slidably fitted into the bearing portion (32c). A space (3a) is formed between the bearing portion (32c) and the inner tooth portion (31c), but the refrigerant is not compressed in this space (3a).

    The first blade (33) extends from the inner peripheral surface of the outer tooth portion (31b) to the outer peripheral surface of the inner tooth portion (31c) in the radial direction of the first cylinder chamber (30a). Then, the first blade (33) is inserted through the dividing portion (3b) of the tooth portion (32b) of the first piston member (32) to pass the first cylinder chamber (30a) into the high pressure chamber (S11H, S12H). And a low pressure chamber (S11L, S12L). In the present embodiment, the first blade (33) is integrally formed with the outer tooth portion (31b) and the inner tooth portion (31c), but is formed as a separate member from both tooth portions (31b, 31c). And you may fix to these.

    The first cylinder member (31) is provided at the divided portion (3b) of the tooth portion (32b), and supports a first piston member (32) and a first blade (33) in a swingable manner. (34). The first bush (34) constitutes a support member, and is a discharge side located on the high pressure chamber (S11H, S12H) side with respect to the first blade (33), and a low pressure chamber with respect to the first blade (33). It is provided on the suction side located on the (S11L, S12L) side. The first bush (34) has a substantially semicircular cross section. The first blade (33) is sandwiched between the opposed surfaces of the first bushes (34, 34) so as to freely advance and retract. The first bush (34) is formed to be swingable with respect to the first piston member (32) in a state where the first blade (33) is sandwiched. The first bushes (34, 34) may be partially connected and integrally formed.

    In the first compression mechanism (30), the first piston member (32) performs an eccentric rotational motion with respect to the first cylinder member (31). In the eccentric rotational movement, the outer peripheral surface of the tooth portion (32b) of the first piston member (32) and the inner peripheral surface of the outer tooth portion (31b) of the first cylinder member (31) substantially slide at one point. The inner peripheral surface of the tooth portion (32b) of the first piston member (32) and the outer peripheral surface of the inner tooth portion (31c) of the first cylinder member (31) Is configured so as to be in sliding contact with one point substantially.

    The second compression mechanism (40) is configured by the same mechanical elements as the first compression mechanism (30). The second compression mechanism (40) is provided in a state where the first compression mechanism (30) is reversed with the middle plate (51) interposed therebetween. In FIG. 2 and the like, reference numerals related to the components of the second compression mechanism (40) are shown in parentheses. The middle plate (51) is fixed to the body (12) of the casing (11).

    Therefore, the second compression mechanism (40) is substantially the same as the first compression mechanism (30), and therefore the outline will be described using the first compression mechanism (30).

    Similar to the first compression mechanism (30), the second compression mechanism (40) includes a second cylinder member (41) that forms a second cylinder chamber (40a), and an outer side of the second cylinder chamber (40a). A second piston member (42) having a tooth portion (42b) partitioned into a compression chamber (S21) and an inner compression chamber (S22) is provided. The second cylinder member (41) includes a second blade (43) that partitions the second cylinder chamber (40a) into a high pressure chamber (S21H, S22H) and a low pressure chamber (S21L, S22L). The second cylinder member (41) and the second piston member (42) serve as counterpart members and are configured to relatively eccentrically rotate.

    The second cylinder member (41) includes a flat end plate (41a), an outer tooth portion (41b) and an inner tooth portion (41c), and is fixed to the casing (11).

    A second suction port (16a) is formed on the end plate (41a) of the second cylinder member (41). One end of the second suction port (16a) communicates with the outer compression chamber (S21) and the inner compression chamber (S22), and the other suction pipe (16) is connected to the other end.

    A second discharge port (17a) is formed in the end plate (41a) of the second cylinder member (41). One end of the second discharge port (17a) communicates with the outer compression chamber (S21) and the inner compression chamber (S22), and the other end differs from the first cylinder member (31) in the interior of the casing (11). Open to space (S10). The second discharge port (17a) has discharge ports (45, 46) of the outer compression chamber (S21) and the inner compression chamber (S22), and both discharge ports (45, 46) have a discharge valve (47). , 48).

    An outer compression chamber (S21) is provided between the outer peripheral surface of the tooth portion (42b) of the second piston member (42) and the inner peripheral surface of the outer tooth portion (41b) of the second cylinder member (41). Between the inner peripheral surface of the tooth portion (42b) of the second piston member (42) and the outer peripheral surface of the inner tooth portion (41c) of the second cylinder member (41). S22) is formed.

    The second piston member (42) includes an end plate (42a), a tooth portion (42b), and a bearing portion (42c). The said tooth | gear part (42b) is formed in the C-shape by which a part of annular ring was parted, and the part part (4b) is formed. The upper eccentric portion (25) of the drive shaft (23) is slidably fitted into the bearing portion (42c). A space (4a) is formed between the bearing portion (42c) and the inner tooth portion (41c), but the refrigerant is not compressed in this space (4a).

    The second blade (43) penetrates the dividing portion (4b) of the second piston member (42) and extends from the inner peripheral surface of the outer tooth portion (41b) to the outer peripheral surface of the inner tooth portion (41c). ing. The second blade (43) is integrally formed with the outer tooth portion (41b) and the inner tooth portion (41c), but is formed as a separate member from both tooth portions (41b, 41c) and fixed thereto. It may be.

    The second cylinder member (41) includes a second bush (44) for swingably supporting the second piston member (42) and the second blade (43). The second bush (44) constitutes a support member and is provided on the discharge side and the suction side of the second blade (43). The second bush (44) has a substantially semicircular cross section. Two said 2nd bushes (44) may be connected in part, and may be formed integrally.

    In the second compression mechanism (40), the second piston member (42) performs an eccentric rotational motion with respect to the second cylinder member (41). In the eccentric rotational movement, the outer peripheral surface of the tooth portion (42b) of the second piston member (42) and the inner peripheral surface of the outer tooth portion (41b) of the second cylinder member (41) are substantially slid at one point. The inner peripheral surface of the tooth part (42b) of the second piston member (42) and the outer peripheral surface of the inner tooth part (41c) of the second cylinder member (41) Is configured so as to be in sliding contact with one point substantially.

    As shown in FIGS. 4 to 7, the first compression mechanism (30) is characterized by the end plate (32 a) of the first piston member (32) and the end plate of the first cylinder member (31). 31a) is provided with a seat member (60) on the front surface, and the second compression mechanism (40) is similar to the first compression mechanism (30) in that the end plate (42a) of the second piston member (42) A sheet member (60) is provided in front of the end plate (41a) of the two cylinder member (41). Therefore, hereinafter, the first piston member (32) and the second piston member (32) are simply referred to as piston members (32, 42), and the first cylinder member (31) and the second cylinder member (31) are It is simply called a cylinder member (31, 41).

    The seat member (60) is provided on the outer seat member (61), the inner seat member (62), the dividing seat member (63), and the cylinder member (31, 41) provided on the piston member (32, 42). And at least one of the cylinder seat member (64).

    That is, the aspect in which the sheet member (60) is provided in each compression mechanism (30, 40) is as follows.

    (1) The compression mechanism (30, 40) includes only a dividing sheet member (63).

    (2) The compression mechanism (30, 40) includes only the outer sheet member (61).

    (3) The compression mechanism (30, 40) includes only the inner sheet member (62).

    (4) The compression mechanism (30, 40) includes only the cylinder seat member (64).

    (5) The compression mechanism (30, 40) includes a sheet member (60) that is a combination of the above (1) to (4). Therefore, the outer sheet member (61), the inner sheet member (62), the dividing sheet member (63), and the cylinder sheet member (64) may all be provided.

    Therefore, the dividing sheet member (63), the outer sheet member (61), the inner sheet member (62), and the cylinder sheet member (64) will be described in order.

    As shown in FIG. 4, the dividing sheet member (63) is provided at the dividing portion (3b, 4b) of the tooth portion (32b, 42b) of the piston member (32, 42). The dividing sheet member (63) is formed in a disc shape corresponding to the blade and the bush, and the dividing portion (3b, 4b) of the tooth portion (32b, 42b) in the end plate (32a) of the piston member (32, 42) It is inserted in. The end plate (32a, 42a) of the piston member (32, 42) has a bottom surface (front surface of the end plate (32a, 42a)) when only the dividing sheet member (63) is provided. Is formed deeper than the front face of the other end plate (32a, 42a) by the thickness of the dividing sheet member (63). Therefore, the surface of the dividing sheet member (63) is flush with the axial end surfaces (30b, 40b) of the cylinder chamber (30a, 40a), that is, the upper surface or the lower surface of the cylinder chamber (30a, 40a). In addition, the blades (33, 43) and bushes (34, 44) of the cylinder members (31, 41), which are counterpart members, are formed so as to be in sliding contact with each other.

    As shown in FIG. 5, the outer sheet member (61) is provided outside the tooth portions (32b, 42b) of the piston member (32, 42). The outer sheet member (61) is formed in a donut plate shape corresponding to the outer compression chamber (S11, S21), and the teeth (32b, 42b) of the end plate (32a, 42a) of the piston member (32, 42). It is fitted on the outside. When the end plate (32a, 42a) of the piston member (32, 42) is provided with only the outer sheet member (61), the outer front surface of the tooth portion (32b, 42b) is the other end plate (32a, 42a). Is formed deeper than the front surface by the thickness of the outer sheet member (61). Therefore, the outer sheet member (61) is formed so that the surface thereof is flush with the axial end faces (30b, 40b) of the cylinder chambers (30a, 40a), and the cylinder member (31 , 41) are formed so that the outer teeth (31b, 41b) are in sliding contact.

    The said inner sheet | seat member (62) is provided inside the tooth | gear part (32b, 42b) of a piston member (32, 42), as shown in FIG. The inner sheet member (62) is formed in a donut plate shape corresponding to the inner compression chamber (S12, S22), and the tooth portion (32b, 42b) in the end plate (32a, 42a) of the piston member (32, 42). It is fitted between the bearing portions (32c, 42c). When the end plate (32a, 42a) of the piston member (32, 42) is provided with only the inner sheet member (62), the front surface inside the tooth portion (32b, 42b) is the other end plate (32a, 42a). The inner sheet member (62) is formed deeper than the front surface. Further, the inner sheet member (62) is formed so that the surface thereof is flush with the axial end faces (30b, 40b) of the cylinder chambers (30a, 40a), and a cylinder member (31 , 41) is formed so that the inner teeth (31c, 41c) are in sliding contact.

    As shown in FIG. 7, the cylinder seat member (64) is provided between the outer teeth (31b, 41b) and the inner teeth (31c, 41c) of the cylinder member (31, 41). . The cylinder seat member (64) is formed in a donut plate shape extending from the inner compression chamber (S12, S22) to the outer compression chamber (S11, S21), and the end plate (31a, 41a) of the cylinder member (31, 41) Is fitted between the outer tooth portion (31b) and the inner tooth portion (31c). The end plate (31a, 41a) of the cylinder member (31, 41) is formed between the outer tooth portion (31b, 41b) and the inner tooth portion (31c, 41c) when only the cylinder seat member (64) is provided. The front surface is formed deeper by the thickness of the cylinder seat member (64). The cylinder seat member (64) is formed with openings (64a) for the first suction port (14a) and the second suction port (16a) and the discharge ports (35, 36, 45, 46). The opening (64b) is formed. Further, the cylinder seat member (64) is formed so that the surface thereof is flush with the axial end faces (30b, 40b) of the cylinder chambers (30a, 40a), and a piston member ( 32, 42) are formed so that the tooth portions (32b, 42b) are in sliding contact.

    That is, the surface of the seat member (60) is the same as the end face (30b, 40b) in the axial direction of the cylinder chamber (30a, 40a), and the piston member (32, 42) or cylinder member which is a counterpart member on the surface. (31, 41) are provided in sliding contact.

    Further, as shown in FIG. 8, the sheet member (60) may be formed by integrally forming a dividing sheet member (63), an outer sheet member (61), and an inner sheet member (62).

    In addition, as shown in FIG. 9, the sheet member (60) has a C-side process that is cut into a straight shape at the back corners to form a cut surface (65). The reason for forming this cut surface (65) is that an arcuate surface (70), which is a corner R, is formed at the corners of the end plate (32a, 42a,...) And the teeth (32b, 42b,...). Therefore, this arc surface (70) is avoided. FIG. 9 shows only the second cylinder member (41) and the second piston member (42).

-Driving action-
Next, the operation of the rotary compressor (10) will be described. First, in the first compression mechanism (30), the low-pressure refrigerant is compressed into an intermediate-pressure refrigerant.

    When the electric motor (20) is started, the tooth portion (32b) of the first piston member (32) reciprocates (advances and retreats) along the first blade (33) and swings. Then, the tooth portion (32b) of the first piston member (32) revolves while swinging with respect to the outer tooth portion (31b) and the inner tooth portion (31c) of the first cylinder member (31), and the first compression is performed. The mechanism (30) performs the compression operation.

    Specifically, in the outer compression chamber (S11), the volume of the low-pressure chamber (S11L) becomes almost minimum in the state of FIG. 2 (B), and from here the drive shaft (23) rotates in the direction of the arrow in the figure. The volume of the low-pressure chamber (S11L) increases as the state changes from 2 (C) to FIG. 2 (A), and the refrigerant in the first suction port (14a) becomes low-pressure chamber (S11) in the outer compression chamber (S11). S11L).

    When the drive shaft (23) makes one revolution and enters the state of FIG. 2 (B) again, the suction of the refrigerant into the low pressure chamber (S11L) is completed. The low pressure chamber (S11L) becomes a high pressure chamber (S11H) in which the refrigerant is compressed, and a new low pressure chamber (S11L) is formed across the first blade (33). When the drive shaft (23) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (S11L), while the volume of the high pressure chamber (S11H) is reduced, and the refrigerant is compressed in the high pressure chamber (S11H). When the pressure in the high pressure chamber (S11H) reaches a predetermined value and the differential pressure from the first discharge port (15a) reaches a set value, the discharge valve (37) opens, and the intermediate pressure refrigerant in the high pressure chamber (S11H) It flows out to the first discharge pipe (15) through the first discharge port (15a).

    In the inner compression chamber (S12), the volume of the low-pressure chamber (S12L) is substantially minimized in the state of FIG. 2 (F), and from here the drive shaft (23) rotates in the direction of the arrow in FIG. ) To FIG. 2 (E), the volume of the low pressure chamber (S12L) increases, and the refrigerant in the first suction port (14a) flows into the low pressure chamber (S12L) of the inner compression chamber (S12). ) Is inhaled.

    Then, when the drive shaft (23) makes one revolution and again enters the state of FIG. 2 (F), the suction of the refrigerant into the low pressure chamber (S12L) is completed. The low pressure chamber (S12L) becomes a high pressure chamber (S12H) in which the refrigerant is compressed, and a new low pressure chamber (S12L) is formed across the first blade (33). When the drive shaft (23) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (S12L), while the volume of the high pressure chamber (S12H) is reduced, and the refrigerant is compressed in the high pressure chamber (S12H). When the pressure in the high pressure chamber (S12H) reaches a preset value and the differential pressure from the first discharge port (15a) reaches the set value, the discharge valve (38) opens and the intermediate pressure refrigerant in the high pressure chamber (S12H) It flows out to the first discharge pipe (15) through the first discharge port (15a).

    In the outer compression chamber (S11), refrigerant discharge is started approximately at the timing of FIG. 2E, and discharge is started approximately at the timing of FIG. 2A in the inner compression chamber (S12). That is, the discharge timing is shifted by approximately 180 ° between the outer compression chamber (S11) and the inner compression chamber (S12). The intermediate pressure refrigerant that has flowed out to the first discharge pipe (15) flows into the second suction pipe (16) and is sucked into the second compression mechanism (40).

    In the second compression mechanism (40), the intermediate-pressure refrigerant is compressed into a high-pressure refrigerant in substantially the same manner as the first compression mechanism (30).

    When the electric motor (20) is driven, the tooth portion (42b) of the second piston member (42) reciprocates (advances and retreats) along the second blade (43) and swings. Then, the tooth portion (42b) of the second piston member (42) revolves while swinging with respect to the outer tooth portion (41b) and the inner tooth portion (41c) of the second cylinder member (41), and the second compression. The mechanism (40) performs the compression operation.

    Specifically, in the outer compression chamber (S21), the volume of the low-pressure chamber (S21L) becomes almost minimum in the state of FIG. 2 (B), and from here the drive shaft (23) rotates in the direction of the arrow in the figure. The volume of the low pressure chamber (S21L) increases with the change to the state of FIG. 2 (C) to FIG. 2 (A), and the refrigerant in the second suction port (16a) becomes the low pressure in the outer compression chamber (S21). Inhaled into the chamber (S21L).

    Then, when the drive shaft (23) makes one revolution and enters the state of FIG. 2 (B) again, the suction of the refrigerant into the low pressure chamber (S21L) is completed. The low pressure chamber (S21L) becomes a high pressure chamber (S21H) in which the refrigerant is compressed, and a new low pressure chamber (S21L) is formed across the second blade (43). When the drive shaft (23) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (S21L), while the volume of the high pressure chamber (S21H) is reduced, and the refrigerant is compressed in the high pressure chamber (S21H). When the pressure in the high pressure chamber (S21H) reaches a predetermined value and the differential pressure with respect to the second discharge port (17a) reaches a set value, the discharge valve (47) opens and the high pressure refrigerant in the high pressure chamber (S21H) is second. It flows out into the internal space (S10) in the casing (11) through the discharge port (17a).

    In the inner compression chamber (S22), the volume of the low-pressure chamber (S22L) becomes almost minimum in the state of FIG. 2 (F), and from here the drive shaft (23) rotates in the direction of the arrow in FIG. ) To FIG. 2 (E), the volume of the low pressure chamber (S22L) increases, and the refrigerant in the second suction port (16a) flows into the low pressure chamber (S22L) of the inner compression chamber (S22). Inhaled.

    Then, when the drive shaft (23) makes one revolution and again enters the state of FIG. 2 (F), the suction of the refrigerant into the low pressure chamber (S22L) is completed. The low pressure chamber (S22L) becomes a high pressure chamber (S22H) in which the refrigerant is compressed, and a new low pressure chamber (S22L) is formed across the second blade (43). When the drive shaft (23) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (S22L), while the volume of the high pressure chamber (S22H) is reduced, and the refrigerant is compressed in the high pressure chamber (S22H). The pressure in the high pressure chamber (S22H) reaches a predetermined value and flows out to the internal space (S10) in the casing (11) through the second discharge port (17a).

    In the outer compression chamber (S21), refrigerant discharge is started approximately at the timing shown in FIG. 2E, and in the inner compression chamber (S22), discharge is started approximately at the timing shown in FIG. That is, the discharge timing is shifted by approximately 180 ° between the outer compression chamber (S21) and the inner compression chamber (S22). The high-pressure refrigerant that has flowed into the internal space (S10) in the casing (11) is discharged from the second discharge pipe (17). In the refrigerant circuit, the refrigerant discharged from the rotary compressor (10) is again sucked into the rotary compressor (10) through the condensation process and the evaporation process.

-Effect of Embodiment 1-
As described above, in the present embodiment, the sheet member is provided on at least a part of the front surface of the end plate (32a, 42a) of the piston member (32, 42) and the front surface of the end plate (31a, 41a) of the cylinder member (31, 41). Since (60) is provided, refrigerant leakage caused by the circular arc surface (70) formed at the corners of the end plate (32a, 42a,...) And the teeth (32b, 42b,...) Can be suppressed.

    That is, the circular arc surface (70) generated at the corner of the end plate (32a, 31a) and the tooth portion (32b, 31b, 31c) is covered by the sheet member (60), and the sheet member (60) and the tooth portion The corners with (32b, 31b, 31c) are 45 ° corners. As a result, fluid leakage due to the circular arc surface (70) is suppressed.

    Specifically, for example, conventionally, when the tip corner portion of the tooth portion (d) of the cylinder member (a) is chamfered at 45 ° to form the cut surface (h), the refrigerant from the cut surface (h) There was a leak. However, in this embodiment, since the sheet member (60) is provided, it is not necessary to form a cut surface on the tooth portions (31b, 31c,...) Of the cylinder members (31, 41). Can be suppressed.

    For example, conventionally, the tip of the tooth part (d) of the cylinder member (a) rides on the arc surface (g), and the tooth part (d) of the cylinder member (a) and the end plate (e) of the piston member (b). And a gap is formed between the tooth portion (h) of the piston member (b) and the end plate (c) of the cylinder member (a), and fluid leaks from the high pressure compression chamber to the low pressure compression chamber. It was. However, in the present embodiment, since the sheet member (60) is provided, the tooth portions (31b, 41b,...) Are always in contact with the sheet member (60), so that refrigerant leakage can be suppressed.

    In particular, when the refrigerant is carbon dioxide (CO2), the differential pressure between the high pressure and the low pressure is large, and the influence of leakage is increased, but since this leakage can be suppressed, a decrease in compressor efficiency can be suppressed. .

    In the case of the rotary compressor (10), since the high pressure chamber and the low pressure chamber are adjacent to each other, the influence of refrigerant leakage is increased, but this leakage can be suppressed.

    Moreover, since formation of the said circular arc surface (70) can be accept | permitted, the lifetime of a processing tool becomes long and the raise of component cost can be suppressed.

    In addition, when the seat member (60) is provided in the divided portion (3b, 4b) of the tooth portion (32b, 42b) on the front surface of the end plate (32a, 42a) of the piston member (32, 42), the outer compression Refrigerant leakage between the chambers (S11, S21) and the inner compression chambers (S12, S22) can be reliably suppressed.

    Further, when the dividing sheet member (63), the outer sheet member (61), and the inner sheet member (62) are integrally formed, it is possible to more reliably suppress refrigerant leakage and simplify the structure. Can be planned.

    In addition, when the cylinder seat member (64) is provided, refrigerant leakage can be reliably suppressed when the cylinder members (31, 41) are formed of a relatively difficult steel material.

    Moreover, since the cut surface (65) is formed in the said sheet | seat member (60), the circular arc surface (70 which arises in the corner | angular part of an end plate (32a, 42a, ...) and a tooth | gear part (32b, 42b, ...) ) And the sheet member (60) can be avoided.

<Other embodiments>
The present invention may be configured as follows with respect to the first embodiment.

    Although the said embodiment demonstrated the rotary compressor (10), an rotary machine etc. may be sufficient as a rotary fluid machine.

    The rotary compressor (10) may be provided with any one of the first compression mechanism (30) and the second compression mechanism (40).

    Further, the rotary fluid machine as the rotary compressor (10) has a space (3a, 4a) between the bearing portion (32c, 42c) and the inner tooth portion (31c, 41c) such as a compression chamber. It may be formed in the working space. That is, the rotary fluid machine may include two or more cylinder chambers.

    Further, an outer working space such as a compression chamber may be formed outside the end plate (32a, 42a) of the piston member (32, 42).

    In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

    As described above, the present invention is useful for a rotary fluid machine in which a tooth portion is formed on an end plate.

DESCRIPTION OF SYMBOLS 10 Rotating compressor 30, 40 Compression mechanism 3b, 4b Dividing part 31, 41 Cylinder member 31a, 41a End plate 31b, 41b Outer tooth part 31c, 41c Inner tooth part 32, 42 Piston member 32a, 42a End plate 32b, 42b Tooth part 33, 43 Blade 34, 44 Bush (support member)
30a, 40a Cylinder chamber 60 Sheet member 61 Outer sheet member 62 Inner sheet member 63 Dividing sheet member 64 Cylinder sheet member 65 Cut portion

Claims (7)

A cylinder member (31) having an end plate (31a) and tooth portions (31b, 31c) projecting from the front surface of the end plate (31a), and having at least one annular cylinder chamber (30a) formed thereon; ,
A piston member (32) having an end plate (32a) and a toothed portion (32b) of an annular piston that is formed to project from the front surface of the end plate (32a) and is disposed in the cylinder chamber (30a);
The cylinder member (31) and the piston member (32) are disposed so that the front surfaces of the end plates (31a, 32a) face each other, and the cylinder member (31) and the piston member (32) are mutually opposed to each other (32, 31) is a rotary fluid machine in which the cylinder member (31) and the piston member (32) rotate relatively eccentrically,
The cylinder member (31) penetrates the dividing portion (3b) formed in the tooth portion (32b) so as to divide the tooth portion (32b) of the piston member (32) from the inside to the outside, A blade (33) that divides the cylinder chamber (30a) into a high-pressure side and a low-pressure side, and the blade (33) that is swingably supported on the piston member (32) by being arranged in the dividing portion (3b). A support member (34),
At least part of the front surface of the end plate (32a) of the piston member (32) and the end plate (31a) of the cylinder member (31) and where the piston member (32) and the cylinder member (31) are in sliding contact with each other The rotary fluid machine is characterized in that the surface is flush with the end face (30b) of the cylinder chamber (30a), and the sheet member (60) on which the mating member (31, 32) is slidably contacted is provided on the surface. . In claim 1,
The rotary fluid machine according to claim 1, wherein the seat member (60) is provided at a dividing portion (3b) of the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). In claim 1 or 2,
The rotary fluid machine according to claim 1, wherein the seat member (60) is provided outside the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). In any one of Claims 1-3,
The rotary fluid machine according to claim 1, wherein the seat member (60) is provided inside the tooth portion (32b) on the front surface of the end plate (32a) of the piston member (32). In claim 1,
The sheet member (60) is provided on the front surface of the end plate (32a) of the piston member (32), and on the outer side of the cutting sheet member (63) and the tooth portion (32b) provided on the dividing portion (3b) of the tooth portion (32b). The outer sheet member (61) provided on the inner side and the inner sheet member (62) provided on the inner side of the tooth portion (32b) are integrally formed. In any one of Claims 1-5,
In
The rotary fluid machine according to claim 1, wherein the seat member (60) is provided on a front surface of the end plate (31a) of the cylinder member (31). In any one of Claims 1-6,
In
The rotary fluid machine according to claim 1, wherein a back corner portion of the sheet member (60) is formed in a cut surface (65) cut in a straight line.

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