Compressor unit

Abstract

This compressor unit comprises: a compressor (1) having a first casing (10) with a cylindrical first trunk section (11), an electric motor (20) accommodated in the first casing (10), a drive shaft (70) driven by the electric motor (20), and a rotary compression mechanism (15); and an accumulator (2) having a second casing (60) with a cylindrical second trunk section (61) adjacent to the first casing (10) in the horizontal direction, and outlet pipes (65a, 65b) extending from a lower part of the second casing (60) and connected to the first trunk section (11). A first eigenvalue s1 in a rolling direction of the accumulator (2) does not overlap a value of n·N (N being an integer), which is an integral multiple of the maximum rotational speed n of the compressor (1).

Description

Compressor Unit

[0001] The present disclosure relates to a compressor unit.

[0002] There is a refrigeration cycle apparatus having a compressor connected to an accumulator. The accumulator described in Patent Document 1 is fixed to a side surface of a casing of the compressor via a bracket.

[0003] Japanese Patent Application Laid-Open No. 2001-317479

[0004] When the compressor is operating, resonance may occur, causing vibration and noise in the accumulator. In Patent Document 1, adjusting the position of the bracket is attempted to suppress the vibration and noise of the accumulator caused by the operation of the compressor, but this is not sufficient.

[0005] An object of the present disclosure is to suppress vibration of an accumulator caused by operation of a compressor.

[0006] In a first aspect, a compressor (1) includes: a compressor (1); and an accumulator (2) adjacent to the compressor (1), wherein the compressor (1) includes: a first casing (10) having a cylindrical first body (11); an electric motor (20) accommodated in the first casing (10); a drive shaft (70) driven by the electric motor (20); and a rotary compression mechanism (15) that compresses a fluid; and the accumulator (2) includes: a second casing (60) having a cylindrical second body (61) horizontally adjacent to the first casing (10); and outlet pipes (65a, 65b) extending from a lower part of the second casing (60) and connected to the first body (11), wherein: when a direction in which the second body (61) advances so as to roll circumferentially on the outer circumferential surface of the first body (11) is defined as a rolling direction, The compressor unit has a first eigenvalue s1 of the rolling direction of the accumulator (2) that does not coincide with a value of n·N (N is an integer) that is an integer multiple of the maximum rotation speed n of the compressor (1).

[0007] One of the vibration modes of the accumulator that occurs due to the operation of the compressor is a vibration mode in which the accumulator vibrates in a rolling manner on the outer peripheral surface of the compressor casing. It has been found that when this vibration mode coincides with an integer multiple of the maximum rotation speed n of the compressor (1), the vibration of the accumulator increases. Therefore, in the first aspect, the first eigenvalue does not overlap with n·N, so that the increase in such vibration can be suppressed.

[0008] A second aspect is the first aspect, wherein the first eigenvalue s1 satisfies n·N+n / 4≦s1≦n·N+3n / 4.

[0009] While the closer the first eigenvalue s1 is to an integer multiple of n, the greater the vibration, in the second aspect, the first eigenvalue s1 can be set to a value relatively far from an integer multiple of n, thereby improving the vibration reduction effect.

[0010] A third aspect is the first or second aspect, further comprising a first adjuster (64) that adjusts the first eigenvalue s1.

[0011] In the third aspect, the first eigenvalue s1 can be set to a desired value.

[0012] A fourth aspect is the third aspect, wherein the first adjustment portion (64) is a plate-shaped fixed member (64) that fixes the compressor (1) and the accumulator (2), and the fixed member (64) has a bent portion (64d) formed so that the plate is bent between the first body portion (11) and the second body portion (61), and the shape of the bent portion (64d) or the position of the bent portion (64d) on the fixed member (64) is determined so that the first eigenvalue s1 does not overlap the value of n·N.

[0013] In the fourth aspect, the first eigenvalue s1 can be easily adjusted by setting the shape and the attachment position of the fixing member (64).

[0014] A fifth aspect is the compressor according to any one of the first to fourth aspects, wherein the compression mechanism (15) is a two-cylinder rotary compression mechanism, and the first eigenvalue s1 is greater than 2n.

[0015] In the fifth aspect, since the compression mechanism (15) is a two-cylinder rotary type, an excitation force of 2n acts on the compression mechanism (15). In this way, the excitation force of 2n of the two-cylinder compressor (1) and the first eigenvalue s1 can be prevented from overlapping, thereby suppressing an increase in vibration of the accumulator (2).

[0016] A sixth aspect is the fifth aspect, wherein the outlet pipes (65a, 65b) include a first outlet pipe (65a) and a second outlet pipe (65b) extending side by side from a lower part of the accumulator (2), a second characteristic value s2 of the outlet pipes (65a, 65b) is greater than 2n, and a first connection portion (82a) which is a connection portion between the first outlet pipe (65a) and the second casing (60) and a second connection portion (82b) which is a connection portion between the second outlet pipe (65b) and the second casing (60) are located at positions deviated from the cylindrical axis center of the second casing (60).

[0017] In the sixth aspect, the first connection portion (82a) and the second connection portion (82b) are offset from the cylindrical axis center of the second casing (60), so that the second eigenvalue s2 does not overlap with n·N.

[0018] A seventh aspect is the sixth aspect, further comprising a second adjustment section (68) that adjusts the second eigenvalue s2.

[0019] In the seventh aspect, the second adjusting section (68) can prevent the second eigenvalue s2 from overlapping with n·N.

[0020] An eighth aspect is the seventh aspect, wherein the second adjustment portion (68) is a support member (68) that supports the outlet pipes (65a, 65b) in the second casing (60).

[0021] In the eighth aspect, the second eigenvalue s2 can be easily adjusted by setting the shape and the attachment position of the support member (68).

[0022] A ninth aspect is the seventh aspect, wherein the outlet pipe (65a, 65b) has a first pipe portion (80a) and a second pipe portion (80b) having different pipe thicknesses, the first pipe portion (80a) and the second pipe portion (80b) are continuous with each other in the outlet pipe (65a, 65b), and the second adjustment portion (68) is the first pipe portion (80a) or the second pipe portion (80b).

[0023] In the ninth aspect, the first pipe portion (80a) and the second pipe portion (80b) having different pipe thicknesses are provided in the outlet pipe (65a, 65b), thereby making it possible to adjust the characteristic value of the outlet pipe (65a, 65b). That is, the second characteristic value s2 can be easily adjusted by setting the positions and pipe thicknesses of the first pipe portion (80a) and the second pipe portion (80b) in the outlet pipe (65a, 65b).

[0024] A tenth aspect is the compressor according to any one of the first to ninth aspects, wherein the compressor (1) rotates at a rotation speed of 120 rps or more.

[0025] In the tenth aspect, it is possible to improve the effect of suppressing vibration of the accumulator (2), which increases at a rotation speed of 120 rps or more, particularly 150 rps.

[0026] An eleventh aspect is a refrigeration apparatus including the compressor unit according to any one of the first to tenth aspects.

[0027] In the eleventh aspect, it is possible to provide a refrigeration system capable of reducing vibration of the accumulator (2) caused by operation of the compressor (1).

[0028] FIG. 1 is a piping system diagram of a refrigeration apparatus according to an embodiment. FIG. 2 is a diagram showing a cross section of a compressor unit according to an embodiment cut in the vertical direction. FIG. 3 is a plan view of a piston of a compression mechanism. (A) is a plan view of a first compression mechanism. (B) is a plan view of a second compression mechanism. FIG. 4 is a diagram showing the shape of a fixing member. (A) is a diagram showing a part of a state in which a compressor and an accumulator are fixed by a fixing member, as seen from above. (B) is a diagram showing a first surface of the fixing member as seen from the front. FIG. 5 is a diagram showing the operation of the compression mechanism. FIG. 6 is a cross section of an accumulator according to Modification 1 cut in the vertical direction. FIG. 7 is a cross section of an accumulator according to Modification 2 cut in the vertical direction.

[0029] Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the following embodiments are essentially preferred examples and are not intended to limit the scope of the present invention, its applications, or its uses. Furthermore, each configuration of the embodiments, modifications, other examples, etc. described below can be combined or partially substituted within the scope of the present invention.

[0030] (1) Compressor Unit As shown in FIG. 1 , the compressor unit (U) of the embodiment is applied to a refrigeration system (100). The refrigeration system (100) is, for example, an air conditioner that conditions the air inside a room. The refrigeration system (100) includes a refrigerant circuit (9) that performs a refrigeration cycle. The refrigerant circuit (9) includes a refrigerant pipe (9a) through which a refrigerant flows. A compressor (1), an accumulator (2), a four-way switching valve (3), an outdoor heat exchanger (4), an expansion valve (5), and an indoor heat exchanger (6) are connected to the refrigerant pipe (9a). The compressor unit (U) of the embodiment includes a compressor (1) and an accumulator (2).

[0031] The four-way switching valve (3) has four ports (P1, P2, P3, P4). The four-way switching valve (3) switches the flow path of the refrigerant circuit (9) between the state shown by the solid lines and the state shown by the dashed lines in Fig. 1. In this way, the refrigerant circuit (9) switches between a first refrigeration cycle for cooling the room and a second refrigeration cycle for heating the room.

[0032] The outdoor heat exchanger (4) is provided in an outdoor unit (not shown) located outside the room. The outdoor heat exchanger (4) exchanges heat between the refrigerant and the outside air. The outdoor heat exchanger (4) functions as a radiator in the first refrigeration cycle and as an evaporator in the second refrigeration cycle.

[0033] The expansion valve (5) reduces the pressure of the refrigerant in the refrigerant circuit and is, for example, an electronic expansion valve whose opening is adjustable.

[0034] The indoor heat exchanger (6) is provided in an indoor unit (not shown) arranged indoors. The indoor heat exchanger (6) exchanges heat between the refrigerant and the indoor air. The indoor heat exchanger (6) functions as an evaporator in the first refrigeration cycle and as a radiator in the second refrigeration cycle.

[0035] (2) Compressor The compressor (1) is a rotary compressor. The compressor (1) compresses a refrigerant flowing through a refrigerant circuit. The refrigerant is an example of a fluid. The compressor (1) has a first casing (10), an electric motor (20), and a compression mechanism (15). The electric motor (20) and the compression mechanism (15) are housed in the first casing (10). The compressor (1) is configured as a so-called high-pressure dome in which the refrigerant compressed in the compression mechanism (15) is discharged into the internal space of the first casing (10), causing the internal space to become high-pressure.

[0036] (2-1) First Casing The first casing (10) is a vertically elongated, sealed metallic container. The first casing (10) has a cylindrical first body (11) extending in the vertical direction, an upper head (12) closing the upper end of the first body (11), and a lower head (13) closing the lower end of the first body (11). A discharge pipe (8) is connected to the upper head (12). A first suction pipe (14a) and a second suction pipe (14b) are provided at the lower part of the first body (11). The first body (11) forms the side surface of the first casing (10).

[0037] (2-2) Electric Motor The electric motor (20) is disposed in the upper portion of the internal space of the first casing (10). The electric motor (20) includes a stator (21) and a rotor (22). The stator (21) is fixed to the first body (11). The rotor (22) is attached to a drive shaft (70) of a compression mechanism (15) described later. The drive shaft (70) is disposed so as to extend in the vertical direction within the first casing (10). The drive shaft (70) is driven by the electric motor (20). An upper portion of the drive shaft (70) is connected to the rotor (22) of the electric motor (20). The drive shaft (70) will be described in detail later.

[0038] (2-3) Compression Mechanism The compression mechanism (15) is a so-called swing piston type rotary fluid machine. The compression mechanism (15) of this embodiment is a two-cylinder rotary fluid machine having a first compression mechanism (K1) and a second compression mechanism (K2). In the internal space of the first casing (10), the compression mechanism (15) is disposed below the electric motor (20).

[0039] The compression mechanism (15) is configured so that, arranged from top to bottom in this order, are a front head (24), a first cylinder (30), an intermediate plate (50), a second cylinder (35), and a rear head (25).

[0040] (2-3-1) Front Head The front head (24) is a member that closes the end face of the first cylinder (30) on the electric motor (20) side (the upper end face of the first cylinder (30) in FIG. 1). The front head (24) is fixed to the inner surface of the first body portion (11). The front head (24) has a main bearing portion (23). The main bearing portion (23) constitutes a journal bearing that supports the drive shaft (70) of the compression mechanism (15). A discharge port (not shown) that discharges refrigerant from a cylinder chamber (S) described below is formed in the front head (24).

[0041] (2-3-2) Rear Head The rear head (25) is a member that closes the end face of the second cylinder (35) on the side opposite to the electric motor (20) (the lower end face of the second cylinder (35) in FIG. 1). The rear head (25) has an auxiliary bearing portion (27). The auxiliary bearing portion (27) constitutes a journal bearing that supports the drive shaft (70) of the compression mechanism (15). A discharge port (not shown) that discharges refrigerant from a cylinder chamber (S) described below is formed in the rear head (25).

[0042] (2-3-3) Cylinder and Piston As shown in Fig. 3, the first compression mechanism (K1) has a first cylinder (30), a first piston (40), and a first blade (41). The second compression mechanism (K2) has a second cylinder (35), a second piston (45), and a second blade (46).

[0043] Each cylinder (30, 35) is a thick-walled disk-shaped member. The cylinders (30, 35) have the same thickness. Each cylinder (30, 35) has a cylinder bore (31, 36) and a blade receiving hole (32, 37) formed therein.

[0044] The cylinder bores (31, 36) are circular holes that penetrate the cylinders (30, 35) in the thickness direction. Specifically, the first cylinder bore (31) is formed in the center of the first cylinder (30). The second cylinder bore (36) is formed in the center of the second cylinder (35).

[0045] A first piston (40) is accommodated in the first cylinder bore (31). A second piston (45) is accommodated in the second cylinder bore (36). The inner diameter of the first cylinder bore (31) and the inner diameter of the second cylinder bore (36) are equal to each other.

[0046] A first cylinder chamber (S) is formed between the wall surface of the first cylinder bore (31) and the first piston (40). In this manner, the first cylinder (30) has the first cylinder chamber (S). A second cylinder chamber (S) is formed between the wall surface of the second cylinder bore (36) and the second piston (45). In this manner, the second cylinder (35) has the second cylinder chamber (S).

[0047] The blade accommodating holes (32, 37) are holes in which the blades (41, 46) are accommodated. The blade accommodating holes (32, 37) are formed to extend from the inner circumferential surface of the cylinder (30, 35) (i.e., the outer edge of the cylinder bore (31, 36)) toward the radially outer side of the cylinder (30, 35). The blade accommodating holes (32, 37) penetrate the cylinder (30, 35) in the thickness direction. The first blade accommodating hole (32) is formed in the first cylinder (30). The second blade accommodating hole (37) is formed in the second cylinder (35).

[0048] The first cylinder (30) is provided with a first suction port (33). The second cylinder (35) is provided with a second suction port (38). The first suction port (33) is connected to the first suction pipe (14a). The second suction port (38) is connected to the second suction pipe (14b). Each suction port (33, 38) communicates with the first chamber (S1) of the cylinder chamber (S). When the cylinders (30, 35) shown in FIG. 4 are viewed from above, each suction port (33, 38) is located to the right of the blade accommodating holes (32, 37). The discharge port (not shown) is located to the left of the blade accommodating holes (32, 37).

[0049] The pistons (40, 45) shown in Fig. 3 rotate eccentrically within the cylinders (30, 35). The first piston (40) and the second piston (45) are members having the same shape, dimensions, and material. Each piston (40, 45) is a cylindrical member with a slightly thick wall.

[0050] The first eccentric portion (75) of the drive shaft (70) is inserted into the first piston (40). The first piston (40) rotates eccentrically as the first eccentric portion (75) of the drive shaft (70) rotates. The second piston (45) is inserted into the second eccentric portion (76) of the drive shaft (70) is inserted into the second piston (45). The second piston (45) rotates eccentrically as the second eccentric portion (76) of the drive shaft (70) rotates.

[0051] Each blade (41, 46) is a relatively thick rectangular plate-like member. The first blade (41) is formed integrally with the first piston (40). The first blade (41) is disposed in the first blade housing hole (32). The first blade (41) divides the first cylinder chamber (S) into a first chamber (S1) on the suction side and a second chamber (S2) on the discharge side. The second blade (46) is disposed in the second blade housing hole (37). The second blade (46) divides the second cylinder chamber (S) into a first chamber (S1) on the suction side and a second chamber (S2) on the discharge side.

[0052] Each blade (41, 46) is sandwiched between a pair of bushes (42, 47). Each blade (41, 46) is supported by the cylinder (30, 35) via the bushes (42, 47) so as to be swingable and movable back and forth.

[0053] (2-3-4) Intermediate Plate The intermediate plate (50) shown in Fig. 2 is disposed so as to be sandwiched between the first cylinder (30) and the second cylinder (35). The intermediate plate (50) is in close contact with the lower end surface of the first cylinder (30) and the upper end surface of the second cylinder (35).

[0054] A central hole (51) is formed in the central portion of the intermediate plate (50) so as to penetrate the intermediate plate (50) in the thickness direction. The central connector (78) of the drive shaft (70) is inserted into the central hole (51) of the intermediate plate (50).

[0055] (2-4) Drive Shaft As shown in Figures 2 and 3, the drive shaft (70) is a member that drives the pistons (40, 45). Specifically, the drive shaft (70) includes, arranged in this order from top to bottom, a main shaft portion (72), a first eccentric portion (75), an intermediate connecting portion (78), a second eccentric portion (76), and a counter shaft portion (74). The rotational axis (70a) of the drive shaft (70) substantially coincides with the central axes of the cylinder bores (31, 36) of the cylinders (30, 35).

[0056] The main shaft (72) is attached to the rotor (22) of the electric motor (20) and is supported by the main bearing (23) of the front head (24). The counter shaft (74) is supported by the counter bearing (27) of the rear head (25).

[0057] The first eccentric portion (75) and the second eccentric portion (76) are cylindrical portions having a diameter larger than that of the main shaft portion (72). The first eccentric portion (75) and the second eccentric portion (76) have the same shape. The central axes of the first eccentric portion (75) and the second eccentric portion (76) are eccentric with respect to the rotation axis (70a) of the drive shaft (70). The first eccentric portion (75) is eccentric with respect to the rotation axis (70a) of the drive shaft (70) on the side opposite to the second eccentric portion (76). In other words, the eccentric direction of the first eccentric portion (75) with respect to the rotation axis (70a) of the drive shaft (70) differs by 180° from the eccentric direction of the second eccentric portion (76) with respect to the rotation axis (70a) of the drive shaft (70).

[0058] The intermediate connector (78) is disposed between the first eccentric part (75) and the second eccentric part (76), and connects the first eccentric part (75) and the second eccentric part (76).

[0059] (3) Accumulator The accumulator (2) shown in FIGS. 1 and 2 temporarily stores the refrigerant drawn into the compressor (1). The accumulator (2) separates gas from liquid. Specifically, the accumulator (2) separates liquid refrigerant and refrigeration oil contained in the gas refrigerant. The accumulator (2) is disposed adjacent to the compressor (1). The accumulator (2) includes a second casing (60), outlet pipes (65a, 65b), and a fixed member (64).

[0060] (3-1) Second Casing The second casing (60) is a vertically elongated sealed container made of metal. The second casing (60) has a cylindrical second body (61) extending in the vertical direction, an upper lid (81) closing the upper end of the second body (61), and a lower lid (82) closing the lower end of the second body (61). The second casing (60) is horizontally adjacent to the first casing (10). Specifically, the second body (61) is disposed adjacent to the first body (11). The cylindrical axes of the first body (11) and the second body (61) are oriented in the same direction. The second body (61) constitutes the side surface of the second casing (60).

[0061] In this example, the second body portion (61) has an upper body portion (61a) and a lower body portion (61b). The upper body portion (61a) and the upper cover portion (81) are integrally formed. The lower body portion (61b) and the lower cover portion (82) are integrally formed. The upper end of the lower body portion (61b) is fitted into the lower end of the upper body portion (61a).

[0062] The upper cover portion (81) is formed with an inlet portion (81a) which is a hole to which the inlet pipe (7) is connected. The inlet pipe (7) is fixed to the inlet portion (81a) by, for example, welding. The inlet pipe (7) is connected to the refrigerant pipe (9a). The inlet portion (81a) is formed in the center of the upper cover portion (81) when the second casing (60) is viewed from above. In other words, the inlet portion (81a) is disposed on the cylindrical axis of the second body portion (61).

[0063] The lower cover portion (82) is formed with connection portions (82a, 82b) which are holes to which the outlet pipes (65a, 65b) are connected. The connection portions (82a, 82b) have a first connection portion (82a) and a second connection portion (82b). The first connection portion (82a) and the second connection portion (82b) open downward. The first connection portion (82a) and the second connection portion (82b) are formed at positions that are off-center of the lower cover portion (82) when the second casing (60) is viewed from below. In other words, the first connection portion (82a) and the second connection portion (82b) are formed at positions that do not coincide with the cylindrical axis of the second body portion (61).

[0064] (3-2) Outlet Pipes The outlet pipes (65a, 65b) are pipes that extend from the lower part of the second casing (60) and are connected to the side surface of the first casing (10). The outlet pipes (65a, 65b) include a first outlet pipe (65a) and a second outlet pipe (65b) that extend side by side from the lower part of the accumulator (2).

[0065] The first outlet pipe (65a) is inserted through the first connecting portion (82a). The first outlet pipe (65a) is fixed to the first connecting portion (82a), for example, by welding. One end, i.e., the upper end, of the first outlet pipe (65a) extends from the first connecting portion (82a) to an upper portion of the second casing (60) along the cylindrical axis direction. The other end of the first outlet pipe (65a) is connected to the first suction pipe (14a). The first outlet pipe (65a) extends downward from the first connecting portion (82a) and then extends horizontally toward the first suction pipe (14a).

[0066] The second outlet pipe (65b) is inserted through the second connecting portion (82b). The second outlet pipe (65b) is fixed to the second connecting portion (82b), for example, by welding. One end of the second outlet pipe (65b) extends from the second connecting portion (82b) to an upper portion of the second casing (60) along the cylindrical axis direction. The other end of the second outlet pipe (65b) is connected to the second suction pipe (14b). The second outlet pipe (65b) extends downward from the second connecting portion (82b) and then extends horizontally toward the second suction port (38). The upper ends of the first outlet pipe (65a) and the second outlet pipe (65b) are located at approximately the same height.

[0067] (3-3) Fixing Member As shown in FIGS. 2 and 4(A), the fixing member (64) fixes the compressor (1) and the accumulator (2). The fixing member (64) is provided between the first casing (10) and the second casing (60). Specifically, the fixing member (64) is provided between the first body portion (11) and the second body portion (61). The fixing member (64) is a plate-shaped member.

[0068] The fixing member (64) has a first fixing portion (64a) fixed to the outer peripheral surface of the second body portion (61), two second fixing portions (64b) fixed to the outer peripheral surface of the first body portion (11), and an extension portion (64c) extending from the first fixing portion (64a) to the second fixing portion (64b).

[0069] The first fixing portion (64a) is formed so as to curve along the outer peripheral surface of the second body portion (61). The surface of the first fixing portion (64a) facing the second body portion (61) is in contact with the outer peripheral surface of the second body portion (61).

[0070] The extension portion (64c) connects the first fixed portion (64a) and the second fixed portion (64b). The extension portion (64c) is provided to extend from both ends of the first fixed portion (64a) in the circumferential direction of the second trunk portion (61) toward the outer peripheral surface of the first trunk portion (11). The extension portion (64c) has a bent portion (64d). The bent portion (64d) forms a connection portion between the connection portion (82a, 82b) and the first fixed portion (64a). The bent portion (64d) is formed to bend from both ends of the first fixed portion (64a) toward the outer peripheral surface of the first trunk portion (11). A predetermined bend radius (R) is set in the bent portion (64d). In this manner, the fixing member (64) has the bent portion (64d). The bent portion (64d) is formed such that the plate is bent between the first body portion (11) and the second body portion (61).

[0071] The second fixing portion (64b) extends from the end of the extension portion (64c) in the circumferential direction of the first trunk portion (11). A surface of the second fixing portion (64b) facing the first trunk portion (11) is in contact with the outer peripheral surface of the second trunk portion (61). In this manner, the two second fixing portions (64b) are fixed to the second trunk portion (61) so as to sandwich the first trunk portion (11).

[0072] The first fixing portion (64a) has welding projections (66) formed thereon ( FIG. 4(B) ). In this embodiment, four projections (66) are formed on the surface of the first fixing portion (64a) facing the second body portion (61). By melting the projections (66), the first fixing portion (64a) is fixed to the first body portion (11). The number of projections (66) formed on the first fixing portion (64a) may be two.

[0073] (3-4) Support Member As shown in FIG. 2, the support member (68) supports the outlet pipes (65a, 65b) in the second casing (60). The support member (68) is fixed in the second casing (60). The support member (68) contacts the upper portions of the first outlet pipe (65a) and the second outlet pipe (65b). As a result, the first outlet pipe (65a) is fixed in the second casing (60) by the first connecting portion (82a) and the support member (68). The second outlet pipe (65b) is fixed in the second casing (60) by the second connecting portion (82b) and the support member (68).

[0074] (4) Operation of the Compressor The operation of the compressor (1) will be described with reference to Figure 5. When the electric motor (20) drives the drive shaft (70), each piston (40, 45) of the compression mechanism (15) is driven by the drive shaft (70). Each piston (40, 45) is periodically displaced within the corresponding cylinder (30, 35) with each rotation of the drive shaft (70). In a two-cylinder rotary compressor, the first compression mechanism (K1) and the second compression mechanism (K2) each perform a process of drawing, compressing, and discharging a refrigerant.

[0075] In each cylinder (30, 35), the volumes of the first chamber (S1) and the second chamber (S2) of the cylinder chamber (S, S) change with the displacement of the piston (40, 45). In each cylinder (30, 35), a suction stroke is performed in which refrigerant is drawn into the cylinder chamber (S, S) from the suction port (33, 38), a compression stroke is performed in which the refrigerant drawn into the cylinder chamber (S, S) is compressed, and a discharge stroke is performed in which the compressed refrigerant is discharged from the discharge port to the outside of the cylinder chamber (S, S).

[0076] Here, the angles shown in Figure 5 are 0°, which is the rotation angle of the drive shaft (70) when the first blade (41) of the first compression mechanism (K1) is at its farthest retreat from the first cylinder (30), and 180°, which is the rotation angle of the drive shaft (70) when the first blade (41) of the first compression mechanism (K1) is at its farthest retreat from the first cylinder (30).

[0077] The eccentric direction of the first piston (40) relative to the rotation axis (70a) of the drive shaft (70) differs by 180° from the eccentric direction of the second piston (45) relative to the rotation axis (70a) of the drive shaft (70), and therefore the period of displacement of the first piston (40) and the period of displacement of the second piston (45) are shifted by 180° (i.e., half a period). In the following, the operation of the first compression mechanism (K1) will be described, and a description of the operation of the second compression mechanism (K2) will be omitted.

[0078] (5) Operation of the First Compression Mechanism (5-1) Suction Process When the drive shaft (70) rotates slightly clockwise in Fig. 5 from a rotation angle of 0°, the contact position between the first piston (40) and the first cylinder (30) passes through the first suction port (33). At this time, suction of refrigerant into the first chamber (S1) of the first cylinder (30) begins.

[0079] As the rotation angle of the drive shaft (70) increases, the volume of the first chamber (S1) gradually increases, and the amount of refrigerant drawn into the first chamber (S1) increases. This refrigerant suction process continues until the rotation angle of the drive shaft (70) reaches 360°, after which the process transitions to a discharge process.

[0080] (5-2) Discharge Process When the drive shaft (70) rotates slightly from the state where the rotation angle is 0°, the contact position between the first piston (40) and the first cylinder (30) again passes through the first suction port (33). At this time, the confinement of the refrigerant in the first chamber (S1) is completed, and the first chamber (S1) that was connected to the first suction port (33) becomes the second chamber (S2) that is connected only to the discharge port.

[0081] From this state, the refrigerant in the second chamber (S2) starts to be compressed. As the rotation angle of the drive shaft (70) increases, the volume of the second chamber (S2) decreases and the pressure in the second chamber (S2) increases. When the pressure in the second chamber (S2) exceeds a predetermined pressure, the discharge valve opens. At this time, the refrigerant in the second chamber (S2) is discharged from the discharge port to the outside of the compression mechanism (15).

[0082] This discharge stroke of the refrigerant continues until the rotation angle of the drive shaft (70) reaches 360°, after which the suction stroke begins. In this manner, in the first compression mechanism (K1), the suction stroke and the discharge stroke are alternately repeated, thereby continuously compressing the refrigerant.

[0083] (6) Issues of Vibration Due to Compressor Operation In a compressor unit including a compressor and an accumulator, the accumulator has multiple vibration modes. Specifically, the vibration modes include a first mode in which the upper part of the accumulator vibrates, a second mode in which the lower part of the accumulator vibrates, and a third mode in which the accumulator moves in a rolling direction along the circumferential direction of the compressor on the outer circumferential surface of the compressor. Regarding the accumulator's eigenvalues, the first and second modes have eigenvalues ​​around 500 Hz to 2000 Hz, while the third mode often has an eigenvalue between 200 Hz and 300 Hz. When the compressor is operating, not only do the first and second modes generate noise, but the third mode also vibrates the accumulator, potentially leading to damage to the refrigerant pipes and outlet pipes.

[0084] In addition, the vibration mode of the outlet pipe of the accumulator may also have an eigenvalue in the same frequency band as the third mode, so when the vibration mode of the outlet pipe and the third vibration mode overlap, the vibration of the accumulator becomes even stronger.

[0085] Furthermore, when the compressor is a rotary compressor having two cylinders, a 2n (n: compressor rotation speed) excitation force acts on the compressor due to torque fluctuations and vibrations of the drive shaft caused by rotation of the drive shaft. In particular, in a small, high-speed compressor, the eigenvalue of the drive shaft decreases as the diameter of the drive shaft decreases. Therefore, it has been found that when the compressor rotation speed reaches 120 rpm or more, particularly 150 rpm, the frequency bands of the 2n excitation force, the third mode, and the outlet pipe vibration mode become close to each other, resulting in increased vibration of the accumulator. Based on this finding, the compressor unit (U) of this embodiment is provided with a first adjustment unit (64) and a second adjustment unit (68) for adjusting the eigenvalue.

[0086] (7) First Adjustment Unit and Second Adjustment Unit The first adjustment unit (64) adjusts the first eigenvalue s1, which is an eigenvalue of the rolling direction of the accumulator (2). The rolling direction is the direction in which the second casing (60) rolls circumferentially around the outer circumferential surface of the first casing (10). In this embodiment, the first adjustment unit (64) is a fixed member (64). The fixed member (64) adjusts the first eigenvalue s1 so that it does not become a value n·N (N is an integer), which is an integer multiple of the maximum rotation speed n of the compressor (1). Here, since the compressor in this embodiment is a two-cylinder rotary compressor, N=2. Therefore, the fixed member (64) adjusts the first eigenvalue s1 so that it is greater than 2n.

[0087] Specifically, the first eigenvalue s1 of the fixing member (64) is adjusted to satisfy the target range. The target range of the first eigenvalue s1 is n·N+n / 4≦s1≦n·N+3n / 4 (N≧2). The fixing member (64) is shaped so that the first eigenvalue s1 falls within the target range. Here, the fixing member (64) is formed by bending a single metal plate, and the shape or position of the bent portion (64d) is determined so that the first eigenvalue s1 falls within the target range. For example, the bending radius of the bent portion (64d) is set so that the first eigenvalue s1 falls within the target range. Furthermore, the bent portion (64d) is formed at a position on the fixing member (64) so ​​that the first eigenvalue s1 falls within the target range. In this way, during the manufacture of the compressor unit (U), the fixing member (64) is formed so that the first eigenvalue s1 falls within the target range, and therefore, a compressor unit (U) capable of suppressing vibration can be easily manufactured. The natural frequency or vibration measurement can be determined by a known test or measurement method.

[0088] The second adjustment section (68) adjusts a second eigenvalue s2, which is an eigenvalue of the outlet pipes (65a, 65b). The second eigenvalue s2 is an eigenvalue of the first outlet pipe (65a) and the second outlet pipe (65b). In this embodiment, the second adjustment section (68) is a support member (68). The second eigenvalue s2 can be adjusted by adjusting the position at which the support member (68) supports the first outlet pipe (65a) and the second outlet pipe (65b). The first outlet pipe (65a) and the second outlet pipe (65b) are supported by the support member (68) at the same height position. In other words, the first outlet pipe (65a) and the second outlet pipe (65b) are supported by the support member (68) at the same height position.

[0089] Specifically, the support member (68) supports the first outlet pipe (65a) and the second outlet pipe (65b) in the second casing (60) so that the second eigenvalue s2 does not coincide with n × N. The support member (68) of this embodiment supports the first outlet pipe (65a) and the second outlet pipe (65b) so that the second eigenvalue s2 does not coincide with 2n. In this manner, by providing the support member (68) to the second casing (60) so that the second eigenvalue s2 does not coincide with 2n during manufacturing of the compressor unit (U), a compressor unit (U) capable of suppressing vibration can be easily manufactured.

[0090] (8) Features (8-1) Feature 1 In the compressor unit (U) of this embodiment, the first eigenvalue s1 in the rolling direction of the accumulator (2) does not overlap with the value of n·N (N is an integer), which is an integer multiple of the maximum rotation speed n of the compressor (1). This prevents the third vibration mode from overlapping with the 2n vibration, thereby suppressing vibration of the accumulator. As a result, noise generated from the refrigeration system (100) due to operation of the compressor (1) can be suppressed, and damage to the piping connected to the accumulator (2), and consequently failure of the refrigeration system (100), can be suppressed.

[0091] (8-2) Feature 2 The first eigenvalue s1 of the present embodiment satisfies n·N+n / 4≦s1≦n·N+3n / 4. While an exciting force acts on the compressor (1) at an integer multiple of the maximum rotation speed n of the compressor (1), the first eigenvalue s1 is in the range farthest from an integer multiple of n, and therefore, the effect of suppressing vibration of the accumulator (2) can be improved.

[0092] (8-3) Feature 3 The compressor unit (U) of this embodiment includes a first adjustment unit (64) that adjusts the first eigenvalue s1. This allows the first eigenvalue s1 to be adjusted to a target value, thereby easily suppressing vibration of the accumulator (2) without considering the shape, size, placement, etc. of the accumulator (2).

[0093] (8-4) Feature 4 The first adjustment section (64) of the present embodiment includes a fixing member (64) having a bent portion (64d) formed so that the plate is bent between the first body portion (11) and the second body portion (61). The shape of the bent portion (64d) or the position of the bent portion (64d) in the fixing member (64) is determined so that the first eigenvalue s1 does not overlap the value of n·N.

[0094] In this manner, the first eigenvalue s1 can be easily adjusted by setting the shape and the mounting position of the fixing member (64).

[0095] (8-5) Feature 5 In the two-cylinder rotary compression mechanism of this embodiment, the first eigenvalue s1 is greater than 2n. Since the compression mechanism (15) is a two-cylinder rotary type, an exciting force of 2n acts on the compression mechanism (15). In this way, the exciting force of 2n of the two-cylinder compressor (1) and the first eigenvalue s1 can be prevented from overlapping, thereby suppressing an increase in vibration of the accumulator (2).

[0096] (8-6) Feature 6 In the present embodiment, the second eigenvalue s2 is greater than 2n, and the first connection portion (82a) which is the connection portion between the first outlet pipe (65a) and the second casing (60) and the second connection portion (82b) which is the connection portion between the second outlet pipe (65b) and the second casing (60) are located at positions offset from the cylindrical axis center of the second casing (60). By offsetting the first connection portion (82a) and the second connection portion (82b) from the cylindrical axis center of the second casing (60) in this manner, it is possible to prevent the second eigenvalue s2 from overlapping with n·N, which is an integer multiple of n.

[0097] (8-7) Feature 7 The compressor unit (U) of this embodiment further includes a second adjuster (68) that adjusts the second eigenvalue s2. The second adjuster (68) can prevent the second eigenvalue s2 from overlapping with n·N.

[0098] (8-8) Feature 8 The second adjustment part (68) of the present embodiment is a support member (68) that supports the first outlet pipe (65a) and the second outlet pipe (65b) in the second casing (60). In this manner, the second eigenvalue s2 can be easily adjusted by setting the shape and the attachment position of the support member (68).

[0099] (8-9) Feature 9: The compressor (1) of this embodiment rotates at a rotation speed of 120 rps or more. This can improve the effect of suppressing vibration of the accumulator (2), which increases at a rotation speed of 120 rps or more, particularly 150 rps.

[0100] (10) Modifications Modifications of the compressor unit (U) of the above embodiment will be described. Only the configurations that differ from the compressor unit (U) of the above embodiment will be described below, and descriptions of other configurations will be omitted.

[0101] (10-1) Modification 1 As shown in FIG. 6 , in a compressor unit (U) of Modification 1, the outlet pipes (65a, 65b) have a first pipe section (80a) and a second pipe section (80b) having different pipe thicknesses. The first pipe section (80a) and the second pipe section (80b) are continuous with each other in the outlet pipes (65a, 65b). The first pipe section (80a) and the second pipe section (80b) are formed in the first outlet pipe (65a) and the second outlet pipe (65b), respectively. In this modification, the first outlet pipe (65a) and the second outlet pipe (65b) are formed from the first pipe section (80a) and the second pipe section (80b). The lower end of the first pipe section (80a) is connected to the upper end of the second pipe section (80b). In this manner, the refrigerant in the accumulator (2) flows from the first pipe portion (80a) to the second pipe portion (80b).

[0102] Here, the thickness of a pipe is the difference between the outer radius and the inner radius of the pipe. The thickness of the first pipe section (80a) is smaller than the thickness of the second pipe section (80b). In this modification, the first pipe section (80a) and the second pipe section (80b) have the same inner diameter, and the outer diameter of the second pipe section (80b) is larger than the outer diameter of the first pipe section (80a). In this manner, the first outlet pipe (65a) and the second outlet pipe (65b) are formed so that the thickness of the pipe changes in the direction of extension of each pipe. In this modification, a transition section (90) where the pipe thickness changes is formed with a step section (91) where the outer diameter increases. The transition section (90) and the step section (91) are formed at the upper end of the second pipe section (80b). The transition section (90) and the step section (91) are formed inside the second casing (60). The transitional portion (90) and the step portion (91) are located below the height position of the center in the second casing (60).

[0103] The second adjustment portion (68) of this modification is the second pipe portion (80b). The second eigenvalue s2 can be adjusted by forming the first outlet pipe and the second outlet pipe (65b) so that the pipe thickness varies. Specifically, the second eigenvalue s2 can be set so as not to overlap with n·N by adjusting the positions of the transition portion (90) and the step portion (91) or by adjusting the pipe thickness of the second pipe portion (80b).

[0104] (10-2) Modification 2 As shown in FIG. 7 , in a compressor unit (U) of Modification 2, the shape of the outlet pipes (65a, 65b) is different from the shape of the outlet pipes (65a, 65b) of Modification 1. Specifically, the outlet pipes (65a, 65b) have an upper pipe portion (92) and a lower pipe portion (93). The upper pipe portion (92) is formed linearly. The lower pipe portion (93) has a linear portion and a curved portion. The upper pipe portion (92) and the lower pipe portion (93) are connected to each other so that the upper pipe portion (92) is located above the lower pipe portion (93) in the second casing (60), thereby forming the outlet pipes (65a, 65b). Specifically, the outer diameter of the upper pipe portion (92) is approximately the same as the inner diameter of the second outlet pipe (65b). As a result, the lower part of the upper pipe part (92) is inserted into and fixed to the upper part of the lower pipe part (93), thereby connecting the upper pipe part (92) and the lower pipe part (93). The upper pipe part (92) and the lower pipe part (93) may also be fixed to each other by press-fitting or welding.

[0105] In the outlet pipe (65a, 65b) of this modification, a portion where the upper pipe portion (92) is fitted into the lower pipe portion (93) is thick. In other words, the thickness of the pipe at the portion where the upper pipe portion (92) contacts the lower pipe portion (93) is greater than that of the other portions. Therefore, in this modification, the second pipe portion (80b) is the portion where the upper pipe portion (92) and the lower pipe portion (93) contact each other. The first pipe portion (80a) is the portion of the upper pipe portion (92) that is not in contact with the lower pipe portion (93) and the portion of the lower pipe portion (93) that is not in contact with the upper pipe portion (92). The second adjustment portion (68) of this modification is the second pipe portion (80b). The transition portion (90) and the step portion (91) of this modification are formed at the lower end of the upper pipe portion (92) and the upper end of the lower pipe portion (93).

[0106] (11) Other Embodiments The above-described embodiments may be configured as follows.

[0107] The compressor unit (U) may have either the first adjustment section (64) or the second adjustment section (68).

[0108] The compressor (1) may be a rotary compressor having one cylinder. In this case, N is an integer equal to or greater than 1. The accumulator (2) is connected to one outlet pipe (65a, 65b). Even in this case, the connection portions (82a, 82b) of the outlet pipe (65a, 65b) are formed at positions offset from the center of the cylinder axis of the second body portion (61).

[0109] In the embodiment, the first adjustment part (64) may include a structure other than the fixing member (64). The second adjustment part (68) may include a structure other than the support member (68).

[0110] In an embodiment, the accumulator (2) may be fixed to the compressor (1) by a belt. Specifically, the belt is attached so as to be wound around the second casing (60) of the accumulator (2) in the circumferential direction. In this manner, the belt comes into contact with the circumferential surface of the second casing (60), thereby fixing the accumulator (2) to the compressor (1). In this case, the first adjustment unit (64) may be a belt. By adjusting the position where the belt is provided in the second casing, the size of the belt, and the like, the first eigenvalue s1 can be prevented from overlapping with n·N.

[0111] In the embodiment, the outlet pipes (65a, 65b) may not be connected to a joint pipe such as the suction pipes (14a, 14b). For example, the outlet pipes (65a, 65b) may be connected to the first body portion (11) by welding.

[0112] In this modification, since the second eigenvalue s2 can be adjusted by changing the pipe thickness of the outlet pipes (65a, 65b), the second adjustment portion (68) may be the first pipe portion (80a). Furthermore, the outlet pipes (65a, 65b) may have a transition portion where the pipe thickness changes. The step portion (91) of the first modification may be formed inside the outlet pipes (65a, 65b). That is, the outlet pipes (65a, 65b) may be formed so that the outer diameter does not change but the inner diameter changes along the pipe extension direction. Furthermore, in the first modification, two or more transition portions (90) may be formed. For example, the first pipe portion (80a) and the second pipe portion (80b) may be formed alternately and continuously.

[0113] In the embodiment, the first adjustment portion (64) may be the extension portion (64c) of the fixed member (64). In this case, the shape of the extension portion (64c) and the length from the first fixed portion (64a) to the second fixed portion (64b) are set so that the first eigenvalue s1 does not coincide with the value of n·N.

[0114] In the embodiment, the first fixed portion (64a) may be fixed to the outer peripheral surface of the second body portion (61) by brazing. Alternatively, the fixing member (64) may be provided in the compressor unit (U) such that the first fixed portion (64a) is fixed to the first body portion (11) and the second fixed portion (64b) is fixed to the second body portion (61).

[0115] In the embodiment, the first adjustment portion (64) may be a bent portion connecting the extension portion (64c) and the second fixed portion (64b).

[0116] Although the embodiments and modifications have been described above, it will be understood that various modifications in form and detail are possible without departing from the spirit and scope of the claims. Furthermore, the above embodiments and modifications may be combined or substituted as appropriate as long as the functionality of the subject matter of the present disclosure is not impaired. The terms "first," "second," etc., described above, are used to distinguish the terms to which these terms are attached, and do not limit the number or order of the terms.

[0117] INDUSTRIAL APPLICABILITY As described above, the present disclosure is useful for compressor units and refrigeration devices.

[0118] REFRIGERATION SYSTEM U COMPRESSOR UNIT 100 REFRIGERATION APPARATUS U COMPRESSOR UNIT 150 REFRIGERATION APPARATUS U ...

Claims

1. A compressor (1) comprising: an accumulator (2) adjacent to the compressor (1), wherein the compressor (1) comprises: a first casing (10) having a cylindrical first body (11); an electric motor (20) housed in the first casing (10); a drive shaft (70) driven by the electric motor (20); and a rotary compression mechanism (15) that compresses a fluid; and the accumulator (2) comprises: a second casing (60) having a cylindrical second body (61) horizontally adjacent to the first casing (10); and outlet pipes (65a, 65b) extending from a lower part of the second casing (60) and connected to the first body (11), wherein: when the direction in which the second body (61) advances so as to roll circumferentially on the outer circumferential surface of the first body (11) is defined as the rolling direction, A compressor unit in which a first eigenvalue s1 of the rolling direction of the accumulator (2) does not overlap with a value of n·N (N is an integer) that is an integer multiple of the maximum rotation speed n of the compressor (1).

2. The compressor unit according to claim 1, wherein the first eigenvalue s1 satisfies n·N+n / 4≦s1≦n·N+3n / 4.

3. The compressor unit according to claim 1 or 2, further comprising a first adjusting section (64) that adjusts the first eigenvalue s1.

4. The compressor unit according to claim 3, wherein the first adjustment portion (64) is a plate-shaped fixed member (64) that fixes the compressor (1) and the accumulator (2), the fixed member (64) has a bent portion (64d) formed so that the plate is bent between the first body portion (11) and the second body portion (61), and the shape of the bent portion (64d) or the position of the bent portion (64d) on the fixed member (64) is determined so that the first eigenvalue s1 does not overlap the value of n·N.

5. The compressor unit according to any one of claims 1 to 4, wherein the compression mechanism (15) is a two-cylinder rotary compression mechanism, and the first eigenvalue s1 is greater than 2n.

6. The compressor unit according to any one of claims 1 to 5, wherein the outlet pipes (65a, 65b) have a first outlet pipe (65a) and a second outlet pipe (65b) extending side by side from a lower part of the accumulator (2), a second characteristic value s2 of the outlet pipes (65a, 65b) is greater than 2n, and a first connection part (82a) which is a connection part between the first outlet pipe (65a) and the second casing (60) and a second connection part (82b) which is a connection part between the second outlet pipe (65b) and the second casing (60) are located at positions deviated from the center of the cylindrical axis of the second casing (60).

7. The compressor unit according to claim 6, further comprising a second adjusting section (68) that adjusts the second eigenvalue s2.

8. A compressor unit according to claim 7, wherein the second adjustment portion (68) is a support member (68) that supports the outlet pipes (65a, 65b) within the second casing (60).

9. The compressor unit according to claim 8, wherein the outlet pipe (65a, 65b) has a first pipe section (80a) and a second pipe section (80b) having different pipe thicknesses, the first pipe section (80a) and the second pipe section (80b) are continuous with each other in the outlet pipe (65a, 65b), and the second adjustment section (68) is the first pipe section (80a) or the second pipe section (80b).

10. A compressor unit according to any one of claims 1 to 9, wherein the compressor (1) rotates at a rotation speed of 120 rpm or more.

11. A refrigeration system comprising a compressor unit according to any one of claims 1 to 10.

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