Compressor unit

Abstract

To suppress vibration of an accumulator caused by operation of a compressor.SOLUTION: A compressor unit includes a compressor (1) and an accumulator (2) adjacent to the compressor (1), and the compressor (1) includes a first casing (10) having a cylindrical first body portion (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. An accumulator (2) has a second casing (60) having a tubular second body section (61) horizontally adjacent to the first casing (10), and also has outlet pipes (65a, 65b) extending from the lower part of the second casing (60) and connected to the first body section (11), wherein a first eigenvalue (s1) in the rolling direction of the accumulator (2) does not overlap with a value of n·N (where N is an integer) which is an integer multiple of the maximum rotational speed (n) of a compressor (1).SELECTED DRAWING: Figure 2

Description

Technical Field

[0006] , , , , , , ,

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

Background Art

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

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] When the compressor is operated, vibration and noise of the accumulator may occur due to resonance. In Patent Document 1, by adjusting the position of the bracket, vibration and noise of the accumulator generated by the operation of the compressor are suppressed, but it cannot be said to be sufficient.

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

Means for Solving the Problems

[0006] The first aspect is a compressor (1) and an accumulator (2) adjacent to the compressor (1), wherein the compressor (1) has a first casing (10) having a cylindrical first body portion (11), a motor (20) housed in the first casing (10), a drive shaft (70) driven by the motor (20), It has a rotary compression mechanism (15) for compressing the fluid, The accumulator (2) is A second casing (60) having a cylindrical second body portion (61) adjacent to the first casing (10) in the horizontal direction, It has outlet pipes (65a, 65b) that extend from the lower part of the second casing (60) and are connected to the first body portion (11), When the direction in which the second body portion (61) moves along the outer circumferential surface of the first body portion (11) is defined as the direction of rolling, The first eigenvalue s1 of the accumulator (2) in the rolling direction does not coincide with a value of n·N (where N is an integer), which is an integer multiple of the maximum rotational speed n of the compressor (1). This is a compressor unit.

[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 by rolling along the outer surface of the compressor casing. It has been found that when this vibration mode coincides with an integer multiple of the maximum rotational speed n of the compressor (1), the vibration of the accumulator increases. Therefore, in the first embodiment, since the first eigenvalue does not coincide with n·N, this increase in vibration can be suppressed.

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

[0009] While the oscillation increases as the first eigenvalue s1 approaches an integer multiple of n, in the second embodiment, the first eigenvalue s1 can be set to a value relatively far from an integer multiple of n. This improves the oscillation reduction effect.

[0010] A third aspect is a manifestation of the first or second aspect, The system further includes a first adjustment unit (64) for adjusting the first eigenvalue s1.

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

[0012] A fourth aspect is, in the third aspect, The first adjustment unit (64) is a plate-shaped fixing member (64) that fixes the compressor (1) and the accumulator (2), The fixing member (64) has a bent portion (64d) formed so that the plate bends 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) on the fixing member (64) is determined such that the first eigenvalue s1 does not overlap with the value of n·N.

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

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

[0015] In the fifth embodiment, since the compression mechanism (15) is a two-cylinder rotary type, an excitation force of 2n acts on it. In this way, the excitation force of 2n of the two-cylinder compressor (1) and the first eigenvalue s1 are made so as not to overlap, and thus the increase in vibration of the accumulator (2) can be suppressed.

[0016] The sixth aspect is as described in the fifth aspect. The outlet pipes (65a, 65b) have a first outlet pipe (65a) and a second outlet pipe (65b) that extend side by side from the lower part of the accumulator (2), The second eigenvalue s2 of the aforementioned outlet pipes (65a, 65b) is greater than 2n. The first connection portion (82a), which is the connection between the first outlet pipe (65a) and the second casing (60), and the second connection portion (82b), which is the connection between the second outlet pipe (65b) and the second casing (60), are located off-center from the cylindrical axis of the second casing (60).

[0017] In the sixth aspect, by shifting the first connection part (82a) and the second connection part (82b) from the center of the cylinder axis of the second casing (60), the second eigenvalue s2 can be made not to overlap with n·N.

[0018] The seventh aspect is based on the sixth aspect, and further includes a second adjustment part (68) for adjusting the second eigenvalue s2.

[0019] In the seventh aspect, the second adjustment part (68) can make the second eigenvalue s2 not overlap with n·N.

[0020] The eighth aspect is based on the seventh aspect, and the second adjustment part (68) is a support member (68) that supports the outlet pipes (65a, 65b) within the second casing (60).

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

[0022] The ninth aspect is based on the seventh aspect, the outlet pipes (65a, 65b) have a first pipe part (80a) and a second pipe part (80b) with different wall thicknesses, in the outlet pipes (65a, 65b), the first pipe part (80a) and the second pipe part (80b) are continuous, and the second adjustment part (68) is the first pipe part (80a) or the second pipe part (80b).

[0023] In the ninth aspect, by providing the outlet pipes (65a, 65b) with the first pipe part (80a) and the second pipe part (80b) having different wall thicknesses, the eigenvalue of the outlet pipes (65a, 65b) can be adjusted. That is, in the outlet pipes (65a, 65b), by setting the positions and wall thicknesses of the first pipe part (80a) and the second pipe part (80b), the second eigenvalue s2 can be easily adjusted.

[0024] The tenth aspect is one of the first to ninth aspects, The compressor (1) rotates at a rotational speed of 120 rps or more.

[0025] In the tenth embodiment, the effect of suppressing vibrations of the accumulator (2), which increase at rotational speeds of 120 rps or more, and especially at 150 rps, can be improved.

[0026] The eleventh embodiment is a refrigeration system comprising a compressor unit according to any one of the first to tenth embodiments.

[0027] In the eleventh embodiment, a refrigeration system can be provided that can reduce vibrations of the accumulator (2) generated by the operation of the compressor (1). [Brief explanation of the drawing]

[0028] [Figure 1] Figure 1 is a piping diagram of a refrigeration system according to an embodiment. [Figure 2] Figure 2 shows a cross-sectional view obtained by cutting the compressor unit according to the embodiment in the vertical direction. [Figure 3] Figure 3 is a plan view of the piston of the compression mechanism. (A) is a plan view of the first compression mechanism. (B) is a plan view of the second compression mechanism. [Figure 4] Figure 4 shows the shape of the fixing member. (A) is a view from above of a part of the state in which the compressor and accumulator are fixed by the fixing member. (B) is a view of the first surface of the fixing member from the front. [Figure 5] Figure 5 shows the operation of the compression mechanism. [Figure 6] Figure 6 shows a cross-section of the accumulator according to Modification 1, obtained by cutting it vertically. [Figure 7] Figure 7 shows a cross-section of the accumulator according to Modification 2, obtained by cutting it vertically. [Modes for carrying out the invention]

[0029] Embodiments of the present invention will be described below with reference to the drawings. 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, the embodiments, modifications, and other examples described below can be combined or partially replaced to the extent that the present invention is implementable.

[0030] (1) Compressor unit As shown in Figure 1, the compressor unit (U) of this embodiment is applied to a refrigeration system (100). The refrigeration system (100) is, for example, an air conditioning system that air-conditions a room. The refrigeration system (100) includes a refrigerant circuit (9) that performs a refrigeration cycle. The refrigerant circuit (9) has refrigerant piping (9a) through which the 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 piping (9a). The compressor unit (U) of this embodiment includes a compressor (1) and an accumulator (2).

[0031] The four-way directional control valve (3) has four ports (P1, P2, P3, P4). The four-way directional control valve (3) switches the flow path of the refrigerant circuit (9) between the solid line state and the dashed line state in Figure 1. This switches the refrigerant circuit (9) 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 installed in the outdoor unit (not shown) located outside. The outdoor heat exchanger (4) exchanges heat between the refrigerant and the outside air. The outdoor heat exchanger (4) functions as a heat radiator in the first refrigeration cycle and as an evaporator in the second refrigeration cycle.

[0033] The expansion valve (5) reduces the refrigerant pressure in the refrigerant circuit. The expansion valve (5) is, for example, an electronically controlled expansion valve with an adjustable opening.

[0034] The indoor heat exchanger (6) is installed in an indoor unit (not shown) located inside the room. 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 heat radiator in the second refrigeration cycle.

[0035] (2) Compressor The compressor (1) is a rotary compressor. The compressor (1) compresses the refrigerant flowing through the 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 inside the first casing (10). The compressor (1) is configured as a so-called high-pressure dome type, in which the refrigerant compressed in the compression mechanism (15) is discharged into the internal space of the first casing (10), and the internal space becomes high pressure.

[0036] (2-1) First casing The first casing (10) is a vertically elongated, sealed metal container. The first casing (10) has a cylindrical first body (11) extending vertically, an upper end plate (12) that closes the upper end of the first body (11), and a lower end plate (13) that closes the lower end of the first body (11). A discharge pipe (8) is connected to the upper end plate (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) constitutes the side surface of the first casing (10).

[0037] (2-2) Electric motor The electric motor (20) is located in the upper part of the internal space of the first casing (10). The electric motor (20) comprises a stator (21) and a rotor (22). The stator (21) is fixed to the first body (11). The rotor (22) is attached to the drive shaft (70) of the compression mechanism (15), which will be described later. The drive shaft (70) is arranged to extend vertically within the first casing (10). The drive shaft (70) is driven by the electric motor (20). The upper part of the drive shaft (70) is connected to the rotor (22) of the electric motor (20). Details of the drive shaft (70) will be described later.

[0038] (2-3) Compression mechanism The compression mechanism (15) is a so-called oscillating piston type rotary fluid machine. The compression mechanism (15) in 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 located below the electric motor (20).

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

[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 motor (20) side (the upper end face of the first cylinder (30) in Figure 1). The front head (24) is fixed to the inner surface of the first body (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). The front head (24) has a discharge port (not shown) formed therein for discharging refrigerant from the cylinder chamber (S), which will be described later.

[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 Figure 1). The rear head (25) has a sub-bearing section (27). The sub-bearing section (27) is a journal that supports the drive shaft (70) of the compression mechanism (15) It constitutes a bearing. The rear head (25) has a discharge port (not shown) for discharging refrigerant from the cylinder chamber (S) described later.

[0042] (2-3-3) Cylinder and Piston As shown in Figure 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 disc-shaped member. The thickness of each cylinder (30, 35) is equal. Each cylinder (30, 35) has a cylinder bore (31, 36) and a blade housing hole (32, 37) formed within it.

[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] The first cylinder bore (31) houses the first piston (40). The second cylinder bore (36) houses the second piston (45). 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). Thus, the first cylinder (30) has a 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). Thus, the second cylinder (35) has a second cylinder chamber (S).

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

[0048] The first cylinder (30) is provided with a first inhalation port (33). The second cylinder (35) is provided with a second inhalation port (38). The first inhalation port (33) is connected to a first inhalation tube (14a). The second inhalation port (38) is connected to a second inhalation tube (14b). Each inhalation port (33, 38) communicates with the first chamber (S1) of the cylinder chamber (S). Each inhalation port (33, 38) is located to the right of the blade housing holes (32, 37) when viewing the cylinders (30, 35) shown in Figure 4 from above. The discharge port is located to the left of the blade housing holes (32, 37) (not shown).

[0049] The pistons (40, 45) shown in Figure 3 rotate eccentrically within the cylinders (30, 35). The first piston (40) and the second piston (45) are identical in shape, dimensions, and material. Each piston (40, 45) is a slightly thick-walled cylindrical component.

[0050] The first piston (40) has the first eccentric portion (75) of the drive shaft (70) inserted through it. The first piston (40) rotates eccentrically as the first eccentric portion (75) of the drive shaft (70) rotates. The second eccentric portion (76) of the drive shaft (70) has the second piston (45) inserted through it. 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 slightly thick rectangular flat plate-shaped member. The first blade (41) is formed integrally with the first piston (40). The first blade (41) is positioned in the first blade housing hole (32). The first blade (41) divides the first cylinder chamber (S) into a first chamber (S1) on the intake side and a second chamber (S2) on the discharge side. The second blade (46) is positioned in the second blade housing hole (37). The second blade (46) divides the second cylinder chamber (S) into a first chamber (S1) on the intake side and a second chamber (S2) on the discharge side.

[0052] Each blade (41, 46) is sandwiched between a pair of bushings (42, 47). Each blade (41, 46) is pivotably and reciprocally supported by the cylinders (30, 35) via the bushings (42, 47).

[0053] (2-3-4) Intermediate plate The intermediate plate (50) shown in Figure 2 is positioned 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 center of the intermediate plate (50), penetrating the intermediate plate (50) in the thickness direction. The intermediate connecting portion (78) of the drive shaft (70) is inserted through 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 component that drives the pistons (40, 45). Specifically, the drive shaft (70) comprises a main shaft portion (72), a first eccentric portion (75), an intermediate connecting portion (78), a second eccentric portion (76), and a sub-shaft portion (74), arranged in order from top to bottom. The rotational axis (70a) of the drive shaft (70) substantially coincides with the central axis of the cylinder bore (31, 36) of each cylinder (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 secondary shaft (74) is supported by the secondary bearing (27) of the rear head (25).

[0057] The first eccentric portion (75) and the second eccentric portion (76) are cylindrical parts with a larger diameter than 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 rotational axis (70a) of the drive shaft (70). The first eccentric portion (75) is eccentric with respect to the rotational axis (70a) of the drive shaft (70) in the opposite direction to the second eccentric portion (76). In other words, the direction of eccentricity of the first eccentric portion (75) with respect to the rotational axis (70a) of the drive shaft (70) is 180° different from the direction of eccentricity of the second eccentric portion (76) with respect to the rotational axis (70a) of the drive shaft (70).

[0058] The intermediate connecting section (78) is positioned between the first eccentric section (75) and the second eccentric section (76), and connects the first eccentric section (75) and the second eccentric section (76).

[0059] (3) Accumulator The accumulator (2) shown in Figures 1 and 2 temporarily stores the refrigerant drawn in by the compressor (1). The accumulator (2) separates the gas from the liquid. Specifically, the accumulator (2) separates the liquid refrigerant and refrigerant oil contained in the gaseous refrigerant. The accumulator (2) is positioned adjacent to the compressor (1). The accumulator (2) comprises a second casing (60), outlet pipes (65a, 65b), and fixing members (64).

[0060] (3-1) Second casing The second casing (60) is a vertically elongated, sealed metal container. The second casing (60) has a vertically extending cylindrical second body (61), an upper lid (81) that closes the upper end of the second body (61), and a lower lid (82) that closes the lower end of the second body (61). The second casing (60) is adjacent to the first casing (10) in the horizontal direction. Specifically, the second body (61) is positioned 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] The second body portion (61) in this example has an upper body portion (61a) and a lower body portion (61b). The upper body portion (61a) and the upper lid portion (81) are formed integrally. The lower body portion (61b) and the lower lid portion (82) are formed integrally. The upper end of the lower body portion (61b) is fitted into the lower end of the upper body portion (61a).

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

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

[0064] (3-2) Outlet pipe The outlet pipes (65a, 65b) are pipes that extend from the lower part of the second casing (60) and are connected to the side of the first casing (10). The outlet pipes (65a, 65b) consist of 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 connector (82a). The first outlet pipe (65a) is fixed to the first connector (82a), for example, by welding. One end of the first outlet pipe (65a), the upper end, extends along the axial direction of the cylinder from the first connector (82a) to the upper part inside the second casing (60). The other end of the first outlet pipe (65a) is connected to the first intake pipe (14a). The first outlet pipe (65a) extends downward from the first connector (82a) and then extends horizontally toward the first intake pipe (14a).

[0066] The second outlet pipe (65b) is inserted through the second connector (82b). The second outlet pipe (65b) is fixed to the second connector (82b), for example, by welding. One end of the second outlet pipe (65b) extends along the axial direction from the second connector (82b) to the upper part inside the second casing (60). 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 connector (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 at approximately the same height.

[0067] (3-3) Fixing members As shown in Figures 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 section (11) and the second body section (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 circumferential surface of the second body portion (61), two second fixing portions (64b) fixed to the outer circumferential surface of the first body portion (11), and an extension portion (64c) extending from the first fixing portion (64a) to the second fixing portions (64b).

[0069] The first fixing portion (64a) is formed to curve along the outer circumferential 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 circumferential surface of the second body portion (61).

[0070] The extension portion (64c) connects the first fixing portion (64a) and the second fixing portion (64b). The extension portion (64c) is provided so as to extend from both ends of the first fixing portion (64a) in the circumferential direction of the second body portion (61) toward the outer circumferential surface of the first body portion (11). The extension portion (64c) has a bent portion (64d). The bent portion (64d) constitutes the connection portion between the connecting portions (82a, 82b) and the first fixing portion (64a). The bent portion (64d) is formed so as to bend from both ends of the first fixing portion (64a) toward the outer circumferential surface of the first body portion (11). A predetermined bending radius is set for the bent portion (64d). In this way, the fixing member (64) has a bent portion (64d). The bent portion (64d) is formed so that the plate bends 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) along the circumferential direction of the first body portion (11). The surface of the second fixing portion (64b) facing the first body portion (11) is in contact with the outer circumferential surface of the second body portion (61). In this way, the two second fixing portions (64b) are fixed to the second body portion (61) so as to sandwich the first body portion (11).

[0072] Welding protrusions (66) are formed on the first fixing portion (64a) (Figure 4(B)). In this embodiment, four protrusions (66) are formed on the surface of the first fixing portion (64a) facing the second body portion (61). By melting these protrusions (66), the first fixing portion (64a) is fixed to the first body portion (11). There may be two protrusions (66) formed on the first fixing portion (64a).

[0073] (3-4) Support members As shown in Figure 2, the support member (68) supports the outlet pipes (65a, 65b) within the second casing (60). The support member (68) is fixed within the second casing (60). The support member (68) is in contact with the upper parts of the first outlet pipe (65a) and the second outlet pipe (65b). As a result, the first outlet pipe (65a) is fixed within the second casing (60) by the first connector (82a) and the support member (68). The second outlet pipe (65b) is fixed within the second casing (60) by the second connector (82b) and the support member (68).

[0074] (4) Operation of the compressor The operation of the compressor (1) will be explained using 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 processes of drawing in, compressing, and discharging refrigerant are performed in both the first compression mechanism (K1) and the second compression mechanism (K2).

[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), an intake stroke is performed in which refrigerant is drawn into the cylinder chamber (S,S) from the intake 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 to the outside of the cylinder chamber (S,S) from the discharge port.

[0076] Here, the angles shown in Figure 5 are defined as the rotation angle of the drive shaft (70) at the position where the first blade (41) of the first compression mechanism (K1) is furthest back from the first cylinder (30), with 0°, and the rotation angle of the drive shaft (70) at the position where the first blade (41) of the first compression mechanism (K1) is furthest inside the first cylinder (30). Let the rotation angle be 180°.

[0077] The eccentricity direction of the first piston (40) relative to the rotational axis (70a) of the drive shaft (70) is 180° different from the eccentricity direction of the second piston (45) relative to the rotational axis (70a) of the drive shaft (70). Therefore, the displacement period of the first piston (40) and the displacement period of the second piston (45) are out of sync by 180° (i.e., half a period). Below, the operation of the first compression mechanism (K1) will be described, and the operation of the second compression mechanism (K2) will be omitted.

[0078] (5) Operation of the first compression mechanism (5-1) Inhalation process When the drive shaft (70) rotates slightly clockwise from a rotation angle of 0° as shown in Figure 5, the contact point between the first piston (40) and the first cylinder (30) passes through the first intake port (33). At this time, the intake 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 intake stroke continues until the rotation angle of the drive shaft (70) reaches 360°, after which the process transitions to the discharge stroke.

[0080] (5-2) Discharge process When the drive shaft (70) rotates slightly from a rotation angle of 0°, the contact point between the first piston (40) and the first cylinder (30) passes through the first intake port (33) again. At this point, the refrigerant is contained in the first chamber (S1), and the first chamber (S1), which was connected to the first intake port (33), becomes the second chamber (S2), which is connected only to the discharge port.

[0081] From this state, compression of the refrigerant in the second chamber (S2) begins. 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 refrigerant discharge stroke continues until the rotation angle of the drive shaft (70) reaches 360°, after which it transitions to the suction stroke. In this way, the refrigerant compression operation is continuously performed in the first compression mechanism (K1) by alternating between the suction stroke and the discharge stroke.

[0083] (6) Issues related to vibrations caused by compressor operation In a compressor unit comprising 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 direction in which it rolls along the outer surface of the compressor in the circumferential direction of the compressor. Regarding the eigenvalues ​​of the accumulator, the first and second modes have eigenvalues ​​around 500Hz to 2000Hz, while the third mode often has eigenvalues ​​around 200Hz to 300Hz. When the compressor is in operation, not only are noises generated by the first and second modes, but the accumulator vibrates by the third mode, which could lead to damage to the refrigerant pipes and outlet pipes.

[0084] In addition, the vibration mode of the accumulator's outlet tube may have an eigenvalue in the same frequency band as the third mode. Therefore, when the vibration mode of the outlet tube and the third mode overlap, the vibration of the accumulator becomes larger.

[0085] Furthermore, in the case of a rotary compressor having two cylinders, an excitation force of 2n (n: compressor rotation speed) acts on the compressor due to torque fluctuations and vibrations of the drive shaft caused by the rotation of the drive shaft. In particular, in small high-speed compressors, the natural value of the drive shaft decreases due to the reduction in the diameter of the drive shaft. As a result, it has been found that when the compressor rotation speed reaches 120 rpm or higher, especially 150 rpm, the frequency bands of the excitation force of 2n, the third mode, and the vibration mode of the outlet pipe become close together, increasing the 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 natural value.

[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) moves so as to roll along the outer circumferential surface of the first casing (10). In this embodiment, the first adjustment unit (64) is a fixing member (64). The fixing member (64) adjusts the first eigenvalue s1 so as not to be an integer multiple of the maximum rotational speed n of the compressor (1), which is n·N (where N is an integer). Here, since the compressor in this embodiment is a 2-cylinder rotary compressor, N=2. Therefore, the fixing member (64) adjusts the first eigenvalue s1 so as to be greater than 2n.

[0087] Specifically, the fixing member (64) is adjusted so that the first eigenvalue s1 satisfies the target range. The target range for the first eigenvalue s1 is n·N+n / 4≦s1≦n·N+3n / 4 (N≧2). The fixing member (64) is formed 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 at this time, 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 satisfies the target range. Also, the bent portion (64d) is formed at a position on the fixing member (64) such that the first eigenvalue s1 satisfies the target range. In this way, since the fixing member (64) is formed so that the first eigenvalue s1 satisfies the target range during the manufacture of the compressor unit (U), a compressor unit (U) that can suppress vibration can be easily manufactured. Furthermore, the natural frequency or vibration can be determined by known test or measurement methods.

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

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

[0090] (8) Characteristics (8-1) Feature 1 In this embodiment, the compressor unit (U) has a first eigenvalue s1 in the rolling direction of the accumulator (2) that does not coincide with a value n·N (where N is an integer), which is an integer multiple of the maximum rotational speed n of the compressor (1). As a result, the third vibration mode and the 2n excitation do not overlap, and vibration of the accumulator can be suppressed. Consequently, noise generated from the refrigeration system (100) due to the 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 prevented.

[0091] (8-2) Feature 2 The first eigenvalue s1 of this embodiment satisfies n·N+n / 4≦s1≦n·N+3n / 4. Since the excitation force acts on the compressor (1) at integer multiples of the maximum rotational speed n of the compressor (1), the first eigenvalue s1 is in the range furthest from integer multiples of n, thus improving the vibration suppression effect of the accumulator (2).

[0092] (8-3) Feature 3 The compressor unit (U) of this embodiment includes a first adjustment unit (64) for adjusting the first eigenvalue s1. This allows the first eigenvalue s1 to be adjusted to a desired value, making it possible to easily suppress vibrations of the accumulator (2) without considering its shape, size, or arrangement.

[0093] (8-4) Feature 4 The first adjustment section (64) of this embodiment includes a fixing member (64) having a bent portion (64d) formed so that the plate bends 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) on the fixing member (64) is determined so that the first eigenvalue s1 does not overlap with the value of n·N.

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

[0095] (8-5) Feature 5 This embodiment is a two-cylinder rotary compression mechanism, and the first eigenvalue s1 is greater than 2n. Since the compression mechanism (15) is a two-cylinder rotary type, an excitation force of 2n acts on it. In this way, the excitation force of 2n of the two-cylinder compressor (1) and the first eigenvalue s1 are made not to overlap, so that the increase in vibration of the accumulator (2) can be suppressed.

[0096] (8-6) Feature 6 In this embodiment, the second eigenvalue s2 is greater than 2n, and the first connection part (82a), which is the connection between the first outlet pipe (65a) and the second casing (60), and the second connection part (82b), which is the connection between the second outlet pipe (65b) and the second casing (60), are located off-center from the cylindrical axis of the second casing (60). By offsetting the first connection part (82a) and the second connection part (82b) from the cylindrical axis of the second casing (60) in this way, the second eigenvalue s2 can be prevented from coinciding 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 adjustment unit (68) for adjusting the second eigenvalue s2. The second adjustment unit (68) ensures that the second eigenvalue s2 does not overlap with n·N.

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

[0099] (8-9) Feature 9 The compressor (1) in this embodiment rotates at a rotational speed of 120 rps or more. This improves the effect of suppressing vibrations of the accumulator (2), which increase at rotational speeds of 120 rps or more, especially at 150 rps.

[0100] (10) Variations A modified version of the compressor unit (U) of the above embodiment will be described below. In the following, only the configurations that differ from the compressor unit (U) of the above embodiment will be described, and other details will be omitted.

[0101] (10-1) Experiment 1 As shown in Figure 6, in the compressor unit (U) of Modified Example 1, the outlet pipe (65a, 65b) has a first pipe section (80a) and a second pipe section (80b) with different pipe thicknesses. The first pipe section (80a) and the second pipe section (80b) are continuous in the outlet pipe (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 modified example, the first outlet pipe (65a) and the second outlet pipe (65b) are composed of a first pipe section (80a) and a 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 way, the refrigerant in the accumulator (2) flows from the first pipe section (80a) to the second pipe section (80b).

[0102] Here, the thickness of the 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 modified example, the inner diameters of the first pipe section (80a) and the second pipe section (80b) are the same, and the outer diameter of the second pipe section (80b) is larger than the outer diameter of the first pipe section (80a). Thus, the first outlet pipe (65a) and the second outlet pipe (65b) are formed such that the thickness of the pipe changes in the direction in which each pipe extends. In this modified example, a stepped section (91) with an increased outer diameter is formed at the change section (90) where the pipe thickness changes. The change section (90) and the stepped section (91) are formed at the upper end of the second pipe section (80b). The change section (90) and the stepped section (91) are formed inside the second casing (60). The modified section (90) and the stepped section (91) are positioned below the central height position within the second casing (60).

[0103] In this modified example, the second adjustment section (68) is the second pipe section (80b). The second eigenvalue s2 can be adjusted by forming the first outlet pipe and the second outlet pipe (65b) so that the thickness of the pipes changes. Specifically, by adjusting the position of the change section (90) and the step section (91), or by adjusting the thickness of the pipe in the second pipe section (80b), the second eigenvalue s2 can be made not to overlap with n·N.

[0104] (10-2) Modification 2 As shown in Figure 7, in the compressor unit (U) of Modified Example 2, the shape of the outlet pipes (65a, 65b) differs from the shape of the outlet pipes (65a, 65b) of Modified Example 1. Specifically, the outlet pipes (65a, 65b) have an upper pipe section (92) and a lower pipe section (93). The upper pipe section (92) is formed in a straight line. The lower pipe section (93) has a straight section and a curved section. The outlet pipes (65a, 65b) are formed by connecting the upper pipe section (92) and the lower pipe section (93) so that the upper pipe section (92) is positioned above the lower pipe section (93) within the second casing (60). Specifically, the outer diameter of the upper pipe section (92) is approximately the same as the inner diameter of the second outlet pipe (65b). This connects the upper pipe section (92) and the lower pipe section (93) by inserting and securing the lower portion of the upper pipe section (92) into the upper portion of the lower pipe section (93). Alternatively, the upper pipe section (92) and the lower pipe section (93) may be fixed together by press-fitting or welding.

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

[0106] (11) Other embodiments The above embodiment may also have the following configuration.

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

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

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

[0110] In one embodiment, the accumulator (2) may be fixed to the compressor (1) by a belt. Specifically, the belt is attached so as to wrap around the second casing (60) of the accumulator (2) in the circumferential direction. The belt is fixed to the compressor (1) by contacting the circumferential surface of the second casing (60) in this way. In this case, the first adjustment part (64) may be a belt. In the second casing, the position of the belt and the size of the belt can be adjusted so that the first eigenvalue s1 does not overlap with n·N.

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

[0112] In the modified example, the second eigenvalue s2 can be adjusted by changing the thickness of the pipe in the outlet pipe (65a, 65b), so the second adjustment section (68) may be the first pipe section (80a). Also, the outlet pipe (65a, 65b) only needs to have a section in which the thickness of the pipe changes. The stepped section (91) in Modified Example 1 may be formed on the inside of the outlet pipe (65a, 65b). That is, the outlet pipe (65a, 65b) may be formed such that the outer diameter does not change and the inner diameter changes in the direction in which the pipe extends. Also, in Modified Example 1, two or more sections (90) may be formed. For example, the first pipe section (80a) and the second pipe section (80b) may be formed alternately in a continuous manner.

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

[0114] In this embodiment, the first fixing portion (64a) may be fixed to the outer circumferential 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 fixing portion (64a) is fixed to the first body portion (11) and the second fixing portion (64b) is fixed to the second body portion (61).

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

[0116] While embodiments and modifications have been described above, it will be understood that a variety of changes in form and details are possible without departing from the spirit and scope of the claims. Furthermore, these embodiments and modifications may be combined or substituted as appropriate, as long as they do not impair the functions of the subject matter of this disclosure. The terms “First,” “Second,” etc., used above are used to distinguish the phrases to which these terms are attached, and do not limit the number or order of such phrases. [Industrial applicability]

[0117] As described above, this disclosure is useful for compressor units and refrigeration systems. [Explanation of symbols]

[0118] 1. Compressor 2 Accumulators 10. First casing 11 First Fuselage 15 Compression mechanism 20 Electric motor 60 Second casing 61 Second fuselage 64 Fixing member (first adjustment part) 64d bent part 65a 1st outlet pipe 65a,65b outlet pipe 65b 2nd outlet pipe 68 Support member (second adjustment section) 70 Drive shaft 80a First Pipe Section 80b 2nd pipe section 82a First connection section 82a, 82b Connection section 82b Second connection section 100 Refrigeration equipment U Compressor Unit

Claims

1. Compressor (1), The system comprises a compressor (1) and an accumulator (2) adjacent to it. The compressor (1) is A first casing (10) having a cylindrical first body portion (11), The electric motor (20) housed in the first casing (10), A drive shaft (70) driven by the aforementioned electric motor (20), It has a rotary compression mechanism (15) for compressing the fluid, The accumulator (2) is A second casing (60) having a cylindrical second body portion (61) adjacent to the first casing (10) in the horizontal direction, It has outlet pipes (65a, 65b) that extend from the lower part of the second casing (60) and are connected to the first body portion (11), When the direction in which the second body portion (61) moves so as to roll along the outer circumferential surface of the first body portion (11) is defined as the direction of rolling, The first eigenvalue s1 of the accumulator (2) in the rolling direction does not coincide with the value of n・N (where N is an integer), which is an integer multiple of the maximum rotational speed n of the compressor (1), and satisfies n・N + n / 4 ≤ s1 ≤ n・N + 3n / 4. Compressor unit.

2. The system further comprises a first adjustment unit (64) for adjusting the first eigenvalue s1. The compressor unit according to claim 1.

3. The first adjustment unit (64) is a plate-shaped fixing member (64) that fixes the compressor (1) and the accumulator (2), The fixing member (64) has a bent portion (64d) formed so that the plate bends 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) on the fixing member (64) is determined such that the first eigenvalue s1 does not overlap with the value of n・N. The compressor unit according to claim 2.

4. The compression mechanism (15) is a two-cylinder rotary compression mechanism. The first eigenvalue s1 is greater than 2n. The compressor unit according to claim 1.

5. The outlet pipes (65a, 65b) have a first outlet pipe (65a) and a second outlet pipe (65b) that extend side by side from the lower part of the accumulator (2), The second eigenvalue s2 of the aforementioned outlet pipes (65a, 65b) is greater than 2n. The first connection portion (82a), which is the connection between the first outlet pipe (65a) and the second casing (60), and the second connection portion (82b), which is the connection between the second outlet pipe (65b) and the second casing (60), are located off-center from the cylindrical axis of the second casing (60). The compressor unit according to claim 1.

6. The system further comprises a second adjustment unit (68) for adjusting the second eigenvalue s2. The compressor unit according to claim 5.

7. The second adjustment section (68) is a support member (68) that supports the outlet pipes (65a, 65b) within the second casing (60). The compressor unit according to claim 6.

8. The outlet pipe (65a, 65b) has a first pipe section (80a) and a second pipe section (80b) with different pipe thicknesses. In the outlet pipes (65a, 65b), the first pipe section (80a) and the second pipe section (80b) are continuous. The second adjustment section (68) is either the first pipe section (80a) or the second pipe section (80b). The compressor unit according to claim 7.

9. The compressor (1) rotates at a rotational speed of 120 rpm or more. The compressor unit according to claim 1.

10. A refrigeration apparatus comprising the compressor unit described in claim 1.

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