Rotary compressor and refrigeration device

Abstract

The drive shaft (25) has a main shaft section (26) and an eccentric section (27). An oil passage (30) is provided in the drive shaft (25). The oil passage (30) has one or more oil holes (31) extending in the axial direction. When viewed from the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by an imaginary envelope (40) that envelops the oil hole (31) is defined as a first direction (Y), and a direction orthogonal to the first direction (Y) is defined as a second direction (X). When viewed from the axial direction, the length of the oil passage (30) in the first direction (Y) is longer than the length in the second direction (X) in the region surrounded by the virtual envelope (40).

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a rotary compressor and a refrigeration apparatus. BACKGROUND

[0002] A compressor disclosed in Patent Literature 1 includes a compression mechanism having a rolling piston, and a drive shaft (rotary shaft) that eccentrically rotates the rolling piston. An oil passage (center hole) extending in the axial direction is formed in the drive shaft. Refrigerant oil stored in the bottom portion of a closed container is supplied to each sliding portion through the oil passage.

[0003] PRIOR ART DOCUMENTS

[0004] PATENT LITERATURE

[0005] Patent Literature 1: Japanese Patent No. 7003305 SUMMARY

[0006] PROBLEMS TO BE SOLVED BY THE INVENTION

[0007] Here, the compression mechanism is driven to rotate, and a centrifugal force and a gas load are applied to the drive shaft in association with the rotation, so there is a problem that the shaft deflection of the drive shaft becomes large.

[0008] Therefore, the present inventors focused on the oil passage as a main cause of the decrease in the rigidity of the drive shaft, and have studied to improve the rigidity of the drive shaft by improving the shape of the oil passage.

[0009] An object of the present disclosure is to improve the shape of the oil passage to suppress the shaft deflection of the drive shaft.

[0010] TECHNICAL SOLUTION TO SOLVE THE PROBLEMS

[0011] A first aspect of the present disclosure relates to a rotary compressor including a compression mechanism 50 and a drive shaft 25 that drives the compression mechanism 50 to rotate, the drive shaft 25 having a main shaft portion 26 and an eccentric portion 27 that is eccentric from a shaft center CI of the main shaft portion 26 by a prescribed amount, an oil passage 30 being provided in the drive shaft 25, the oil passage 30 having one or more oil holes 31 extending in the axial direction, a prescribed direction in an area surrounded by an imaginary envelope line 40 that envelopes the oil holes 31 when viewed in the axial direction being set as a first direction Y, and a direction orthogonal to the first direction Y being set as a second direction X, the length in the first direction Y in the area surrounded by the imaginary envelope line 40 of the oil passage 30 being longer than the length in the second direction X when viewed in the axial direction.

[0012] In the first aspect, by forming the oil passage 30 having a length in the first direction Y that is longer than a length in the second direction X in the area surrounded by the imaginary envelope line 40, it is possible to increase the rigidity of the drive shaft 25, and thus it is possible to reduce shaft deflection.

[0013] Specifically, in order to use centrifugal pumping to draw up oil, a centrifugal pump needs to include, in its structure, a small-diameter portion on the inlet side and a large-diameter portion on the outlet side, the large-diameter portion having a larger hole diameter than the small-diameter portion.

[0014] In the case of the existing rotary compressor, the small-diameter portion on the inlet side of the centrifugal pump corresponds to a suction port that is opened in a tapered shape with a narrower front end at the lower end portion of the centrifugal pump, and the large-diameter portion on the outlet side corresponds to a circular oil passage that extends in the axial direction at the central portion of the drive shaft 25. Therefore, in the existing rotary compressor, the oil passage having a large diameter is provided at the central portion of the drive shaft 25, the oil passage has a circular shape with a length in the first direction Y as a diameter, and the rigidity of the drive shaft 25 can be reduced.

[0015] In this regard, by making the length of the oil passage 30 in the second direction X shorter than the length in the first direction Y, the passage area of the oil passage 30 is smaller compared to the case where a circular oil passage is provided at the central portion of the drive shaft 25, and it is possible to increase the rigidity of the drive shaft 25 and thus reduce shaft deflection.

[0016] In addition, by ensuring that the distance from the rotational center of the drive shaft 25 to the inner wall surface of the oil passage 30 up to the radially farthest portion is equal to the radius of the circular oil passage, it is possible to obtain equivalent centrifugal pumping.

[0017] The second aspect of the present disclosure is based on the rotary compressor of the first aspect, and when viewed in the axial direction of the drive shaft 25, the first direction Y is a direction that connects the shaft center CI of the main shaft portion 26 and the shaft center C2 of the eccentric portion 27.

[0018] In the second aspect, since the rigidity of the drive shaft 25 in the second direction X is higher than the rigidity in the first direction Y, even in the case where the maximum gas load when the compression mechanism 50 is driven and rotated is applied in the second direction X of the drive shaft 25, it is possible to suppress the shaft deflection of the drive shaft 25.

[0019] The third aspect of the present disclosure is based on the rotary compressor of the first or second aspect, and when viewed in the axial direction, the oil passage 30 is formed by the long-hole-shaped oil hole 31 that extends in the first direction Y.

[0020] In the third aspect, when viewed in the axial direction, by forming the oil passage 30 by the long-hole-shaped oil hole 31 that extends in the first direction Y, it is possible to make the rigidity of the drive shaft 25 in the second direction X higher than the rigidity in the first direction Y.

[0021] The fourth aspect of the present disclosure is based on the rotary compressor of the first or second aspect, and the oil passage 30 is formed by a plurality of the oil holes 31 arranged in the first direction Y when viewed in the axial direction.

[0022] In the fourth aspect, by forming the oil passage 30 by a plurality of the oil holes 31 arranged in the first direction Y, it is possible to make the rigidity in the second direction X of the drive shaft 25 higher than the rigidity in the first direction Y.

[0023] The fifth aspect of the present disclosure is based on the rotary compressor of the fourth aspect, and a portion of the adjacent oil holes 31 in the oil passage 30 overlap each other when viewed in the axial direction.

[0024] In the fifth aspect, in a case where the length in the first direction Y of the region surrounded by the imaginary envelope line 40 is constant, the number of the oil holes 31 in the region surrounded by the imaginary envelope line 40 increases in a case where a portion of the adjacent oil holes 31 overlap each other, compared to a case where the adjacent oil holes 31 are arranged apart from each other. Thus, it is easy to process the oil passage 30 into a long hole shape.

[0025] The sixth aspect of the present disclosure is based on the rotary compressor of any one of the first to fifth aspects, and the rotary compressor includes a motor 21 that rotates the drive shaft 25, and the compression mechanism 50 is arranged at a position lower than the motor 21.

[0026] In the sixth aspect, for the rotary compressor in which the compression mechanism 50 is arranged at a position lower than the motor 21, it is possible to adopt a shape of the oil passage 30 in which the length in the first direction Y in the region surrounded by the imaginary envelope line 40 is longer than the length in the second direction X.

[0027] The seventh aspect of the present disclosure relates to a refrigeration device including the rotary compressor 10 of any one of the first to sixth aspects, and a refrigerant circuit 1a through which a refrigerant compressed by the rotary compressor 10 flows.

[0028] In the seventh aspect, it is possible to provide a refrigeration device including the rotary compressor 10 and the refrigerant circuit 1a. BRIEF DESCRIPTION OF DRAWINGS

[0029] Figure 1 is a refrigerant circuit diagram showing the structure of the refrigeration device of the present first embodiment.

[0030] Figure 2 is a longitudinal sectional view showing the structure of the rotary compressor.

[0031] Figure 3This is a cross-sectional view showing the structure of a rotary compressor.

[0032] Figure 4 This is a diagram showing the drive shaft viewed from the axial direction.

[0033] Figure 5 It is along Figure 2 A sectional view taken along line A-A of the drive shaft.

[0034] Figure 6 This is a diagram illustrating the second moment of the cross section when a load is applied to the main shaft portion of the drive shaft from the first direction.

[0035] Figure 7 This is a diagram used to illustrate the second moment of the cross section when a load is applied to the main shaft portion of the drive shaft from the second direction.

[0036] Figure 8 It is a graph showing the relationship between the angle relative to the top dead center and the magnitude of the force applied to the drive shaft.

[0037] Figure 9 It is a graph showing the relationship between the angle relative to the top dead center and the direction of the force applied to the drive shaft.

[0038] Figure 10 It is a graph showing the relationship between the angle relative to the top dead center and the direction of the force applied to the drive shaft when the eccentric direction of the eccentric part is taken as 0°.

[0039] Figure 11 This is a diagram illustrating the angle at which the maximum gas load is applied to the drive shaft.

[0040] Figure 12 This is a diagram showing the drive shaft of this second embodiment viewed from the axial direction.

[0041] Figure 13 This is a diagram showing the drive shaft of this third embodiment viewed from the axial direction.

[0042] Figure 14 This is a diagram showing the drive shaft of this fourth embodiment viewed from the axial direction.

[0043] Figure 15 This is a diagram showing the drive shaft of this fifth embodiment viewed from the axial direction.

[0044] Figure 16 This is a longitudinal sectional view showing the structure of the rotary compressor according to the sixth embodiment.

[0045] Figure 17 This is a diagram showing the structure of the drive shaft as viewed from the axial direction. Detailed Implementation

[0046] (First Implementation)

[0047] like Figure 1 As shown, a rotary compressor 10 is installed in a refrigeration unit 1. The refrigeration unit 1 has a refrigerant circuit 1a filled with refrigerant. The refrigerant circuit 1a includes the rotary compressor 10, a radiator 3, a pressure reducing mechanism 4, and an evaporator 5. The pressure reducing mechanism 4 is, for example, an expansion valve. The refrigerant circuit 1a performs a vapor compression refrigeration cycle.

[0048] Refrigeration unit 1 is an air conditioning unit. The air conditioning unit can be a dedicated refrigeration unit, a dedicated heating unit, or an air conditioning unit that switches between refrigeration and heating. In this case, the air conditioning unit has a switching mechanism (e.g., a four-way reversing valve) for switching the refrigerant circulation direction. Refrigeration unit 1 can also be a water heater, a cooling unit, a cooling device for cooling the air inside a storage facility, etc. The cooling device cools the air inside cold storage rooms, freezers, containers, etc.

[0049] like Figure 2 As shown, the rotary compressor 10 has a housing 11, a drive mechanism 20, and a compression mechanism 50.

[0050] The shell 11 is a cylindrical, sealed container with a relatively long longitudinal length. A suction pipe 16 penetrates the body of the shell 11 and is fixed to the body of the shell 11. A liquid reservoir (not shown) is connected to the suction pipe 16. A discharge pipe 17 penetrates the upper part of the shell 11 and is fixed to the upper part of the shell 11.

[0051] An oil reservoir 18 is provided at the bottom of the housing 11. Oil is stored in the oil reservoir 18. The oil is used to lubricate the sliding parts of the compression mechanism 50 and the drive shaft 25.

[0052] <Drive mechanism>

[0053] The drive mechanism 20 is housed inside the housing 11. The drive mechanism 20 has a motor 21 and a drive shaft 25. The motor 21 is arranged above the compression mechanism 50. The motor 21 has a stator 22 and a rotor 23.

[0054] The stator 22 is fixed to the inner circumferential surface of the housing 11. The rotor 23 extends through the interior of the stator 22 in the vertical direction. A drive shaft 25 is fixed inside the shaft of the rotor 23. When the motor 21 is energized, the drive shaft 25 and the rotor 23 are driven to rotate together.

[0055] A drive shaft 25 is arranged on the axis of the housing 11. An oil passage 30 is formed inside the drive shaft 25. A centrifugal oil pump 28 is provided at the lower end of the drive shaft 25. A suction port 28a is provided at the lower part of the oil pump 28. The oil pump 28 delivers oil stored in the oil storage section 18. The delivered oil is supplied to the compression mechanism 50 and the sliding part of the drive shaft 25 through the oil passage 30 of the drive shaft 25.

[0056] The drive shaft 25 has a main shaft portion 26 and an eccentric portion 27. The upper part of the main shaft portion 26 is fixed to the rotor 23 of the motor 21. The axis of the eccentric portion 27 is eccentrically offset from the axis of the main shaft portion 26 by a predetermined amount.

[0057] The portion of the main shaft 26 that is higher than the eccentric portion 27 is rotatably supported by the front cylinder head 52, which will be described later. The portion of the main shaft 26 that is lower than the eccentric portion 27 is rotatably supported by the rear cylinder head 53, which will be described later.

[0058] <Compression Mechanism>

[0059] The compression mechanism 50 is housed inside the housing 11. The compression mechanism 50 is located below the electric motor 21. The compression mechanism 50 includes a cylinder 51, a front cylinder head 52, a rear cylinder head 53, and a piston 54.

[0060] The cylinder 51 is formed from a flat, approximately annular component. A circular compression chamber 55 is formed in the center of the cylinder 51. A radially extending intake passage 56 is formed in the cylinder 51. The downstream end of the intake passage 56 communicates with the compression chamber 55. An intake pipe 16 is connected to the upstream end of the intake passage 56.

[0061] The front cylinder head 52 is disposed above the cylinder 51. The front cylinder head 52 is arranged to cover the internal space of the cylinder 51 from above. The front cylinder head 52 supports the main shaft portion 26 of the drive shaft 25, and the main shaft portion 26 of the drive shaft 25 is rotatable. An ejection passage (not shown) is formed in the front cylinder head 52, extending axially through the front cylinder head 52.

[0062] The rear cylinder head 53 is located below the cylinder 51. The rear cylinder head 53 is arranged to cover the internal space of the cylinder 51 from below. The rear cylinder head 53 supports the main shaft portion 26 of the drive shaft 25, and the main shaft portion 26 of the drive shaft 25 is rotatable.

[0063] Just like Figure 3 As shown, piston 54 is housed inside cylinder 51. Blade 57 is integrally formed with piston 54. Compression chamber 55 is divided by cylinder 51 and piston 54. Piston 54 is formed into a perfectly circular ring. An eccentric portion 27 of drive shaft 25 is embedded inside piston 54.

[0064] The interior of the compression chamber 55 is divided into a low-pressure chamber 55a and a high-pressure chamber 55b by the blades 57 (see reference). Figure 11 The blade 57 is supported by a pair of bushings 58, and the blade 57 is capable of oscillation.

[0065] Piston 54 rotates eccentrically within cylinder 51 in conjunction with the rotation of drive shaft 25. As the volume of low-pressure chamber 55a gradually increases with the eccentric rotation of piston 54, refrigerant flowing in suction pipe 16 is drawn into low-pressure chamber 55a from suction passage 56.

[0066] Next, when the low-pressure chamber 55a is disconnected from the suction passage 56, the disconnected space constitutes the high-pressure chamber 55b. As the volume of the high-pressure chamber 55b gradually decreases, the internal pressure of the high-pressure chamber 55b continuously increases. When the internal pressure of the high-pressure chamber 55b exceeds the specified pressure, the refrigerant in the high-pressure chamber 55b flows out towards the outside of the compression mechanism 50 through the ejection passage 59. This high-pressure refrigerant flows upward in the internal space of the housing 11 and passes through the iron core cutout of the motor 21 (not shown). The high-pressure refrigerant flowing out above the motor 21 is sent to the refrigerant circuit 1a through the ejection pipe 17.

[0067] <Regarding oil distribution channels>

[0068] The compression mechanism 50 is driven to rotate, and this rotation applies centrifugal force and gas load to the drive shaft 25, thus causing an increase in shaft deflection of the drive shaft 25.

[0069] Therefore, the inventors of this application focused on the oil passage 30, which is the main cause of the decrease in rigidity of the drive shaft 25, and studied how to improve the rigidity of the drive shaft 25 by improving the shape of the oil passage 30.

[0070] like Figure 2 As shown, an oil passage 30 is provided in the drive shaft 25. The oil passage 30 has an oil hole 31, a lower end hole 35, and a transverse hole 36.

[0071] The lower end hole 35 opens at the lower end of the main shaft portion 26 of the drive shaft 25. An oil supply pump 28 is installed at the lower end hole 35. An oil hole 31 communicates with the lower end hole 35 and extends upward. A horizontal hole 36 communicates with the oil hole 31 and extends horizontally. The horizontal hole 36 opens at positions where oil can be supplied to the compression mechanism 50 and the sliding portion of the drive shaft 25.

[0072] exist Figure 2 In the example shown, the transverse bore 36 opens on the sliding surfaces of the front cylinder head 52, the rear cylinder head 53, and the piston 54. An exhaust port 37 is formed on the drive shaft 25 at a position above the front cylinder head 52. The exhaust port 37 allows gases contained in the oil through the oil passage 30 to be discharged.

[0073] The oil flowing in the oil hole 31 is discharged to the outside of the drive shaft 25 through the transverse hole 36 under the action of centrifugal force generated by the rotation of the drive shaft 25, and is then supplied to the compression mechanism 50 and the sliding part of the drive shaft 25.

[0074] like Figure 4 As shown, the axis of the main shaft 26 is designated as axis C1, and the axis of the eccentric part 27 is designated as axis C2. When viewed from the axial direction of the drive shaft 25, the defined direction in the region enclosed by the imaginary envelope 40 of the enveloping oil hole 31 is designated as the first direction Y, and the direction orthogonal to the first direction Y is designated as the second direction X.

[0075] It should be noted that, in Figure 4 In the example shown, when viewed from the axial direction of the drive shaft 25, the direction connecting the axis C1 of the main shaft 26 and the axis C2 of the eccentric part 27 is defined as the first direction Y, and the direction orthogonal to the first direction Y is defined as the second direction X, but it is not limited to this method.

[0076] Viewed axially, the oil passage 30 is formed by an elongated oil hole 31 extending along the first direction Y. Here, the length of the oil hole 31 in the second direction X is denoted as x, and the length of the oil hole 31 in the first direction Y is denoted as y. The elongated oil hole 31 can be represented as the trajectory of a circle with diameter x moving continuously in the first direction Y. Here, the curve tangent to all circles is called the envelope. Figure 4 In the example shown, when viewed from the axial direction, the imaginary envelope 40 enveloping the oil hole 31 is shown as an imaginary line. The imaginary envelope 40 is represented as an elongated curve extending along the inner periphery of the oil hole 31.

[0077] Here, when viewed axially, the length y in the first direction Y of the region of the oil passage 30 enclosed by the imaginary envelope 40 of the enclosing oil hole 31 is longer than the length x in the second direction X. This increases the rigidity of the drive shaft 25 and reduces shaft deflection.

[0078] Specifically, when a circular oil passage with a diameter equal to its length in the first direction Y and a larger diameter than the suction inlet 28a is provided at the center of the drive shaft 25 in order to draw oil up under the action of a centrifugal pump, a relatively large cavity will be formed at the center of the drive shaft 25 (see reference). Figure 5 The rigidity of the drive shaft 25 may be reduced in the area enclosed by the imaginary lines.

[0079] In contrast, by making the length of the oil passage 30 in the second direction X shorter than the length in the first direction Y, the passage area of ​​the oil passage 30 is reduced compared to the case where a circular oil passage is provided at the center of the drive shaft 25. This can improve the rigidity of the drive shaft 25 and reduce shaft deflection.

[0080] Furthermore, by ensuring that the distance from the rotation center of the drive shaft 25 to the inner wall of the radially furthest point in the oil passage 30 is equal to the radius of the circular oil passage, an equivalent centrifugal pump effect can be obtained (see reference). Figure 5 ).

[0081] Furthermore, by forming an oil passage 30 in the region enclosed by the imaginary envelope 40, where the length in the first direction Y is longer than the length in the second direction X, the rigidity of the drive shaft 25 in the second direction X is higher than the rigidity in the first direction Y.

[0082] The following uses Figure 6 and Figure 7 The relationship between the shape of the oil hole 31 and the bending stiffness of the drive shaft 25 is explained. It should be noted that... Figure 6 and Figure 7 In this illustration, only the main shaft portion 26 of the drive shaft 25 is shown, and the description of the eccentric portion 27 is omitted. In addition, for ease of explanation, the oil hole 31 is not described as an elongated hole extending along the first direction Y, but rather as a rectangle extending along the first direction Y that approximates an elongated hole shape.

[0083] like Figure 6 As shown, the diameter of the main shaft portion 26 is set to D. When a load is applied to the main shaft portion 26 of the drive shaft 25 from the first direction Y, the second moment of the section Iy is calculated by the following equation (1).

[0084] Iy = (π·D) 4 / 64)-(x·y 3 / 12)……(1)

[0085] On the other hand, such as Figure 7 As shown, when a load is applied to the main shaft portion 26 of the drive shaft 25 from the second direction X, the second moment Ix of the cross section is calculated by the following equation (2).

[0086] Ix = (π·D) 4 / 64)-(y·x 3 / 12)……(2)

[0087] Here, since x < y, it includes "y 3 The value of Iy is significantly lower than the value of Ix containing "y". That is, since Ix > Iy, the bending stiffness of the drive shaft 25 in the second direction X is higher than the bending stiffness in the first direction Y.

[0088] Next, use Figure 8-10 The graph illustrates the relationship between the rotation angle of the drive shaft 25 and the load applied to the drive shaft 25. It should be noted that, as... Figure 3As shown, the eccentric portion 27 of the drive shaft 25 is in Figure 3 The orientation of the middle-to-upward direction is set to the top dead center at 0°.

[0089] Figure 8 This is a graph showing the relationship between the angle relative to the top dead center and the magnitude of the force applied to the drive shaft 25. Figure 8 In this case, it can be seen that the gas load of the compression mechanism 50 reaches its maximum when the drive shaft 25 rotates 227° from the top dead center 0°.

[0090] Figure 9 This is a graph showing the relationship between the angle relative to the top dead center and the direction of the force applied to the drive shaft 25. For example... Figure 9 As shown, when the gas load reaches its maximum angle of 227° when the compression mechanism 50 is driven to rotate, the direction of the gas load applied to the drive shaft 25 is 119.18° (≈119°).

[0091] Figure 10 This is a graph showing the relationship between the angle relative to the top dead center and the direction of the gas load applied to the drive shaft 25 when the eccentric direction of the eccentric part 27 is taken as 0°. For example... Figure 10 As shown, when the gas load of the compression mechanism 50 reaches the maximum rotation angle of 227° when it is driven to rotate, the direction of the gas load applied to the drive shaft 25 with the eccentric direction of the eccentric part 27 as the reference 0° is -107.82° (≈-108°).

[0092] Figure 11 This diagram illustrates the angle at which the maximum gas load is applied to the drive shaft 25. Figure 11 In this case, at the position where the drive shaft 25 has rotated 227° from the top dead center 0°, the maximum gas load when the compression mechanism 50 is driven to rotate is applied in the direction after rotating 108° counterclockwise from the first direction Y connecting the axis C1 of the main shaft 26 and the axis C2 of the eccentric part 27. Figure 11 In the diagram, the load direction is indicated by a white arrow.

[0093] Here, the direction of the maximum gas load when the compression mechanism 50 is driven to rotate varies, for example, within the range of 80° to 110° depending on the compression conditions. The second direction X is orthogonal to the first direction Y, that is, the second direction X is the direction after rotating 90° relative to the first direction Y, and therefore is included in the range of 80° to 110° of the maximum gas load direction.

[0094] As described above, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y. Therefore, even when the maximum gas load is applied to the drive shaft 25 in the second direction X when the compression mechanism 50 is driven to rotate, shaft deflection of the drive shaft 25 can be suppressed.

[0095] It should be noted that, in order to further improve the rigidity of the drive shaft 25 in the face of the maximum gas load when the compression mechanism 50 is driven to rotate, the shape of the oil passage 30 can also be set so that the angle of the maximum gas load direction (108°) is consistent with the angle of the second direction X.

[0096] Furthermore, it is preferable to set the length y of the oil hole 31 in the first direction Y such that, when viewed from the axial direction, the two ends of the imaginary envelope 40 in the first direction Y are located radially outward from the suction port 28a of the oil supply pump 28. In this way, the centrifugal pump can smoothly supply oil using the centrifugal force generated by the rotation of the drive shaft 25.

[0097] -Effects of the first implementation method-

[0098] According to the features of this embodiment, by forming an oil passage 30 in the region surrounded by the imaginary envelope 40, the length in the first direction Y is longer than the length in the second direction X, the rigidity of the drive shaft 25 can be improved.

[0099] Therefore, even when the drive shaft 25 is subjected to centrifugal force by the eccentric weight of the eccentric part 27 and the piston 54 when the drive shaft 25 rotates, the shaft deflection of the drive shaft 25 can be reduced.

[0100] In addition, by ensuring that the distance from the rotation center of the drive shaft 25 to the inner wall of the radially furthest part in the oil passage 30 is equal to the radius of the circular oil passage, the same centrifugal pump effect can be obtained.

[0101] Furthermore, by suppressing the shaft deflection of such a drive shaft 25, noise generated by the vibration rotation of the drive shaft 25 can be suppressed.

[0102] According to the features of this embodiment, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y. Therefore, even when the maximum gas load is applied to the second direction X of the drive shaft 25 when the compression mechanism 50 is driven to rotate, the shaft deflection of the drive shaft 25 can be suppressed.

[0103] According to the features of this embodiment, when viewed from the axial direction, by forming an oil passage 30 by an elongated oil hole 31 extending along the first direction Y, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y.

[0104] According to the features of this embodiment, for a rotary compressor in which the compression mechanism 50 is arranged at a position lower than the motor 21, the shape of the oil passage 30 can be adopted such that the length in the first direction Y of the region enclosed by the imaginary envelope 40 is longer than the length in the second direction X.

[0105] According to the features of this embodiment, a refrigeration apparatus including a rotary compressor 10 and a refrigerant circuit 1a can be provided.

[0106] (Second Implementation)

[0107] Hereinafter, the same symbols will be used to mark the parts that are the same as in the first embodiment described above, and only the differences will be explained.

[0108] like Figure 12 As shown, when viewed axially, the oil passage 30 has an oil hole 31 formed by a rectangular hole extending along the first direction Y. Figure 12 In the example shown, when viewed from the axial direction, the imaginary envelope 40 enveloping the oil hole 31 is shown as an imaginary line. The imaginary envelope 40 is represented as a rectangular line extending along the inner periphery of the oil hole 31.

[0109] Here, when viewed from the axial direction, the length y in the first direction Y of the region of the oil passage 30 enclosed by the imaginary envelope 40 of the enclosing oil hole 31 is longer than the length x in the second direction X.

[0110] -Effects of the second implementation method-

[0111] According to the features of this embodiment, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y.

[0112] (Third Implementation)

[0113] like Figure 13 As shown, when viewed axially, the oil passage 30 is formed by a plurality of oil holes 31 arranged along the first direction Y. All of the oil holes 31 are formed by holes of the same inner diameter. Figure 13 In the example shown, four oil holes 31 are provided along the first direction Y, but this is just one example and is not limited to this. Figure 13 In the example shown, when viewed from the axial direction, an imaginary envelope 40 enveloping the plurality of oil holes 31 is shown as an imaginary line. The imaginary envelope 40 is represented as an elongated, hole-shaped curve extending along the first direction Y.

[0114] Here, when viewed from the axial direction, the length y in the first direction Y of the region of the oil passage 30 enclosed by the imaginary envelope 40 that encloses the plurality of oil holes 31 is longer than the length x in the second direction X.

[0115] It should be noted that in this embodiment, the multiple oil holes 31 are arranged symmetrically with respect to the axis C1 of the main shaft 26, but it is not limited to this method and can also be arranged asymmetrically.

[0116] Furthermore, it is preferable to position the oil hole 31 in the first direction Y such that, when viewed from the axial direction, the two ends of the imaginary envelope 40 in the first direction Y are located radially outward from the suction port 28a of the oil pump 28. In this way, the centrifugal pump can smoothly supply oil using the centrifugal force generated by the rotation of the drive shaft 25.

[0117] It should be noted that the two oil holes 31 arranged between the two ends of the oil hole 31 in the first direction Y are used to discharge the gas contained in the oil from the vent hole 37.

[0118] -Effects of the third implementation method-

[0119] According to the features of this embodiment, by forming an oil passage 30 by a plurality of oil holes 31 arranged along the first direction Y, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y.

[0120] (Fourth Implementation)

[0121] like Figure 14 As shown, when viewed axially, the oil passage 30 is formed by a plurality of oil holes 31 arranged along the first direction Y. The plurality of oil holes 31 contain holes with different inner diameters. Figure 14 In the example shown, three oil holes 31 are spaced apart in the first direction Y, but this is only one example and is not limited to this. The inner diameter of the oil hole 31 located in the central part in the first direction Y is larger than the inner diameter of the oil holes 31 located at both ends in the first direction Y.

[0122] exist Figure 14 In the example shown, when viewed from the axial direction, an imaginary envelope 40 enveloping the multiple oil holes 31 is shown as an imaginary line. The imaginary envelope 40 is represented as a curve whose length x in the second direction X is the largest at the center in the first direction Y, and gradually decreases towards the two ends in the second direction X.

[0123] Here, when viewed axially, the length y in the first direction Y of the region enclosed by the imaginary envelope 40 that surrounds the multiple oil holes 31 in the oil passage 30 is longer than the length x in the second direction X. Here, the length x of the central part in the second direction X, where the length x is the largest, is compared with the length y in the first direction Y.

[0124] It should be noted that the oil hole 31 between the two ends of the oil hole 31 arranged in the first direction Y is used to discharge the gas contained in the oil from the exhaust hole 37.

[0125] -Effects of the fourth implementation method-

[0126] According to the features of this embodiment, by forming an oil passage 30 by a plurality of oil holes 31 arranged along the first direction Y, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y.

[0127] (Fifth Implementation)

[0128] like Figure 15 As shown, when viewed axially, the oil passage 30 is formed by a plurality of oil holes 31 arranged along the first direction Y. All of the oil holes 31 are formed by holes of the same inner diameter. When viewed axially, a portion of adjacent oil holes 31 in the oil passage 30 overlaps.

[0129] exist Figure 15 In the example shown, when viewed from the axial direction, an imaginary envelope 40 enveloping the plurality of oil holes 31 is shown as an imaginary line. The imaginary envelope 40 is represented as an elongated, hole-shaped curve extending along the first direction Y.

[0130] Here, when viewed from the axial direction, the length y in the first direction Y of the region of the oil passage 30 enclosed by the imaginary envelope 40 that encloses the plurality of oil holes 31 is longer than the length x in the second direction X.

[0131] -Effects of the fifth implementation method-

[0132] According to the features of this embodiment, when the length of the region enclosed by the imaginary envelope 40 in the first direction Y is kept constant, the number of oil holes 31 in the region enclosed by the imaginary envelope 40 increases when a portion of the adjacent oil holes 31 overlaps, compared to arranging adjacent oil holes 31 separately from each other. Therefore, it is easier to process the oil passage 30 into an elongated shape.

[0133] (Sixth Implementation Method)

[0134] like Figure 16 As shown, the rotary compressor 10 has a housing 11, a drive mechanism 20, and a compression mechanism 50.

[0135] The drive mechanism 20 includes a motor 21 and a drive shaft 25. The drive shaft 25 has a main shaft portion 26 and two eccentric portions 27. The axis of each eccentric portion 27 is eccentricated from the axis of the main shaft portion 26 by a predetermined amount. The two eccentric portions 27 are eccentrically positioned in directions 180° apart from each other (see also...). Figure 17 ).

[0136] The compression mechanism 50 has two cylinders 51, a front cylinder head 52, a rear cylinder head 53, two pistons 54, and a middle plate 60. The middle plate 60 is sandwiched between the two cylinders 51.

[0137] like Figure 17 As shown, the axis of the main shaft 26 is designated as axis C1, and the axes of the two eccentric parts 27 are designated as axis C2 respectively. When viewed from the axial direction of the drive shaft 25, the defined direction in the region enclosed by the imaginary envelope 40 of the enveloping oil hole 31 is designated as the first direction Y, and the direction orthogonal to the first direction Y is designated as the second direction X.

[0138] It should be noted that, in Figure 17 In the example shown, when viewed from the axial direction of the drive shaft 25, the direction connecting the axis C1 of the main shaft 26 and the axis C2 of the eccentric part 27 is defined as the first direction Y, and the direction orthogonal to the first direction Y is defined as the second direction X, but it is not limited to this method.

[0139] Viewed axially, the oil passage 30 is formed by elongated oil holes 31 extending along the first direction Y. Figure 17 In the example shown, when viewed from the axial direction, the imaginary envelope 40 enveloping the oil hole 31 is shown as an imaginary line. The imaginary envelope 40 is represented as an elongated curve extending along the inner periphery of the oil hole 31.

[0140] Here, when viewed from the axial direction, the length y in the first direction Y of the region of the oil passage 30 enclosed by the imaginary envelope 40 of the enclosing oil hole 31 is longer than the length x in the second direction X.

[0141] It should be noted that the oil passage 30 can also be configured in the same way as in the third embodiment described above, where, when viewed from the axial direction, it is formed by a plurality of oil holes 31 arranged along the first direction Y. Furthermore, the oil passage 30 can also be configured in the same way as in the fifth embodiment described above, where, when viewed from the axial direction, a portion of adjacent oil holes 31 overlaps.

[0142] -Effects of the sixth implementation method-

[0143] According to the features of this embodiment, the rigidity of the drive shaft 25 in the second direction X is higher than that in the first direction Y.

[0144] (Other implementation methods)

[0145] The above implementation method can also adopt the following structure.

[0146] In this embodiment, the oil passage 30 is formed by an elongated hole extending along the first direction Y when viewed from the axial direction, but it is not limited to this method. For example, the oil passage 31 may also be formed by an elliptical hole extending along the first direction Y when viewed from the axial direction.

[0147] In this embodiment, an oil supply pump 28 is installed at the lower end of the drive shaft 25 to draw oil up, but this method is not limited to this. For example, the lower end of the drive shaft 25 may be extended to a position immersed in the oil reservoir 18, and the lower end hole 35 of the oil passage 30, which opens at the lower end of the drive shaft 25, may be covered by an end plate (not shown) with an inlet hole in the center. This allows oil to be drawn up from the inlet hole of the end plate toward the oil passage 30 of the drive shaft 25.

[0148] Alternatively, any one of the multiple oil holes 31 can be used as an oil supply path to supply oil to the sliding part between the drive shaft 25 and the front cylinder head 52 and the rear cylinder head 53. On the other hand, other oil holes 31 can be used as oil supply paths to supply oil to the cylinder 51, and so on, depending on the application.

[0149] The embodiments have been described above, but it should be understood that various changes can be made to the manner and specific details without departing from the spirit and scope of the claims. Furthermore, the elements involved in the above embodiments, variations, and other embodiments can be appropriately combined or substituted. The terms "first," "second," "third," etc., in the specification and claims are only used to distinguish statements containing these terms and are not intended to limit the number or order of the statements.

[0150] -Industry Applicability-

[0151] In summary, this disclosure is useful for rotary compressors and refrigeration devices.

[0152] - Symbol Explanation -

[0153] 1. Refrigeration unit

[0154] 1a Refrigerant circuit

[0155] 10 Rotary compressor

[0156] 21 Electric motor

[0157] 25 drive shafts

[0158] 26 Spindle section

[0159] 27. Eccentric part

[0160] 30 Oil passage

[0161] 31 Oil hole

[0162] 40 Imaginary envelope

[0163] 50 Compression Mechanism

[0164] C1 axis

[0165] C2 axis

[0166] X Second Direction

[0167] Y First direction

Claims

1. A rotary compressor comprising a compression mechanism (50) and a drive shaft (25) for driving the compression mechanism (50) to rotate, characterized in that: The drive shaft (25) has a main shaft portion (26) and an eccentric portion (27), the eccentric portion (27) being eccentrically offset from the axis (C1) of the main shaft portion (26) by a predetermined amount. An oil passage (30) is provided in the drive shaft (25), the oil passage (30) having one or more oil holes (31) extending axially. When viewed from the axial direction of the drive shaft (25), the defined direction in the region enclosed by the imaginary envelope (40) that encloses the oil hole (31) is designated as the first direction (Y), and the direction orthogonal to the first direction (Y) is designated as the second direction (X). When viewed from the axial direction, the length of the oil passage (30) in the first direction (Y) of the region enclosed by the imaginary envelope (40) is longer than the length in the second direction (X).

2. The rotary compressor according to claim 1, characterized in that: When viewed from the axial direction of the drive shaft (25), the first direction (Y) is the direction that connects the axis (C1) of the main shaft (26) with the axis (C2) of the eccentric part (27).

3. The rotary compressor according to claim 1 or 2, characterized in that: When viewed from the axial direction, the oil passage (30) is formed by an elongated oil hole (31) extending along the first direction (Y).

4. The rotary compressor according to claim 1 or 2, characterized in that: When viewed from the axial direction, the oil passage (30) is formed by a plurality of oil holes (31) arranged along the first direction (Y).

5. The rotary compressor according to claim 4, characterized in that: When viewed from the axial direction, a portion of the adjacent oil holes (31) in the oil passage (30) overlap.

6. The rotary compressor according to any one of claims 1 to 5, characterized in that: The rotary compressor includes an electric motor (21) that rotates the drive shaft (25). The compression mechanism (50) is located below the motor (21).

7. A refrigeration device, characterized in that: The refrigeration device includes a rotary compressor (10) as described in any one of claims 1 to 6, and a refrigerant circuit (1a) for the refrigerant compressed by the rotary compressor (10) to circulate.

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