Compressor unit and refrigeration device

Abstract

A value F obtained by multiplying the weight of the piston (54) and the vane (57) by the square of the rotational speed of the compressor main body (11), a distance h from the center in the thickness direction of the piston (54) to the center of gravity (G1) of the compressor unit (10), a moment of inertia I around the center of rotation when the compressor main body (11) vibrates in a direction of tilting toward the reservoir (40) side, that is, the center axis passing through the center of gravity (G1) of the compressor unit (10), a distance L from the axis of the inlet pipe (42) of the reservoir (40) to the center of gravity (G1) of the compressor unit (10), and the rated capacity P of the refrigerating apparatus 1 satisfy the condition of F x (h / I) x L ≤ 19 x P + 128.

Description

Technical Field

[0001] This disclosure relates to a compressor unit and a refrigeration device. Background Technology

[0002] Patent document 1 discloses a compressor unit, which includes a compressor body and a liquid receiver connected to the compressor body.

[0003] In the invention of Patent Document 1, by arranging the joint of the inlet pipe of the liquid reservoir close to the support center of the compressor body, the transmission of vibrations in the tilt direction of the compressor body and the axial vibrations of the compressor body to the inlet pipe during compressor body operation is suppressed.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Publication No. 2011-185123 Summary of the Invention

[0007] -The technical problem the invention aims to solve-

[0008] However, to further improve compressor performance, it is desirable to rotate the compressor mechanism at high speed. Here, if the compressor body's rotational speed is increased, the vibration of the compressor body in the direction it tilts towards the receiver will increase proportionally to the square of the rotational speed. As a result, because the axial vibration of the receiver increases, this vibration is transmitted through the inlet pipe to the entire outdoor unit, leading to increased noise from the product.

[0009] In the existing invention, when the rotational speed of the compressor body is increased, there are no provisions for the optimal dimensional relationships of the various components used to suppress the increase in vibration of the liquid receiver.

[0010] The purpose of this disclosure is to suppress the increase in vibration of the liquid receiver even when the rotational speed of the compressor body is increased.

[0011] - Technical solutions used to solve technical problems -

[0012] The first aspect of this disclosure relates to a compressor unit installed in a refrigeration device 1 performing a refrigeration cycle, and includes a compressor body 11 having a compression mechanism 50 and a liquid receiver 40 connected to the compressor body 11. The compression mechanism 50 has a cylinder 51, a piston 54 rotating eccentrically within the cylinder 51, and blades 57 dividing the interior of a compression chamber 55 of the cylinder 51 into a low-pressure chamber 55a and a high-pressure chamber 55b, wherein the weight of the piston 54 and the blades 57 is multiplied by the rotational speed of the compressor body 11. The value F obtained by squaring the piston 54, the distance h from the center of the piston 54 in the thickness direction to the center of gravity G1 of the compressor unit 10, the moment of inertia I about the center of rotation of the compressor body 11 when it vibrates in the direction of tilting towards the liquid reservoir 40, i.e., the central axis through the center of gravity G1 of the compressor unit 10, the distance L from the axis of the inlet pipe 42 of the liquid reservoir 40 to the center of gravity G1 of the compressor unit 10, and the rated capacity P of the refrigeration device 1 satisfy the condition F×(h / I)×L≤19×P+128.

[0013] In the first aspect, F×(h / I)×L is defined as a parameter representing the magnitude of vibration of the liquid reservoir 40 in the vertical direction, such that the parameter is less than the value set according to the rated capacity P of the refrigeration unit 1.

[0014] Therefore, even when the speed of the compressor body 11 is increased, the vibration of the liquid receiver 40 can be suppressed.

[0015] The second aspect of this disclosure, based on the compressor unit of the first aspect, satisfies the condition F×(h / I)×L≤19×P+95.

[0016] In the second aspect, by setting the parameter F×(h / I)×L to satisfy the condition, it is possible to further suppress the increase in vibration of the reservoir 40.

[0017] The third aspect of this disclosure relates to a compressor unit installed in a refrigeration device 1 performing a refrigeration cycle, and includes a compressor body 11 having a compression mechanism 50 and a liquid receiver 40 connected to the compressor body 11. The compression mechanism 50 has a cylinder 51, a piston 54 rotating eccentrically within the cylinder 51, and blades 57 dividing the interior of a compression chamber 55 of the cylinder 51 into a low-pressure chamber 55a and a high-pressure chamber 55b. The value F obtained by multiplying the weight of the piston 54 and the blades 57 by the square of the rotational speed of the compressor body 11 is given by the value of the compressor body 11. The distance h from the center of the piston 54 in the thickness direction to the center of gravity G1 of the compressor unit 10, the moment of inertia I about the center of rotation of the compressor body 11 when it vibrates in the direction of tilting towards the liquid reservoir 40, i.e., the central axis passing through the center of gravity G1 of the compressor unit 10, the distance L from the axis of the inlet pipe 42 of the liquid reservoir 40 to the center of gravity G1 of the compressor unit 10, the volume V of the cylinder 51, and the rotational speed N of the compressor body 11 above the specified speed satisfy the condition F×(h / I)×L≤0.063×V×N+114.

[0018] In the third aspect, F×(h / I)×L is defined as a parameter representing the magnitude of vibration of the reservoir 40 in the vertical direction. This parameter is less than the value set according to the volume V of the cylinder 51 and the rotational speed N of the compressor body 11, and the rotational speed N of the compressor body 11 is above the specified speed.

[0019] Therefore, even when the speed of the compressor body 11 is increased, the vibration of the liquid receiver 40 can be suppressed.

[0020] The fourth aspect of this disclosure, based on the compressor unit of the third aspect, satisfies the condition F×(h / I)×L≤0.063×V×N+85.

[0021] In the fourth aspect, by setting the parameter F×(h / I)×L to satisfy the condition, it is possible to further suppress the increase in vibration of the reservoir 40.

[0022] Based on the compressor unit of any one of the first to fourth aspects of this disclosure, the fifth aspect of this disclosure specifies that the compressor body 11 has a rotational speed of 112 rpm or higher.

[0023] In the fifth aspect, by increasing the rotational speed of the compressor body 11 to above a specified speed, the compressor performance can be improved, and the increase in vibration of the liquid receiver 40 can be suppressed even in the high-speed rotation region.

[0024] The sixth aspect of this disclosure, based on the compressor unit of the fifth aspect, wherein the specified rotational speed of the compressor body 11 is above 130 rpm.

[0025] In the sixth aspect, by further increasing the rotational speed of the compressor body 11 to above a specified speed, the compressor performance can be further improved, and the vibration increase of the liquid receiver 40 can be suppressed even in the high-speed rotation region.

[0026] The seventh aspect of this disclosure is based on the compressor unit of the sixth aspect, wherein the compressor body 11 is a single-cylinder type.

[0027] In the seventh aspect, even the single-cylinder compressor body 11, which has particularly large vibration problems in the high-speed rotation area, can suppress the increase of vibration in the liquid receiver 40.

[0028] Based on the compressor unit of any one of the first to seventh aspects of this disclosure, the eighth aspect of this disclosure states that at least one of the piston 54 and the blade 57 has a density of 6020 kg / m³. 3 the following.

[0029] In the eighth aspect, by making the density of at least one of the piston 54 and the blade 57 below a specified value, weight reduction can be achieved, thereby reducing the parameter F, and thus reducing the value of parameter F×(h / I)×L.

[0030] The ninth aspect of this disclosure, based on the eighth aspect, wherein at least one of the piston 54 and the blade 57 is made of aluminum.

[0031] In the ninth aspect, lightweighting is achieved by using aluminum to form at least one of the piston 54 and the blade 57, thereby reducing the parameter F.

[0032] Based on the compressor unit of any one of the first to ninth aspects of this disclosure, the tenth aspect of this disclosure provides that the weight M1 of the lubricating oil filled in the compressor body 11 and the weight M2 of the compressor unit 10 satisfy the condition M1 / M2 > 0.0172 × P + 0.0418.

[0033] In the tenth aspect, by setting the parameters M1 / M2 to satisfy the aforementioned conditions, the amount of lubricating oil accumulated at the bottom of the compressor body 11 can be increased, thereby lowering the position of the center of gravity G1 of the compressor unit 10. This, in turn, reduces the value of the parameter F×(h / I)×L.

[0034] The eleventh aspect of this disclosure is based on the compressor unit of any one of the first to tenth aspects, wherein the compressor unit includes a drive mechanism 20 that drives the compression mechanism 50, the drive mechanism 20 having: a drive shaft 25; a motor 21 having a rotor 23 that rotates the drive shaft 25; and a counterweight 30 disposed on the rotor 23, the counterweight 30 having an annular counterweight body 31 extending circumferentially at the axial end of the rotor 23, and a circumferentially extending recess 31a formed on the surface of the counterweight body 31 on the side of the rotor 23.

[0035] In the eleventh aspect, the counterweight 30 is formed as a circumferentially extending ring. That is, the counterweight 30 has a continuous circumferential shape, making it difficult for the refrigerant containing lubricating oil to be stirred during the rotation of the rotor 23.

[0036] Therefore, even when the counterweight 30 rotates together with the rotor 23, the phenomenon of lubricating oil rising due to being swept up by the counterweight 30 can be suppressed. As a result, the amount of lubricating oil remaining at the bottom of the compressor body 11 can be adequately ensured, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0037] The twelfth aspect of this disclosure is based on the compressor unit of any one of the first to tenth aspects, the compressor unit including a drive mechanism 20 that drives the compression mechanism 50, the drive mechanism 20 having: a drive shaft 25; a motor 21 having a rotor 23 that rotates the drive shaft 25; and a counterweight 30 disposed on the rotor 23, the counterweight 30 having a counterweight body 31 and a counterweight cover 32, the counterweight body 31 being formed as an arc extending circumferentially from the axial end of the rotor 23, the counterweight cover 32 having an annular cover body 32a, an inner peripheral wall 32b erected along the inner peripheral edge of the cover body 32a, and an outer peripheral wall 32c erected along the outer peripheral edge of the cover body 32a, the counterweight body 31 being covered by the cover body 32a, the inner peripheral wall 32b, and the outer peripheral wall 32c of the counterweight cover 32.

[0038] In the twelfth aspect, the counterweight 30 has a counterweight body 31 and a counterweight cover 32. The counterweight body 31 is covered by an annular counterweight cover 32. That is, the counterweight 30 has a continuous shape in the circumferential direction, so that the refrigerant containing lubricating oil is difficult to be stirred during the rotation of the rotor 23.

[0039] Therefore, even when the counterweight 30 rotates together with the rotor 23, the phenomenon of lubricating oil rising due to being swept up by the counterweight 30 can be suppressed. As a result, the amount of lubricating oil remaining at the bottom of the compressor body 11 can be adequately ensured, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0040] The thirteenth aspect of this disclosure is based on the compressor unit of any one of the first to twelfth aspects, the compressor unit comprising a drive mechanism 20 that drives the compression mechanism 50, the drive mechanism 20 having: a drive shaft 25; and a motor 21 having a rotor 23 that rotates the drive shaft 25, wherein the distance hm from the center of the piston 54 in the thickness direction to the center of gravity G2 of the motor 21 satisfies the condition hm / h < 0.0288 × P + 1.0673.

[0041] In the thirteenth aspect, by setting the parameter hm / h to satisfy the above conditions, the position of the center of gravity G2 of the motor 21 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0042] The fourteenth aspect of this disclosure, based on the compressor unit of the thirteenth aspect, includes a compression mechanism 50 having a front cylinder head 52 disposed below the motor 21, the front cylinder head 52 having an upwardly extending flange 52b to support the drive shaft 25, the lower end of the rotor 23 and the upper end of the flange 52b overlapping when viewed radially.

[0043] In the fourteenth aspect, by arranging the lower end of the rotor 23 and the upper end of the flange 52b to overlap when viewed radially, the position of the center of gravity G2 of the motor 21 is lowered, thereby enabling the position of the center of gravity G1 of the compressor unit 10 to be lowered.

[0044] Based on the compressor unit of any one of the first to fourteenth aspects of this disclosure, the reservoir 40 has an upper frame 41b and a lower frame 41c disposed below the upper frame 41b, wherein the plate thickness of the lower frame 41c is greater than the plate thickness of the upper frame 41b.

[0045] In the fifteenth aspect, by making the plate thickness of the lower frame 41c of the reservoir 40 greater than the plate thickness of the upper frame 41b, the center of gravity of the reservoir 40 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0046] Based on the compressor unit of any one of the first to fifteenth aspects of this disclosure, the sixteenth aspect of the present disclosure has a liquid reservoir 40 having a partition 65 that vertically separates the interior of the liquid reservoir 40, the partition 65 being arranged at a position lower than the axial center position of the liquid reservoir 40.

[0047] In the sixteenth aspect, by arranging the partition 65 at a position lower than the axial center position of the reservoir 40, the center of gravity of the reservoir 40 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0048] The seventeenth aspect of this disclosure is based on the compressor unit of any one of the first to sixteenth aspects, wherein a weight component 66 is provided on the outlet pipe 43 of the liquid reservoir 40.

[0049] In the seventeenth aspect, by providing a weight component 66 on the outlet pipe 43 of the reservoir 40, the center of gravity of the reservoir 40 can be lowered, and the center of gravity G1 of the compressor unit 10 can be lowered.

[0050] Based on the compressor unit of any one of the first to seventeenth aspects of this disclosure, the eighteenth aspect of this disclosure has a rear cylinder cover 53 disposed at the lower part of the cylinder 51, the rear cylinder cover 53 being fixed to the inner circumferential surface of the housing 12 of the compressor body 11.

[0051] In the eighteenth aspect, by fixing the rear cylinder head 53 to the inner circumferential surface of the housing 12 of the compressor body 11, the weight of the rear cylinder head 53 can be increased, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0052] Based on the compressor unit of any one of the first to eighteenth aspects of this disclosure, the housing 12 of the compressor body 11 has a cylindrical body 12a, an upper bowl portion 12b that blocks the upper opening of the body 12a, and a lower bowl portion 12c that blocks the lower opening of the body 12a, wherein the plate thickness of the lower bowl portion 12c is greater than the plate thickness of the upper bowl portion 12b.

[0053] In the nineteenth aspect, by making the thickness of the lower bowl portion 12c of the housing 12 greater than the thickness of the upper bowl portion 12b, the center of gravity of the compressor body 11 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0054] The twentieth aspect of this disclosure relates to a refrigeration apparatus comprising a compressor unit 10 of any one of the first to nineteenth aspects, and a refrigerant circuit 1a in which refrigerant compressed by the compressor unit 10 flows.

[0055] In the twentieth aspect, a refrigeration apparatus including a compressor unit 10 can be provided. Attached Figure Description

[0056] Figure 1This is a refrigerant circuit diagram showing the structure of the refrigeration device according to this embodiment;

[0057] Figure 2 This is a longitudinal sectional view showing the structure of the compressor unit;

[0058] Figure 3 It is a three-dimensional diagram showing the structure of the counterweight;

[0059] Figure 4 This is a top sectional view showing the structure of the compression mechanism;

[0060] Figure 5 It is a graph showing the relationship between the rotational speed of the compressor body in an existing compressor unit and the sound pressure level of the product.

[0061] Figure 6 It is a graph showing the relationship between the rotational speed of the compressor body and the angular acceleration of the compressor unit's rotational vibration around the Y-axis;

[0062] Figure 7 It is a graph showing the relationship between the rated capacity of the refrigeration unit and the parameter F×(h / I)×L;

[0063] Figure 8 It is a graph showing the relationship between the rated capacity of the refrigeration unit and the parameter M1 / M2;

[0064] Figure 9 It is a graph showing the relationship between the rated capacity of the refrigeration unit and the parameter hm / h;

[0065] Figure 10 This is a perspective view showing the structure of the counterweight involved in this modified example 1;

[0066] Figure 11 It is an exploded three-dimensional view showing the structure of the counterweight;

[0067] Figure 12 This is a longitudinal sectional view showing the structure of the compressor unit involved in this modified example 2;

[0068] Figure 13 This is a longitudinal sectional view showing the structure of the compressor unit involved in this modified example 3;

[0069] Figure 14 This is a longitudinal sectional view showing the structure of the compressor unit involved in this modified example 4;

[0070] Figure 15 This is a longitudinal sectional view showing the structure of the compressor unit involved in this modified example 5;

[0071] Figure 16This is a diagram illustrating the forces applied to each piston of a two-cylinder compressor and their distances to the center of gravity in other embodiments;

[0072] Figure 17 It is a graph showing the relationship between the product of cylinder volume and compressor body speed V×N and parameter F×(h / I)×L in other embodiments. Detailed Implementation

[0073] (Implementation Method)

[0074] like Figure 1 As shown, compressor unit 10 is installed in refrigeration unit 1. Refrigeration unit 1 has a refrigerant circuit 1a filled with refrigerant. Refrigerant circuit 1a includes compressor unit 10, radiator 3, pressure reducing mechanism 4, and evaporator 5. Pressure reducing mechanism 4 is, for example, an expansion valve. Refrigerant circuit 1a performs a vapor compression refrigeration cycle.

[0075] In the refrigeration cycle, the refrigerant compressed by the compressor unit 10 releases heat to the air in the radiator 3. The refrigerant, after releasing heat, is depressurized by the pressure reducing mechanism 4 and then evaporates in the evaporator 5. The evaporated refrigerant is then drawn into the compressor unit 10.

[0076] 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 the storage area, etc. The cooling device cools the air inside the cold storage, freezer, container, etc.

[0077] like Figure 2 As shown, the compressor unit 10 includes a compressor body 11 and a liquid receiver 40. The liquid receiver 40 is connected to the compressor body 11. The compressor body 11 has a housing 12, a drive mechanism 20, and a compression mechanism 50.

[0078] Below, in Figure 2 In the figure, the left-right direction of the arrangement of the compressor body 11 and the liquid receiver 40 is set as the X-axis direction, the paper depth direction orthogonal to the X-axis direction is set as the Y-axis direction, and the up-down direction of the compressor body 11 is set as the Z-axis direction.

[0079] The shell 12 is a cylindrical, sealed container with a relatively long longitudinal length. The shell 12 has a body 12a, an upper bowl 12b, and a lower bowl 12c. The body 12a is formed as a vertically extending cylinder with openings at both ends in the axial direction. The upper bowl 12b is fixed to the upper end of the body 12a and blocks the upper opening of the body 12a. The lower bowl 12c is fixed to the lower end of the body 12a and blocks the lower opening of the body 12a. An intake pipe 16 passes through the body 12a and is fixed to the body 12a. An exhaust pipe 17 passes through the upper bowl 12b and is fixed to the upper bowl 12b.

[0080] An oil reservoir 18 is formed at the bottom of the housing 12. The oil reservoir 18 is composed of the inner wall of the lower part of the body 12a and the lower bowl 12c. Lubricating oil is stored in the oil reservoir 18. The lubricating oil lubricates the sliding parts of the compression mechanism 50 and the drive shaft 25.

[0081] The drive mechanism 20 is housed inside the housing 12. The drive mechanism 20 includes a motor 21, a drive shaft 25, and a counterweight 30. The motor 21 is positioned above the compression mechanism 50. The motor 21 has a stator 22 and a rotor 23.

[0082] The stator 22 is fixed to the inner circumferential surface of the body 12a of the housing 12. 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.

[0083] The drive shaft 25 is located on the axis of the body 12a of the housing 12. An oil supply passage 25a is formed inside the drive shaft 25. The lower end of the drive shaft 25 is immersed in the oil reservoir 18. The lubricating oil stored in the oil reservoir 18 is supplied to the compression mechanism 50 and the sliding part of the drive shaft 25 through the oil supply passage 25a inside the drive shaft 25.

[0084] 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.

[0085] The portion of the main shaft 26 that is higher than the eccentric portion 27 is supported by the flange portion 52b of the front cylinder head 52 (described later) and is rotatable. The portion of the main shaft 26 that is lower than the eccentric portion 27 is supported by the rear cylinder head 53 (described later) and is rotatable.

[0086] The counterweights 30 are respectively disposed at both axial ends of the rotor 23. Each counterweight 30 has a circumferentially extending annular counterweight body 31. A circumferentially extending recess 31a (see reference) is formed on the surface of the counterweight body 31 on the side closest to the rotor 23. Figure 3 ).

[0087] The compression mechanism 50 is housed inside the housing 12. The compression mechanism 50 is located below the motor 21. The compression mechanism 50 includes a cylinder 51, a front cylinder head 52, a rear cylinder head 53, a piston 54, and a vane 57.

[0088] 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.

[0089] A through hole 15 is formed on the body 12a of the housing 12 at a position opposite to the suction passage 56. A connector tube 19 is connected to the through hole 15 of the housing 12. The connector tube 19 is formed of a cylindrical component made of metal. The connector tube 19 is engaged with the body 12a of the housing 12 when it is inserted into the through hole 15. The connector tube 19 extends from the body 12a of the housing 12 toward the outside of the housing 12.

[0090] The intake pipe 16 is connected to the intake passage 56 of the cylinder 51 and extends to the outside of the housing 12 through the inside of the connector pipe 19. The outer peripheral surface of the intake pipe 16 is brazed to the inner peripheral surface of the connector pipe 19.

[0091] 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 has an annular plate portion 52a and a flange portion 52b.

[0092] The annular plate portion 52a is formed of a flat, annular member and is stacked on the upper end of the cylinder 51. The annular plate portion 52a is fixed to the inner circumferential surface of the body 12a of the housing 12. The flange portion 52b is formed of a cylindrical member extending upward from the radial center of the annular plate portion 52a. The flange portion 52b supports the main shaft portion 26 of the drive shaft 25, which is rotatable. An ejection passage (not shown) is formed on the front cylinder head 52, extending axially through the annular plate portion 52a.

[0093] 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, which is rotatable.

[0094] Just like Figure 4As 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 in a perfectly circular ring shape. An eccentric portion 27 of drive shaft 25 is embedded inside piston 54. The interior of compression chamber 55 is divided into low-pressure chamber 55a and high-pressure chamber 55b by blade 57. Blade 57 is supported by a pair of bushings 58 and is capable of oscillation.

[0095] 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.

[0096] Next, when the low-pressure chamber 55a is disconnected from the suction passage 56, the disconnected space becomes 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 to the outside of the compression mechanism 50 through the discharge passage 59. This high-pressure refrigerant flows upward in the internal space of the housing 12 and passes through the iron core cutout of the motor 21 (not shown). The high-pressure refrigerant that has flowed out above the motor 21 is sent to the refrigerant circuit through the discharge pipe 17.

[0097] <Structure of the reservoir>

[0098] A receiver 40 is connected upstream of the compressor body 11. The receiver 40 temporarily stores the refrigerant before it is drawn into the compressor body 11 and performs gas-liquid separation between the liquid refrigerant and refrigeration oil contained in the refrigerant gas.

[0099] The receiver 40 has a main container 41, an inlet pipe 42, and an outlet pipe 43. The inlet pipe 42 allows refrigerant to flow into the main container 41. The outlet pipe 43 allows refrigerant to flow out of the main container 41.

[0100] The main container 41 is composed of an elongated cylindrical component. The main container 41 has a body 41a, an upper frame 41b, and a lower frame 41c. The body 41a is formed as a cylinder extending vertically, with openings at both ends axially. The upper frame 41b is fixed to the upper end of the body 41a and blocks the upper opening of the body 41a. The lower frame 41c is fixed to the lower end of the body 41a and blocks the lower opening of the body 41a.

[0101] An inlet pipe 42 is connected to the upper part of the upper frame 41b. The lower end of the inlet pipe 42 opens at the upper part of the internal space of the main body container 41. An outlet pipe 43 is connected to the lower part of the lower frame 41c. The upper end of the outlet pipe 43 extends upward inside the main body container 41 and opens at the upper part of the internal space of the main body container 41.

[0102] The lower end of the outlet pipe 43 extends downward from the lower end of the main body container 41 and bends toward the suction pipe 16 of the compressor body 11 to connect with the suction pipe 16.

[0103] <Dimensional relationships of various components>

[0104] However, to further improve compressor performance, it is desirable to rotate the compressor mechanism 50 at high speed. Here, if the rotational speed of the compressor body 11 is increased, the vibration of the compressor body 11 in the direction of tilting towards the receiver 40 increases proportionally to the square of the rotational speed. As a result, because the axial vibration of the receiver 40 increases, the vibration is transmitted to the entire outdoor unit via the inlet pipe 42, leading to increased noise from the product.

[0105] Therefore, in this embodiment, in order to suppress the increase in vibration of the liquid reservoir 40 even when the rotational speed of the compressor body 11 is increased, the optimal dimensional relationship of various components was studied.

[0106] Figure 5 This is a graph showing the relationship between the rotational speed of the compressor unit in an existing compressor unit and the sound pressure level of the product. For example... Figure 5 As shown, if the rotational speed of the compressor body 11 increases, the noise generated by the product, i.e., the sound pressure level, tends to increase. In the existing compressor unit 10, if the sound pressure level exceeds a first threshold, it is determined that the noise level exceeds the noise standard allowed by the product specifications. The rotational speed of the compressor body 11 at the first threshold is set to 130 rpm.

[0107] A second threshold, lower than the first threshold, was set as a new noise benchmark. When the sound pressure level exceeds the second threshold, it is determined that the noise level exceeds the noise benchmark allowed by the product specifications. The rotational speed of the compressor body 11 at the second threshold is set to 112 rpm.

[0108] Figure 6This is a graph showing the relationship between the rotational speed of the compressor body and the angular acceleration of the compressor unit's rotational vibration about the Y-axis. Here, angular acceleration represents the value of the rotational vibration about the Y-axis caused by the inertial force of the piston 54 and vanes 57, when the Y-axis is taken as the center of rotation passing through the center of gravity G1 of the compressor unit 10, which is the center of rotation when the compressor body 11 vibrates in a direction inclined towards the liquid receiver 40. The inertial force of the piston 54 and vanes 57 is proportional to the value obtained by multiplying the weight of the piston 54 and vanes 57 by the square of the rotational speed.

[0109] like Figure 6 As shown, in a conventional compressor unit used as a comparative example, with the compressor body 11 rotating at a speed of 140 rpm, the angular acceleration is 241 rad / s². 2 Here, in Figure 5 In the study, the compressor body 11, which was used as a reference for sound pressure level, had a rotational speed of 130 rpm and an angular acceleration of 208 rad / s². 2 With the compressor body 11 rotating at 112 rpm, the angular acceleration is 154 rad / s². 2 .

[0110] It should be noted that, in the following description, the speed of the compressor body 11 above the specified speed is referred to as the maximum speed. The specified speed is 112 rpm or higher, preferably 130 rpm or higher. The maximum speed of the compressor body 11 refers to the highest speed that can occur within the operating range of the product.

[0111] Here, the purpose of this embodiment is to suppress the value of rotational vibration about the Y-axis caused by the inertial force of the piston 54 and the blade 57, i.e., angular acceleration, compared with existing compressor units.

[0112] Therefore, in the compressor unit 10 of this embodiment, in order to suppress the rotational vibration around the Y-axis caused by the inertial force of the piston 54 and the blade 57 at the highest speed of the compressor body 11 of 140 rpm to the value of the rotational vibration at 130 rpm, the vibration value needs to be 208 / 241 = 0.86 times.

[0113] In order to suppress the rotational vibration around the Y-axis caused by the inertial force of the piston 54 and the blade 57 at the maximum speed of 140 rpm of the compressor body 11 to the value of the rotational vibration at 112 rpm, the vibration value needs to be 154 / 241 = 0.64 times.

[0114] Figure 7This is a graph showing the relationship between the rated capacity of the refrigeration device and the parameter F×(h / I)×L. In this embodiment, F×(h / I)×L is defined as a parameter representing the magnitude of vibration of the liquid receiver 40 in the vertical direction, and this parameter is set to a value less than the rated capacity P of the refrigeration device 1.

[0115] Specifically, such as Figure 2 As shown, the value obtained by multiplying the weight of piston 54 and blade 57 by the square of the rotational speed of compressor body 11 is denoted as F[kg / s]. 2 Let h [m] be the distance from the center of the piston 54 in the thickness direction to the center of gravity G1 of the compressor unit 10, and let I [kg·m] be the moment of inertia about the center of rotation of the compressor body 11 when it vibrates in the direction of tilting towards the liquid reservoir 40, i.e., the central axis passing through the center of gravity G1 of the compressor unit 10. 2 Let L[m] be the distance from the axis of the inlet pipe 42 of the liquid receiver 40 to the center of gravity G1 of the compressor unit 10, and let P[kW] be the rated capacity of the refrigeration unit 1.

[0116] like Figure 7 As shown in the graph, in the existing compressor unit with the horizontal axis set to x and the vertical axis set to y, when the maximum speed of the compressor body 11 is increased to 140 rpm, the straight line represented by y = 19x + 149 becomes the minimum value line for the parameter F × (h / I) × L. That is, the parameter F × (h / I) × L calculated in the existing single-cylinder compressor unit with one cylinder 51 and the existing double-cylinder compressor unit with two cylinders 51 is located above the straight line shown by y = 19x + 149.

[0117] In contrast, in the compressor unit 10 of this embodiment, the intercept of y = 19x + 149 calculated in a conventional compressor unit is based on... Figure 6 The result calculated from the curve is 0.86 times, that is, the intercept is shifted to 128.

[0118] In this case, in the compressor unit 10 of this embodiment, the parameter F×(h / I)×L is set to satisfy the following formula (1).

[0119] F×(h / I)×L≤19×P+128···(1)

[0120] Thus, by satisfying equation (1), even when the maximum speed of the compressor body 11 is above 130 rpm, the increase in vibration of the liquid receiver 40 can be suppressed.

[0121] In the compressor unit 10 of this embodiment, the intercept of y = 19x + 149 is based on Figure 6The result calculated from the curve is 0.64 times that of the curve, which shifts the intercept to 95.

[0122] Therefore, in the compressor unit 10 of this embodiment, the parameter F×(h / I)×L is set to satisfy the following formula (2).

[0123] F×(h / I)×L≤19×P+95···(2)

[0124] Thus, by satisfying equation (2), even when the maximum speed of the compressor body 11 is above 112 rpm, the increase in vibration of the liquid receiver 40 can be suppressed.

[0125] <Strategies for satisfying conditional expressions>

[0126] The following describes specific countermeasures to make the parameter F×(h / I)×L less than the value set according to the rated capacity P of the refrigeration unit 1.

[0127] First, consider reducing the weight of at least one of the piston 54 and the blade 57. Since the parameter F is proportional to the weight of the piston 54 and the blade 57 multiplied by the square of the rotational speed, reducing the weight of at least one of the piston 54 and the blade 57 will reduce the parameter F.

[0128] For example, in existing compressor units, the density of piston 54 and blade 57 is 7000 kg / m³. 3 Approximately. Therefore, in this embodiment, the density of at least one of the piston 54 and the blade 57 is set to, for example, 7000 × 0.86 = 6020 kg / m³. 3 Therefore, it is set to satisfy equation (1). Specifically, it is preferred that at least one of the piston 54 and the blade 57 is made of aluminum. The density of aluminum is 2700 kg / m³. 3 The conditions are met.

[0129] It is also possible to consider lowering the position of the center of gravity G1 of the compressor unit 10 and reducing the distance h from the center of the piston 54 in the thickness direction to the center of gravity G1 of the compressor unit 10.

[0130] Specifically, Figure 8 This is a graph showing the relationship between the rated capacity of the refrigeration unit and the parameter M1 / M2. Here, let the weight of the lubricating oil filled in the compressor body 11 be M1 [kg], and the weight of the compressor unit 10 be M2 [kg].

[0131] like Figure 8As shown in the graph, with the horizontal axis set to x and the vertical axis set to y, the maximum value line of parameter M1 / M2 in the existing compressor unit is the straight line shown by y = 0.0172x + 0.0418. That is, the parameter M1 / M2 calculated in the existing single-cylinder compressor unit with one cylinder 51 and the existing double-cylinder compressor unit with two cylinders 51 is located below the straight line shown by y = 0.0172x + 0.0418.

[0132] In contrast, in the compressor unit 10 of this embodiment, the parameter M1 / M2 is set to satisfy the following formula (3).

[0133] M1 / M2>0.0172×P+0.0418···(3)

[0134] In this way, by satisfying equation (3), the amount of lubricating oil accumulated at the bottom of the compressor body 11 can be increased, thereby lowering the position of the center of gravity G1 of the compressor unit 10. As a result, the value of parameter F×(h / I)×L can be reduced.

[0135] By adjusting the shape of the counterweight 30, the phenomenon of oil rising can be suppressed, and the amount of lubricating oil accumulated at the bottom of the compressor body 11 can be increased.

[0136] like Figure 3 As shown, the counterweight 30 has a circumferentially extending annular counterweight body 31. On the surface of the counterweight body 31 near the rotor 23, a circumferentially extending recess 31a is formed.

[0137] In this way, the counterweight 30 is formed as a ring extending circumferentially. That is, the counterweight 30 becomes a continuous shape in the circumferential direction, so that the refrigerant containing lubricating oil is difficult to be stirred during the rotation of the rotor 23.

[0138] Therefore, even when the counterweight 30 rotates together with the rotor 23, the phenomenon of lubricating oil rising due to being swept up by the counterweight 30 can be suppressed. As a result, the amount of lubricating oil remaining at the bottom of the compressor body 11 can be adequately ensured, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0139] Alternatively, the distance h from the center of the piston 54 in the thickness direction to the center of the compressor unit 10 can be reduced by lowering the position of the center of gravity G2 of the motor 21 and the position of the center of gravity G1 of the compressor unit 10.

[0140] Specifically, Figure 9This is a graph showing the relationship between the rated capacity of the refrigeration device and the parameter hm / h. Here, the distance from the center of the piston 54 in the thickness direction to the center of gravity G2 of the motor 21 is hm [m].

[0141] like Figure 9 As shown in the graph, with the horizontal axis set to x and the vertical axis to y, in the existing compressor unit, the straight line represented by y = 0.0288x + 1.0673 represents the minimum value for the parameter hm / h. That is, the parameter hm / h calculated in the existing single-cylinder compressor unit with one cylinder 51 and the existing double-cylinder compressor unit with two cylinders 51 is located above the straight line represented by y = 0.0288x + 1.0673.

[0142] In contrast, in the compressor unit 10 of this embodiment, the parameter hm / h is set to satisfy the following equation (4).

[0143] hm / h<0.0288×P+1.0673···(4)

[0144] In this way, by satisfying equation (4), the position of the center of gravity G2 of the motor 21 can be lowered, and the position of the center of gravity G1 of the compressor unit 10 can be lowered.

[0145] -Effects of the implementation method-

[0146] According to the features of this embodiment, the value F obtained by multiplying the weight of piston 54 and blade 57 by the square of the rotational speed of compressor body 11, the distance h from the center of piston 54 in the thickness direction to the center of gravity G1 of compressor unit 10, the moment of inertia I about the center of rotation when compressor body 11 vibrates in the direction of tilting towards liquid receiver 40, i.e., the central axis passing through the center of gravity G1 of compressor unit 10, the distance L from the axis of inlet pipe 42 of liquid receiver 40 to the center of gravity G1 of compressor unit 10, and the rated capacity P of refrigeration device 1 satisfy the condition F×(h / I)×L≤19×P+128.

[0147] In this way, F×(h / I)×L is defined as a parameter representing the magnitude of vibration of the liquid reservoir 40 in the vertical direction, and this parameter is set to a value less than the rated capacity P of the refrigeration unit 1.

[0148] Therefore, even when the speed of the compressor body 11 is increased, the vibration of the liquid receiver 40 can be suppressed.

[0149] According to the features of this embodiment, by satisfying the condition F×(h / I)×L≤19×P+95, the increase in vibration of the reservoir 40 can be further suppressed.

[0150] According to the features of this embodiment, by increasing the rotational speed of the compressor body 11 to 112 rpm or more, the compressor performance can be improved, and the increase in vibration of the liquid receiver 40 can be suppressed even in the high-speed rotation region.

[0151] According to the features of this embodiment, by increasing the rotational speed of the compressor body 11 to 130 rpm or more, the compressor performance can be further improved, and the vibration increase of the liquid receiver 40 can be suppressed even in the high-speed rotation region.

[0152] According to the features of this embodiment, even the single-cylinder compressor body 11, which has particularly large vibration problems in the high-speed rotation area, can suppress the increase of vibration of the liquid receiver 40.

[0153] According to the features of this embodiment, by making the density of at least one of the piston 54 and the blade 57 6020 kg / m³ 3 The following method achieves lightweighting by reducing parameter F, which in turn reduces the value of parameter F×(h / I)×L.

[0154] According to the features of this embodiment, lightweighting is achieved by making at least one of the piston 54 and the blade 57 of aluminum, thereby reducing parameter F.

[0155] According to the features of this embodiment, by ensuring that the weight M1 of the lubricating oil filled in the compressor body 11 and the weight M2 of the compressor unit 10 satisfy the condition M1 / M2 > 0.0172 × P + 0.0418, the amount of lubricating oil accumulated at the bottom of the compressor body 11 can be increased, thereby lowering the position of the center of gravity G1 of the compressor unit 10. This, in turn, reduces the value of the parameter F × (h / I) × L.

[0156] According to the features of this embodiment, the counterweight 30 has an annular counterweight body 31 extending circumferentially at the axial end of the rotor 23. A circumferentially extending recess 31a is formed on the surface of the counterweight body 31 on the side of the rotor 23.

[0157] In this way, the counterweight 30 is formed into a circumferentially extending ring. That is, the counterweight 30 becomes a continuous shape in the circumferential direction, making it difficult for the refrigerant containing lubricating oil to be stirred during the rotation of the rotor 23.

[0158] Therefore, even when the counterweight 30 rotates together with the rotor 23, the phenomenon of lubricating oil rising due to being swept up by the counterweight 30 can be suppressed. As a result, the amount of lubricating oil remaining at the bottom of the compressor body 11 can be adequately ensured, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0159] According to the features of this embodiment, by making the distance hm from the center of the piston 54 in the thickness direction to the center of gravity G2 of the motor 21 satisfy the condition hm / h < 0.0288×P+1.0673, the position of the center of gravity G2 of the motor 21 can be lowered, and the position of the center of gravity G1 of the compressor unit 10 can be lowered.

[0160] According to the features of this embodiment, it includes a compressor unit 10 and a refrigerant circuit 1a for the refrigerant compressed by the compressor unit 10 to flow. Therefore, a refrigeration apparatus 1 including the compressor unit 10 can be provided.

[0161] (Variation Example 1)

[0162] Hereinafter, the same symbols will be used to mark the parts that are the same as those in the above embodiments, and only the different parts will be described.

[0163] like Figure 10 and Figure 11 As shown, the counterweight 30 has a counterweight body 31 and a counterweight cover 32. The counterweight body 31 is formed as an arc extending circumferentially at the axial end of the rotor 23.

[0164] The counterweight cover 32 has a cover body 32a, an inner peripheral wall 32b, and an outer peripheral wall 32c. The cover body 32a is formed of an annular plate. The inner peripheral wall 32b is erected along the inner peripheral edge of the cover body 32a. The outer peripheral wall 32c is erected along the outer peripheral edge of the cover body 32a. The counterweight body 31 is covered by the cover body 32a, the inner peripheral wall 32b, and the outer peripheral wall 32c of the counterweight cover 32.

[0165] - Effect of Variation Example 1 -

[0166] According to the features of this modified example, the counterweight 30 has a counterweight body 31 and a counterweight cover 32. The counterweight body 31 is covered by the annular counterweight cover 32. That is, the counterweight 30 has a continuous shape in the circumferential direction, making it difficult for the refrigerant containing lubricating oil to be stirred during the rotation of the rotor 23.

[0167] Therefore, even when the counterweight 30 rotates together with the rotor 23, the phenomenon of lubricating oil rising due to being swept up by the counterweight 30 can be suppressed. As a result, the amount of lubricating oil remaining at the bottom of the compressor body 11 can be adequately ensured, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0168] (Variation Example 2)

[0169] like Figure 12 As shown, the compression mechanism 50 has a front cylinder head 52 disposed below the motor 21. The front cylinder head 52 has an upwardly extending flange 52b to support the drive shaft 25.

[0170] A recess 23a is formed at the center of the lower end of the rotor 23. The upper end of the flange 52b is inserted into the recess 23a of the rotor 23. Thus, when viewed radially, the lower end of the rotor 23 and the upper end of the flange 52b overlap.

[0171] - Effect of Variation Example 2 -

[0172] According to the features of this modified example, by arranging the lower end of the rotor 23 and the upper end of the flange 52b to overlap when viewed radially, the position of the center of gravity G2 of the motor 21 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0173] (Variation Example 3)

[0174] like Figure 13 As shown, the reservoir 40 has a partition 65. The partition 65 is formed of an annular plate. The outlet pipe 43 of the reservoir 40 is inserted into a hole in the center of the partition 65. The partition 65 divides the interior of the reservoir 40 vertically. The partition 65 is positioned below the axial center of the reservoir 40.

[0175] - Effect of variation example 3 -

[0176] According to the features of this modified example, by arranging the partition 65 at a position lower than the axial center position of the reservoir 40, the center of gravity of the reservoir 40 is lowered, thereby enabling the center of gravity G1 of the compressor unit 10 to be lowered.

[0177] (Variation Example 4)

[0178] like Figure 14 As shown, a weight component 66 is provided on the outlet pipe 43 of the reservoir 40. By installing the weight component 66 on the outlet pipe 43, the center of gravity of the reservoir 40 is lowered. This, in turn, lowers the center of gravity G1 of the compressor unit 10.

[0179] - Effect of variation example 4 -

[0180] According to the features of this modified example, by providing a weight component 66 on the outlet pipe 43 of the reservoir 40, the center of gravity of the reservoir 40 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0181] (Variation Example 5)

[0182] like Figure 15 As shown, the compression mechanism 50 has a rear cylinder head 53 disposed at the lower part of the cylinder 51. The rear cylinder head 53 protrudes radially outward and is tightly engaged with the inner circumferential surface of the housing 12 of the compressor body 11. The rear cylinder head 53 is fixed to the inner circumferential surface of the housing 12 of the compressor body 11.

[0183] - Effect of variation example 5 -

[0184] According to the features of this modified example, by fixing the rear cylinder head 53 to the inner circumferential surface of the housing 12 of the compressor body 11, the weight of the rear cylinder head 53 can be increased, and the position of the center of gravity G1 of the compressor unit 10 can be lowered.

[0185] (Other implementation methods)

[0186] The above implementation method can also adopt the following structure.

[0187] In this embodiment, it is assumed that the body 12a, upper bowl 12b, and lower bowl 12c of the housing 12 of the compressor body 11 are formed with the same plate thickness, but it is not limited to this method. For example, it may be configured such that the plate thickness of the lower bowl 12c is thicker than that of the upper bowl 12b.

[0188] In this way, by making the plate thickness of the lower bowl portion 12c of the housing 12 greater than the plate thickness of the upper bowl portion 12b, the center of gravity of the compressor body 11 is lowered, thereby lowering the position of the center of gravity G1 of the compressor unit 10.

[0189] In this embodiment, it is envisioned that the body 41a, upper frame 41b, and lower frame 41c of the main body container 41 of the liquid reservoir 40 are formed with the same plate thickness, but it is not limited to this method. For example, it is also possible to configure the lower frame 41c to be thicker than the upper frame 41b.

[0190] In this way, by making the plate thickness of the lower frame 41c of the reservoir 40 thicker than the plate thickness of the upper frame 41b, the center of gravity of the reservoir 40 is lowered, thereby lowering the center of gravity G1 of the compressor unit 10.

[0191] In this embodiment, a rotary piston compressor in which the piston 54 and blade 57 are integrally formed has been described. However, a rotary compressor in which the piston 54 and blade 57 are separately formed can also be described. In this case, the parameter F can be calculated by multiplying the weight of the piston 54 and blade 57 by the square of the rotational speed of the compressor body 11. It should be noted that in the case of a rotary compressor in which the piston 54 and blade 57 are separately formed, since it is not necessary to support the blade 57 in a way that allows it to oscillate, the bushing 58 is not required.

[0192] Furthermore, in this embodiment, a single-cylinder compressor with one cylinder 51 has been described. However, the conditional expression of parameter F×(h / I)×L can also be applied to a double-cylinder compressor with two cylinders 51 arranged in the vertical direction.

[0193] Specifically, such as Figure 16 As shown, the value obtained by multiplying the weight of the upper piston 54 and blade 57 by the square of the rotational speed of the compressor body 11 is defined as F1, and the value obtained by multiplying the weight of the lower piston 54 and blade 57 by the square of the rotational speed of the compressor body 11 is defined as F2. The distances from the center of the upper and lower pistons 54 in the thickness direction to the center of gravity G1 of the compressor unit 10 are defined as h1 and h2, respectively.

[0194] Here, if the sum of F1 and F2 is set as F, then F = F1 + F2. If the sum of the torques of the forces about the center of gravity is set as F × h, then F × h = F1 × h1 + F2 × h2. Therefore, the following equation (5) holds.

[0195] h=h1×F1 / (F1+F2)+h2×F2 / (F1+F2) · · · (5)

[0196] Compressors with three or more cylinders 51 can also be used with the conditional formula of parameter F×(h / I)×L.

[0197] Specifically, in the case of a compressor with n cylinders 51, the values ​​obtained by multiplying the weight of each piston 54 and blade 57 by the square of the rotational speed of the compressor body 11 are denoted as F1, F2, F3, ... Hereinafter, the value obtained by multiplying the weight of the i-th piston 54 and blade 57 by the square of the rotational speed of the compressor body 11 is denoted as Fi.

[0198] Furthermore, the distances from the center of the piston 54 in the thickness direction to the center of gravity G1 of the compressor unit 10 are respectively defined as h1, h2, h3, ... Hereinafter, the distance from the i-th piston 54 to the center of gravity G1 is defined as hi.

[0199] Here, if the sum of F1, F2, F3, ... is set as F, then F = F1 + F2 + F3 + ... = ΣFi. If the sum of the torques of the forces about the center of gravity is set as F × h, then F × h = F1 × h1 + F2 × h2 + F3 × h3 + ... = Σ(Fi × hi). Therefore, the following equation (6) holds.

[0200] h=(1 / F)×Σ(Fi×hi)···(6)

[0201] In this embodiment, the parameter F×(h / I)×L is set according to the rated capacity P[kW] of the refrigeration device 1, but it is not limited to this method. For example, the parameter F×(h / I)×L can also be set according to the volume V[cc] of the cylinder 51 and the rotational speed N[rps] of the compressor body 11 at a specified speed or above.

[0202] Figure 17This is a graph showing the relationship between the product of cylinder volume and compressor body speed V×N and the parameter F×(h / I)×L. In this embodiment, F×(h / I)×L is defined as a parameter representing the magnitude of vibration of the reservoir 40 in the vertical direction. This parameter is smaller than the value set based on the product of cylinder volume V and compressor body speed N of compressor body 11, where the compressor body speed N is above a specified speed.

[0203] like Figure 17 As shown in the graph, in the existing compressor unit with the horizontal axis set as x and the vertical axis set as y, when the maximum speed of the compressor body 11 is increased to 140 rpm, the straight line represented by y = 0.063x + 133 becomes the minimum value line for the parameter F×(h / I)×L. That is, the parameter F×(h / I)×L calculated in the existing single-cylinder compressor unit with one cylinder 51 and the existing double-cylinder compressor unit with two cylinders 51 is located above the straight line shown by y = 0.063x + 133.

[0204] In contrast, in the compressor unit 10 of this embodiment, the intercept of y = 0.063x + 133 calculated in a conventional compressor unit is based on... Figure 6 The result calculated from the curve is 0.86 times, that is, the intercept is shifted to 114.

[0205] In this case, in the compressor unit 10 of this embodiment, the parameter F×(h / I)×L is set to satisfy the following formula (7).

[0206] F×(h / I)×L≤0.063×V×N+114···(7)

[0207] Thus, by satisfying equation (7), even when the maximum speed of the compressor body 11 is above 130 rpm, the increase in vibration of the liquid receiver 40 can be suppressed.

[0208] In the compressor unit 10 of this embodiment, the intercept of y = 0.063x + 133 is based on Figure 6 The result calculated from the curve is 0.64 times, which means that the intercept is shifted to 85.

[0209] Therefore, in the compressor unit 10 of this embodiment, the parameter F×(h / I)×L is set to satisfy the following formula (8).

[0210] F×(h / I)×L≤0.063×V×N+85···(8)

[0211] Thus, by satisfying equation (8), even when the maximum speed of the compressor body 11 is above 112 rpm, the increase in vibration of the liquid receiver 40 can be suppressed.

[0212] The embodiments and variations have been described above, but it should be understood that various changes can be made to the manner and specific circumstances without departing from the spirit and scope of the claims. The embodiments and variations described above can also be appropriately combined or substituted, as long as the function of the object of this disclosure is not affected. The terms "first," "second," "third," etc., used 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.

[0213] -Industry Applicability-

[0214] In summary, this disclosure is useful for compressor units and refrigeration devices.

[0215] - Symbol Explanation -

[0216] 1 Refrigeration unit

[0217] 1a refrigerant circuit

[0218] 10 compressor units

[0219] 11 Compressor body

[0220] 12 shells

[0221] 12a trunk

[0222] 12b Upper Bowl

[0223] 12c lower bowl

[0224] 20 drive mechanism

[0225] 21 motors

[0226] 23 rotors

[0227] 25 drive shafts

[0228] 30 counterweights

[0229] 31 Balanced Weight Main Body

[0230] 31a recess

[0231] 32 counterweight shield

[0232] 32a cover body

[0233] 32b inner peripheral wall

[0234] 32c outer peripheral wall

[0235] 40 liquid storage tank

[0236] 41b Upper frame

[0237] 41c lower frame

[0238] 42 Inlet Pipe

[0239] 43 Outlet Pipe

[0240] 50 compression mechanism

[0241] 51 cylinder

[0242] 52 front cylinder head

[0243] 52b flange portion

[0244] 53 rear cylinder head

[0245] 54 Piston

[0246] 65 partition

[0247] 66 heavy components

Claims

1. A compressor unit installed in a refrigeration device (1) performing a refrigeration cycle, comprising a compressor body (11) having a compression mechanism (50) and a liquid receiver (40) connected to said compressor body (11), characterized in that: The compression mechanism (50) includes: a cylinder (51), a piston (54) that rotates eccentrically within the cylinder (51), and blades (57) that divide the interior of the compression chamber (55) of the cylinder (51) into a low-pressure chamber (55a) and a high-pressure chamber (55b). The values ​​F obtained by multiplying the weight of the piston (54) and the blade (57) by the square of the rotational speed of the compressor body (11), the distance h from the center of the piston (54) in the thickness direction to the center of gravity (G1) of the compressor unit (10), the moment of inertia I about the center of rotation of the compressor body (11) when it vibrates in a direction inclined toward the liquid reservoir (40), i.e., through the center axis of the center of gravity (G1) of the compressor unit (10), the distance L from the axis of the inlet pipe (42) of the liquid reservoir (40) to the center of gravity (G1) of the compressor unit (10), and the rated capacity P of the refrigeration device (1) satisfy the condition F×(h / I)×L≤19×P+128.

2. The compressor unit according to claim 1, characterized in that: The compressor unit satisfies the condition F×(h / I)×L≤19×P+95.

3. A compressor unit installed in a refrigeration device (1) performing a refrigeration cycle, comprising a compressor body (11) having a compression mechanism (50) and a liquid receiver (40) connected to said compressor body (11), characterized in that: The compression mechanism (50) includes: a cylinder (51), a piston (54) that rotates eccentrically within the cylinder (51), and blades (57) that divide the interior of the compression chamber (55) of the cylinder (51) into a low-pressure chamber (55a) and a high-pressure chamber (55b). The following values ​​satisfy the following conditions: F, the weight of the piston (54) and the blade (57) multiplied by the square of the rotational speed of the compressor body (11); h, the distance from the center of the piston (54) in the thickness direction to the center of gravity (G1) of the compressor unit (10); I, the moment of inertia about the center of rotation of the compressor body (11) when it vibrates in a direction inclined toward the reservoir (40), i.e., the central axis passing through the center of gravity (G1) of the compressor unit (10); L, the distance from the axis of the inlet pipe (42) of the reservoir (40) to the center of gravity (G1) of the compressor unit (10); V, the volume of the cylinder (51); and N, the rotational speed of the compressor body (11) above the specified speed, satisfying the condition F×(h / I)×L≤0.063×V×N+114.

4. The compressor unit according to claim 3, characterized in that: The compressor unit satisfies the condition F×(h / I)×L≤0.063×V×N+85.

5. The compressor unit according to any one of claims 1 to 4, characterized in that: The specified speed of the compressor body (11) is above 112 rpm.

6. The compressor unit according to claim 5, characterized in that: The specified speed of the compressor body (11) is above 130 rpm.

7. The compressor unit according to claim 6, characterized in that: The compressor body (11) is a single-cylinder type.

8. The compressor unit according to any one of claims 1 to 7, characterized in that: The density of at least one of the piston (54) and the blade (57) is 6020 kg / m³. 3 the following.

9. The compressor unit according to claim 8, characterized in that: At least one of the piston (54) and the blade (57) is made of aluminum.

10. The compressor unit according to any one of claims 1 to 9, characterized in that: The weight M1 of the lubricating oil filled in the compressor body (11) and the weight M2 of the compressor unit (10) satisfy the condition M1 / M2>0.0172×P+0.0418.

11. The compressor unit according to any one of claims 1 to 10, characterized in that: The compressor unit includes a drive mechanism (20) that drives the compression mechanism (50). The drive mechanism (20) includes: a drive shaft (25); a motor (21) having a rotor (23) for rotating the drive shaft (25); and a counterweight (30) disposed on the rotor (23). The counterweight (30) has an annular counterweight body (31) extending circumferentially from the axial end of the rotor (23). A circumferentially extending recess (31a) is formed on the surface of the counterweight body (31) on the side of the rotor (23).

12. The compressor unit according to any one of claims 1 to 10, characterized in that: The compressor unit includes a drive mechanism (20) that drives the compression mechanism (50). The drive mechanism (20) includes: a drive shaft (25); a motor (21) having a rotor (23) for rotating the drive shaft (25); and a counterweight (30) disposed on the rotor (23). The counterweight (30) has a counterweight body (31) and a counterweight cover (32). The counterweight body (31) is formed in the shape of an arc extending circumferentially from the axial end of the rotor (23). The counterweight cover (32) has an annular cover body (32a), an inner peripheral wall (32b) erected along the inner periphery of the cover body (32a), and an outer peripheral wall (32c) erected along the outer periphery of the cover body (32a). The counterweight body (31) is covered by the cover body (32a), the inner peripheral wall (32b), and the outer peripheral wall (32c) of the counterweight cover (32).

13. The compressor unit according to any one of claims 1 to 12, characterized in that: The compressor unit includes a drive mechanism (20) that drives the compression mechanism (50). The drive mechanism (20) includes: a drive shaft (25); and a motor (21) having a rotor (23) that rotates the drive shaft (25). The distance hm from the center of the piston (54) in the thickness direction to the center of gravity (G2) of the motor (21) satisfies the condition hm / h < 0.0288 × P + 1.0673.

14. The compressor unit according to claim 13, characterized in that: The compression mechanism (50) has a front cylinder head (52) arranged below the motor (21). The front cylinder head (52) has an upwardly extending flange (52b) to support the drive shaft (25). The lower end of the rotor (23) and the upper end of the flange (52b) overlap when viewed from the radial direction.

15. The compressor unit according to any one of claims 1 to 14, characterized in that: The reservoir (40) has an upper frame (41b) and a lower frame (41c) disposed below the upper frame (41b). The thickness of the lower frame (41c) is greater than that of the upper frame (41b).

16. The compressor unit according to any one of claims 1 to 15, characterized in that: The reservoir (40) has a partition (65) that separates the interior of the reservoir (40) vertically. The partition (65) is positioned below the axial center of the reservoir (40).

17. The compressor unit according to any one of claims 1 to 16, characterized in that: A weight component (66) is provided on the outlet pipe (43) of the reservoir (40).

18. The compressor unit according to any one of claims 1 to 17, characterized in that: The compression mechanism (50) has a rear cylinder cover (53) arranged at the lower part of the cylinder (51). The rear cylinder head (53) is fixed to the inner circumferential surface of the housing (12) of the compressor body (11).

19. The compressor unit according to any one of claims 1 to 18, characterized in that: The compressor body (11) housing (12) has a cylindrical body (12a), an upper bowl (12b) that blocks the upper opening of the body (12a), and a lower bowl (12c) that blocks the lower opening of the body (12a). The thickness of the lower bowl portion (12c) is greater than that of the upper bowl portion (12b).

20. A refrigeration device, characterized in that: The refrigeration device includes a compressor unit (10) as described in any one of claims 1 to 19, and a refrigerant circuit (1a) in which the refrigerant compressed by the compressor unit (10) flows.

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