Refrigerator

Abstract

To provide a refrigerator which can improve the efficiency of a refrigeration cycle.SOLUTION: A refrigerator 100 comprises a compressor, a condenser, a flow rate adjustment valve, a capillary tube 4, a cooler, a suction pipe 6, and a plurality of holders 10. The capillary tube 4 has a first pipe 41 and a second pipe 42 which are arranged in the suction pipe 6. Each of the holders 10 holds the first pipe 41 and the second pipe 42. The first pipe 41 and the second pipe 42 are spirally twisted around an axial core A of the suction pipe 6 in the suction pipe 6, arranged at an interval therebetween, and also arranged over the entire length of the suction pipe 6 at an interval from an inner face of the suction pipe 6.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present disclosure relates to refrigerators. [Background technology]

[0002] Conventionally, in refrigerators, a high-pressure refrigerant is decompressed using a capillary tube. In refrigerators, in order to improve cooling efficiency, heat exchange is performed between a low-temperature refrigerant flowing through a suction pipe and a refrigerant flowing through a capillary tube. This allows the enthalpy of the low-temperature refrigerant to be recovered, thereby improving the efficiency of the refrigeration cycle. By lengthening the capillary tube, the amount of heat recovered can be increased, and the supercooling region can be expanded. This allows the efficiency of the refrigeration cycle to be improved by improving the cooling capacity. However, when the capillary tube and the suction pipe are the same length, the suction pipe is necessarily longer as the capillary tube becomes longer. This increases the pressure loss of the low-pressure side refrigerant, thereby reducing the efficiency of the refrigeration cycle.

[0003] Japanese Patent Laid-Open Publication No. 2006-189249 (Patent Document 1) proposes a double-pipe heat exchanger that exchanges heat between a primary refrigerant (freon) and a secondary refrigerant (water). In this double-pipe heat exchanger, a circular cross-section outer pipe is fitted with a number of inner pipes that are each twisted in a spiral shape around the axis of the outer pipe and through which the primary refrigerant flows, and spacers that are positioning members are arranged at predetermined intervals. This keeps the gaps between the inner pipes and between the inner surface of the outer pipe and the inner pipe constant. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2006-189249 A Summary of the Invention [Problem to be solved by the invention]

[0005] The double-pipe heat exchanger of the above publication does not disclose a means for the spacer to keep the gap between the inner surface of the outer pipe and the inner pipe constant over the entire length. Therefore, there is a problem that the heat exchange performance between the primary refrigerant (freon) and the secondary refrigerant (water) is reduced due to contact between the inner surface of the outer pipe and the inner pipe. Therefore, when the outer pipe of the double-pipe heat exchanger of the above publication is used as a suction pipe and the multiple spiral inner pipes are used as capillary tubes, there is a problem that the efficiency of the refrigeration cycle is reduced due to the reduced heat exchange performance between the low-temperature refrigerant flowing through the suction pipe and the refrigerant flowing through the capillary tubes.

[0006] The present disclosure has been made in consideration of the above-mentioned problems, and has an object to provide a refrigerator capable of improving the efficiency of the refrigeration cycle. [Means for solving the problem]

[0007] The refrigerator of the present disclosure includes a compressor for compressing a refrigerant, a condenser for condensing the refrigerant compressed by the compressor, a flow rate control valve for controlling the flow rate of the refrigerant condensed by the condenser, a capillary tube for reducing the pressure of the refrigerant whose flow rate is controlled by the flow rate control valve, a cooler for evaporating the refrigerant reduced in pressure by the capillary tube, a suction pipe for feeding the refrigerant evaporated by the cooler to the compressor, and a plurality of holders for holding the capillary tube in the suction pipe. The capillary tube has a first tube and a second tube arranged in the suction pipe. Each of the plurality of holders holds the first tube and the second tube. The first tube and the second tube are spirally twisted around the axis of the suction pipe in the suction pipe, and are arranged with a gap between them, and are arranged with a gap from the inner surface of the suction pipe over the entire length of the suction pipe. Effect of the Invention

[0008] According to the refrigerator of the present disclosure, the efficiency of the refrigeration cycle can be improved. [Brief description of the drawings]

[0009] [Figure 1] 1 is an overall configuration diagram of a refrigerator according to a first embodiment. [Diagram 2] 2 is a schematic cross-sectional view in a radial direction of a suction pipe of the refrigerator according to embodiment 1. FIG. [Diagram 3] 2 is a schematic cross-sectional view in a radial direction and a longitudinal direction of a suction pipe of a refrigerator according to embodiment 1. FIG. [Figure 4] 3 is a schematic cross-sectional view showing the arrangement of capillary tubes in the radial direction of the suction pipe according to the first embodiment. FIG. [Diagram 5] FIG. 4 is a schematic cross-sectional view in a radial direction of a suction pipe of a comparative example. [Figure 6] 11 is a schematic cross-sectional view in the longitudinal direction of a suction pipe of a refrigerator according to embodiment 2. FIG. [Figure 7] 11 is a schematic cross-sectional view in the length direction of a curved portion of a suction pipe of a refrigerator according to embodiment 2. FIG. [Figure 8] 11 is a schematic cross-sectional view in the length direction of a curved portion of a suction pipe of a modified example of a refrigerator according to embodiment 2. FIG. [Figure 9] 10 is a schematic cross-sectional view in the longitudinal direction of a curved portion of a suction pipe of a comparative example. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] Hereinafter, an embodiment will be described with reference to the drawings. In the drawings, the same or corresponding parts are designated by the same reference characters and description thereof will not be repeated.

[0011] Embodiment 1 A configuration of a refrigerator 100 according to the first embodiment will be described with reference to FIG. 1. FIG. 1 is an overall configuration diagram of the refrigerator 100 according to the first embodiment. The refrigerator 100 according to the first embodiment includes a compressor 1, a condenser 2, a flow rate control valve 3, a capillary tube 4, a cooler 5, and a suction pipe 6. In this embodiment, the refrigerator 100 further includes a condenser pipe 7, a cabinet pipe 8, and a dryer 9. The compressor 1, the condenser 2, the flow rate control valve 3, the capillary tube 4, the cooler 5, the suction pipe 6, the condenser pipe 7, the cabinet pipe 8, and the dryer 9 configure a refrigerant circuit RC. The refrigerant circuit RC is configured so that a refrigerant flows in the order of the compressor 1, the condenser 2, the condenser pipe 7, the cabinet pipe 8, the dryer 9, the flow rate control valve 3, the capillary tube 4, the cooler 5, and the suction pipe 6.

[0012] The refrigerant circuit RC is provided with a heat exchanger HE. The heat exchanger HE is configured so that heat exchange takes place between the refrigerant flowing through the capillary tube 4 and the refrigerant flowing through the suction pipe 6.

[0013] The compressor 1 is configured to compress the refrigerant. The compressor 1 is configured to compress the sucked refrigerant and discharge the refrigerant. The compressor 1 has a suction side connected to the heat exchange unit HE and a discharge side connected to the condenser 2. The compressor 1 is configured to compress the refrigerant to a high-temperature and high-pressure refrigerant. The compressor 1 may be driven by an inverter and configured to control the operation according to the inside condition of the refrigerator 100.

[0014] The condenser 2 is configured to condense the refrigerant compressed by the compressor 1. The condenser 2 is configured to condense the refrigerant by dissipating heat from the high-temperature, high-pressure refrigerant discharged from the compressor 1. The condenser 2 is connected between the compressor 1 and the condenser pipe 7 in the refrigerant circuit RC.

[0015] The flow rate control valve 3 is configured to adjust the flow rate of the refrigerant condensed by the condenser 2. The flow rate control valve 3 is configured to adjust the flow rate of the refrigerant passing through the flow rate control valve 3. The flow rate control valve 3 is connected between the dryer 9 and the capillary tube 4 in the refrigerant circuit RC. The flow rate control valve 3 is, for example, a solenoid valve. The flow rate control valve 3 is, for example, a three-way valve.

[0016] The capillary tube 4 is configured to reduce the pressure of the refrigerant whose flow rate is adjusted by the flow rate control valve 3. The capillary tube 4 is connected between the flow rate control valve 3 and the cooler 5 in the refrigerant circuit RC. The capillary tube 4 has a first pipe 41 and a second pipe 42 arranged in the suction pipe 6. The first pipe 41 and the second pipe 42 are connected in parallel to the flow rate control valve 3 and the cooler 5.

[0017] The cooler 5 is configured to evaporate the refrigerant decompressed by the capillary tube 4. The cooler 5 functions as an evaporator. The cooler 5 is connected between the capillary tube 4 and the suction pipe 6 in the refrigerant circuit RC.

[0018] The suction pipe 6 is configured to allow the refrigerant evaporated in the cooler 5 to flow to the compressor 1. The suction pipe 6 is connected between the cooler 5 and the compressor 1 in the refrigerant circuit RC. The suction pipe 6 has an inner diameter larger than the sum of the outer diameters of the first pipe 41 and the second pipe 42 of the capillary tube 4.

[0019] The condenser pipe 7 is configured to further condense the refrigerant by dissipating heat from the refrigerant condensed in the condenser 2. The condenser pipe 7 is connected between the condenser 2 and the cabinet pipe 8 in the refrigerant circuit RC.

[0020] The cabinet pipe 8 has a function of condensing the refrigerant. The cabinet pipe 8 is connected between the condenser pipe 7 and the dryer 9 in the refrigerant circuit RC.

[0021] The dryer 9 is configured to adsorb moisture contained in the refrigerant flowing through the refrigerant circuit RC. The dryer 9 is connected between the cabinet pipe 8 and the flow rate control valve 3 in the refrigerant circuit RC.

[0022] An internal structure of suction pipe 6 of refrigerator 100 according to embodiment 1 will be described with reference to Fig. 2 and Fig. 3. Fig. 2 is a schematic cross-sectional view in a radial direction of suction pipe 6 of refrigerator 100 according to embodiment 1. Fig. 3 is a schematic cross-sectional view in a radial direction and a length direction of suction pipe 6 of refrigerator 100 according to embodiment 1.

[0023] 2, a first tube 41 and a second tube 42 of the capillary tube 4 are disposed in the suction pipe 6. The first tube 41 has a larger inner diameter than the second tube 42. The first tube 41 is a thick tube. The second tube 42 is a thin tube. The first tube 41 may have the same inner diameter as the second tube 42. The first tube 41 and the second tube 42 are disposed on either side of the axis A of the suction pipe 6.

[0024] Refrigerator 100 according to the first embodiment includes a plurality of holders 10. The plurality of holders 10 are configured to hold capillary tubes 4 inside suction pipe 6. Each of the plurality of holders 10 holds a first tube 41 and a second tube 42. Holder 10 has a fixing portion 11, a support portion 12, a first holding portion 13, and a second holding portion 14.

[0025] The fixed part 11 is fixed to the inner surface of the suction pipe 6. The fixed part 11 is configured in an annular shape. The outer peripheral surface of the fixed part 11 is in contact with the inner peripheral surface of the suction pipe 6. The support part 12 is disposed inside the fixed part 11. The support part 12 has two support members that extend in the radial direction of the fixed part 11 and are perpendicular to each other. The support part 12 is configured to support a first holding part 13 and a second holding part 14.

[0026] The first holding part 13 and the second holding part 14 are disposed inside the fixed part 11. The first holding part 13 and the second holding part 14 are disposed between the inner peripheral surface of the fixed part 11 and the axis A of the suction pipe 6 in the radial direction of the suction pipe 6. The first holding part 13 is configured to hold the first tube 41 of the capillary tube 4. The first holding part 13 is configured in an annular shape. The inner peripheral surface of the first holding part 13 is in contact with the outer peripheral surface of the first tube 41. The second holding part 14 is configured to hold the second tube 42 of the capillary tube 4. The second holding part 14 is configured in an annular shape. The inner peripheral surface of the second holding part 14 is in contact with the outer peripheral surface of the second tube 42.

[0027] 3, the multiple holders 10 are arranged at intervals from one another in the longitudinal direction of the suction pipe 6. The first tube 41 and the second tube 42 of the capillary tube 4 are arranged in a coil shape by arranging the multiple holders 10 at different angles with respect to the axis A of the suction pipe 6. The first tube 41 and the second tube 42 are twisted in a spiral shape around the axis A of the suction pipe 6 inside the suction pipe 6.

[0028] The first pipe 41 and the second pipe 42 are arranged with a gap between them. The first pipe 41 and the second pipe 42 are arranged so as not to contact each other. The first pipe 41 and the second pipe 42 are arranged with a gap between them and the inner surface of the suction pipe 6 over the entire length of the suction pipe 6. The first pipe 41 and the second pipe 42 are arranged so as not to contact the inner surface of the suction pipe 6 over the entire length of the suction pipe 6.

[0029] The first pipe 41 and the second pipe 42 are arranged point-symmetrically with respect to each other around the axis A of the suction pipe 6. The first pipe 41 and the second pipe 42 are arranged on a straight line with respect to the axis A of the suction pipe 6. The first pipe 41 and the second pipe 42 are each at a constant distance from the axis A in the radial direction of the suction pipe 6. The first pipe 41 and the second pipe 42 are each at a constant distance from the inner surface of the suction pipe 6 in the radial direction of the suction pipe 6.

[0030] 3 and 4, the positions of the first holding portion 13 and the second holding portion 14 in the radial direction of the suction pipe 6 are the same in the longitudinal direction of the suction pipe 6. Each of the multiple holding devices 10 is arranged at a different angle from the adjacent holding devices 10. When the holding devices 10 are arranged at different angles in the cross-sectional direction of the suction pipe 6, the projection planes overlap every 360 degrees. As a result, regardless of the number of capillary tubes 4 inserted into the suction pipe 6, the area occupied by the capillary tubes 4 does not increase in the projection diagram in the cross-sectional direction of the suction pipe 6. Therefore, an increase in pressure loss can be prevented.

[0031] Next, the effects of the refrigerator 100 according to the first embodiment will be described in comparison with a comparative example.

[0032] 5, in the internal structure of the suction pipe 6 of the comparative example, the capillary tube 4 arranged in the suction pipe is not held by a holder. Therefore, there is a possibility that other capillary tubes 4 are arranged in close proximity to the capillary tube 4. In this case, if the refrigerant flows through the capillary tube 4 in contact with the inner surface of the suction pipe 6 and the refrigerant does not flow through the other capillary tubes 4, the heat dissipation of the capillary tube 4 through which the refrigerant flows is hindered by the other capillary tubes 4. This reduces the amount of heat exchange between the refrigerant flowing through the capillary tube 4 and the refrigerant flowing through the suction pipe 6.

[0033] According to the refrigerator 100 of this embodiment, the capillary tube 4 has the first tube 41 and the second tube 42 arranged in the suction pipe 6. The first tube 41 and the second tube 42 are arranged with a gap between them. The first tube 41 and the second tube 42 are arranged with a gap between them from the inner surface of the suction pipe 6 over the entire length of the suction pipe 6. Therefore, the first tube 41 and the second tube 42 can be arranged so that the outer surface of the first tube 41 and the outer surface of the second tube 42 do not contact each other. Also, the first tube 41 and the second tube 42 can be arranged so that the outer surfaces of the first tube 41 and the second tube 42 do not contact the inner surface of the suction pipe 6. Therefore, the heat dissipated in the entire circumferential direction of the capillary tube 4 is heat exchanged with the refrigerant flowing through the suction pipe 6, so that the amount of heat exchange per unit length of the suction pipe 6 is increased. Therefore, the heat exchange performance between the refrigerant flowing through the suction pipe 6 and the refrigerant flowing through the capillary tube 4 can be improved. Therefore, the efficiency of the refrigeration cycle can be improved.

[0034] In addition, since the soldering required when arranging the capillary tube 4 on the outside of the suction pipe 6 is no longer necessary, it is possible to prevent a decrease in the amount of heat exchange caused by the soldering processing precision and the coming off of the adhesive due to aging. Furthermore, since the heat dissipated from the capillary tube 4 is used to increase the temperature of the suction pipe 6, the suction temperature increases and it is possible to prevent condensation on the suction pipe 6. In addition, the reduction in heat leakage into the chamber reduces the thermal load, resulting in an energy saving effect.

[0035] Moreover, the first tube 41 and the second tube 42 are twisted in a spiral shape around the axis A of the suction pipe 6 inside the suction pipe 6. Therefore, by lengthening the capillary tube 4, the amount of heat recovery is increased, and the supercooling region can be expanded. This improves the cooling capacity and improves the efficiency of the refrigeration cycle. Also, the length of the suction pipe 6 can be made shorter than the length of the capillary tube 4. Therefore, the pressure loss of the low-pressure side refrigerant is reduced, and the efficiency of the refrigeration cycle can be improved.

[0036] In refrigerator 100 according to the present embodiment, first tube 41 has an inner diameter smaller than that of second tube 42. Therefore, by flowing a refrigerant through first tube 41 or second tube 42, the pressure can be reduced more precisely.

[0037] In refrigerator 100 according to the present embodiment, first tube 41 and second tube 42 are arranged point-symmetrically with respect to each other around axis A of suction pipe 6. Therefore, a gap between first tube 41 and second tube 42 can be secured.

[0038] In refrigerator 100 according to the present embodiment, first tube 41 and second tube 42 are each located at a constant distance from axis A in the radial direction of suction pipe 6. This makes it possible to ensure a gap between first tube 41 and second tube 42 and the inner surface of suction pipe 6.

[0039] Embodiment 2 Unless otherwise specified, refrigerator 100 according to the second embodiment has the same configuration and functions and effects as refrigerator 100 according to the first embodiment.

[0040] 6, in refrigerator 100 according to the second embodiment, suction pipe 6 has straight portion 61 and curved portion 62. Straight portion 61 is configured in a straight line. Curved portion 62 is connected to straight portion 61. Curved portion 62 is configured in a curved line. Curved portion 62 may be configured in a semicircular shape. The outer diameter of fixing portion 11 of holder 10 arranged at curved portion 62 is smaller than the outer diameter of fixing portion 11 of holder 10 arranged at straight portion 61.

[0041] 7, if the bending radius R, angle, outer diameter X, and wall thickness t of the suction pipe 6 are known, and the width W of the fixed part 11 of the holder 10 is determined, the angles a and b formed by the center of the bending radius R of the suction pipe 6 and both ends of the fixed part 11 of the holder 10, the width W of the fixed part 11 of the holder 10, and the outer diameter (height H) of the suction pipe 6 can be calculated. The number of holders 10 that can be arranged within the angle range of the bending radius R of the suction pipe 6 is set to a value smaller than the angle of the bending radius R of the suction pipe 6 / angle b, so that the suction pipe 6 can be bent without applying excessive load to the fixed part 11.

[0042] For example, assume that the outer diameter X of the suction pipe 6 is 7 mm, the wall thickness t is 0.5 mm, the bending radius R is 25 mm, and the bending radius angle is 180°. If the holder 10 is created so that the angle a between the center of the bending radius and both ends of the fixing part 11 (outside) of the holder 10 is 60°, the length of each part can be calculated by the following formula.

[0043] Width of holder W=(R+Xt)×Sin(a / 2)×2 =(25+7-0.5)×sin(60° / 2)×2=31.5 Distance Hi from the center of bending radius R to the inside of the holder 10 = R + t =25+0.5=25.5 Distance Ho from the center of bending radius R to the outside of the holder 10 = (R + Xt) × cos(a / 2) =(25+7-0.5)×cos(60° / 2)=27.28 Height of holder 10 H=Ho-Hi =27.28-25.5=1.78 Angle b between the center of bending radius R and both ends of fixing part 11 (inner side) of holder 10 =tan -1 (W / 2 / Hi)×180 / π×2 =tan -1 (31.5 / 2 / 25.5)×180 / π×2=63.4 The number of holders that can be installed within the bending radius R angle c = 180° = c / b =180 / 63.4≒2.8 For this reason, up to two holders 10 with fixing portion 11 width W = 31.5 mm and height H = 1.78 mm can be placed within this bending radius range. Here, the angle a formed by the center of bending radius R and both ends of the fixing portion (outside) of holder 10 is used as a variable, but the dimensions and angles of each part may be found by using the holder width W or the number of holders 10 to be placed within the bending radius R as a variable.

[0044] Next, the effects of the refrigerator 100 according to the second embodiment will be described.

[0045] According to refrigerator 100 according to the second embodiment, the outer diameter of fixing portion 11 of holder 10 arranged at curved portion 62 is smaller than the outer diameter of fixing portion 11 of holder 10 arranged at straight portion 61. Therefore, even at curved portion 62 of suction pipe 6, first tube 41 and second tube 42 of capillary tube 4 can be prevented from contacting the inner surface of suction pipe 6. Moreover, first tube 41 and second tube 42 of capillary tube 4 can maintain a spiral positional relationship without contacting the inner surface of suction pipe 6.

[0046] By widening the intervals between the multiple holders 10 according to the bending radius of the suction pipe 6, the multiple holders 10 can be arranged regardless of the shape of the suction pipe 6. Furthermore, by narrowing the intervals between the multiple holders 10, the number of turns of the capillary tube 4 per unit length increases, thereby increasing the effect of recovering the enthalpy of the low-temperature refrigerant.

[0047] Next, a modification of the refrigerator 100 according to the second embodiment will be described.

[0048] With reference to FIG. 8, in refrigerator 100 according to the second embodiment, fixing portion 11 of holder 10 arranged in curved portion 62 has an inner width smaller than an outer width. Fixing portion 11 is configured so that its width decreases from the outside toward the inside. Curved portion 62 has inner wall 62a arranged on the side closer to the center of curvature of curved portion 62, and outer wall 62b arranged on the side farther from the center of curvature of curved portion 62. Fixing portion 11 arranged in curved portion 62 has inner portion 11a fixed to inner wall 62a of curved portion 62, and outer portion 11b fixed to outer wall 62b of curved portion 62. The width of inner portion 11a is smaller than the width of outer portion 11b.

[0049] By setting the width of the side of the fixing portion 11 of the holder 10 that comes into contact with the side with the smaller bending diameter to be smaller than the width required by the angle a, the fixing portions 11 of the holder 10 will not come into contact with each other when the suction pipe 6 is bent.

[0050] Next, the effects of the modified example of refrigerator 100 according to the second embodiment will be described in comparison with a comparative example.

[0051] 9, in the internal structure of the suction pipe 6 of the comparative example, the inside width of the fixing portion 11 of the holder 10 arranged in the curved portion 62 is the same as the outside width. Therefore, when the suction pipe 6 is bent, the insides of the fixing portions 11 of the holders 10 adjacent to each other are likely to come into contact with each other.

[0052] According to the modification of refrigerator 100 according to the second embodiment, the inner width of fixing portion 11 of holder 10 arranged at curved portion 62 is smaller than the outer width. This makes it possible to prevent the inner sides of fixing portions 11 of adjacent holders 10 from contacting each other during bending process of suction pipe 6.

[0053] The above-described embodiments can be combined as appropriate.

[0054] The embodiments disclosed herein should be considered to be illustrative and not restrictive in all respects. The scope of the present disclosure is defined by the claims, not the above description, and is intended to include all modifications within the meaning and scope of the claims. [Explanation of symbols]

[0055] 1 compressor, 2 condenser, 3 flow control valve, 4 capillary tube, 5 cooler, 6 suction pipe, 7 condenser pipe, 8 cabinet pipe, 9 dryer, 10 holder, 11 fixed part, 12 support part, 13 first holding part, 14 second holding part, 41 first pipe, 42 second pipe, 61 straight part, 62 curved part, 100 refrigerator, A axis, HE heat exchange part.

Claims

1. A compressor that compresses a refrigerant; a condenser that condenses the refrigerant compressed by the compressor; a flow rate control valve for controlling a flow rate of the refrigerant condensed by the condenser; a capillary tube for reducing the pressure of the refrigerant whose flow rate is adjusted by the flow rate adjustment valve; a cooler that evaporates the refrigerant decompressed by the capillary tube; a suction pipe through which the refrigerant evaporated in the cooler flows to the compressor; a plurality of holders for holding the capillary tube within the suction pipe; the capillary tube has a first tube and a second tube disposed within the suction pipe; each of the plurality of holders holds the first tube and the second tube; the first tube and the second tube are spirally twisted around the axis of the suction pipe within the suction pipe, are arranged with a gap between them, and are arranged with a gap from the inner surface of the suction pipe over the entire length of the suction pipe.

2. 2. The refrigerator according to claim 1, wherein the first tube has a larger inside diameter than the second tube.

3. The refrigerator according to claim 1 or 2, wherein the first pipe and the second pipe are arranged point-symmetrically with respect to each other around the axis of the suction pipe.

4. The refrigerator according to any one of claims 1 to 3, wherein the first pipe and the second pipe are each spaced at a constant distance from the axis in a radial direction of the suction pipe.

5. The suction pipe has a straight portion and a curved portion connected to the straight portion, the holder has a fixing portion that is fixed to the inner surface of the suction pipe, The refrigerator according to any one of claims 1 to 4, wherein an outer diameter of the fixing portion of the holder arranged on the curved portion is smaller than an outer diameter of the fixing portion of the holder arranged on the straight portion.

6. The refrigerator according to claim 5 , wherein an inner width of the fixing portion of the holder arranged on the curved portion is smaller than an outer width of the fixing portion.

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