Refrigerator

Abstract

To provide a refrigerator capable of reducing vibration transmitted from a compressor to a casing of the refrigerator and reducing vibration on the basis of the vibration of the casing.SOLUTION: A refrigerator 1 includes: a compressor 5 disposed on the upper rear side of the refrigerator 1; and a vibration damping member 80 that supports the compressor 5. The vibration damping member 80 is set so that a spring constant thereof varies depending on a vibrating direction of the compressor 5. Thus setting so that the spring constant of the vibration damping member 80 varies depending on the vibrating direction of the compressor 5 can reduce vibration transmitted from the compressor 5 to the refrigerator 1. Accordingly, vibration of a door 14 on the basis of the vibration of a casing 10 can be reduced.SELECTED DRAWING: Figure 3

Description

[Technical field]

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

[0002] Patent Document 1 discloses a refrigerator in which an anti-vibration device has a structure in which three rubber members, upper, middle and lower, are stacked in three layers and joined together by means such as welding into an integrated structure, the middle rubber member has a durometer hardness of less than 40 degrees, and the upper rubber member that comes into contact with the compressor leg members and the lower rubber member that comes into contact with the base member are made of a material harder than the middle rubber member, thereby improving the anti-vibration performance. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2012-057475 A Summary of the Invention [Problem to be solved by the invention]

[0004] The present disclosure provides a refrigerator that can reduce vibrations transmitted from a compressor to a housing of the refrigerator and reduce vibrations of the door caused by vibrations of the housing. [Means for solving the problem]

[0005] The refrigerator of the present disclosure is a refrigerator including a compressor arranged at the upper rear of the refrigerator and a vibration-damping member supporting the compressor, and the vibration-damping member is set to have a different spring constant depending on the vibration direction of the compressor. Effect of the Invention

[0006] In the refrigerator according to the present disclosure, the spring constant of the vibration-proof member is set to be different depending on the vibration direction of the compressor, thereby making it possible to reduce the vibration transmitted from the compressor to the refrigerator, and therefore to reduce the vibration of the door caused by the vibration of the housing. [Brief description of the drawings]

[0007] [Figure 1] FIG. 1 is a vertical cross-sectional view of a refrigerator according to a first embodiment. [Diagram 2] FIG. 1 is a schematic plan view of a refrigerator as viewed from above, showing a support structure for a compressor according to a first embodiment; [Diagram 3] FIG. 1 is a schematic front view showing a support structure for a compressor according to a first embodiment; [Figure 4] FIG. 1 is a schematic diagram showing an input and a transmission force from a compressor in the first embodiment. [Diagram 5] Formula for calculating the natural frequency of the vibration system consisting of the compressor and the vibration-isolating member in the first embodiment [Figure 6] Formula for determining the force transmission rate of the vibration-proof member in embodiment 1 [Figure 7] FIG. 1 is an explanatory diagram showing the relationship between frequency and force transmissibility in the first embodiment. [Figure 8] Equation expressing vibration displacement taking into account phase in embodiment 1 [Figure 9] FIG. 1 is an explanatory diagram showing the relationship between frequency and phase in the first embodiment. [Figure 10] FIG. 1 is a schematic diagram showing input from a compressor and transmission of vibration to a door in the first embodiment. [Figure 11] FIG. 10 is an explanatory diagram showing the relationship between the drive frequency of the compressor and door vibration in each direction in the first embodiment. [Figure 12] FIG. 1 is an explanatory diagram showing the relationship between the front-rear vibration of the door, the compressor input, the force transmission rate of the vibration-proof member, and the transfer function of the housing in the first embodiment. [Figure 13] FIG. 1 is a schematic diagram showing input from a compressor and transmission of vibration to a door in the first embodiment. [Figure 14]FIG. 1 is an explanatory diagram showing the relationship between the front-rear vibration of the door in response to input from the compressor in each direction, the input from the compressor, the force transmission rate of the vibration-proof member, and the transfer function of the housing in the first embodiment. [Figure 15] FIG. 15(a) is a schematic diagram of the housing of the first embodiment vibrating at 18 Hz, and FIG. 15(b) is a schematic diagram of the housing of the first embodiment vibrating at 8 Hz. [Figure 16] FIG. 10 is an explanatory diagram showing a vibration cancellation phenomenon caused by the antiphase of vibration transmission in the front-rear direction and the left-right direction in the first embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0008] (The knowledge and other information that formed the basis of this disclosure) At the time when the inventors came up with the idea of ​​this disclosure, a vibration-damping device for a compressor existed that was made by stacking upper, middle, and lower rubber members in three layers and joining them together by means of welding or the like. However, the inventors discovered a problem in the conventional technology in that vibrations of the compressor are transmitted to the refrigerator as vibrations in the front-back and left-right directions, which may cause the door to vibrate and generate unpleasant noise. In order to solve this problem, the inventors have come up with the subject matter of the present disclosure. The present disclosure provides a refrigerator that can reduce vibrations transmitted from a compressor to a housing of the refrigerator and reduce vibrations of the door caused by vibrations of the housing.

[0009] Hereinafter, the embodiments will be described in detail with reference to the drawings. However, in some cases, more detailed explanations than necessary may be omitted. For example, detailed explanations of already well-known matters or duplicate explanations of substantially the same configurations may be omitted. It should be noted that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims.

[0010] (Embodiment 1) Hereinafter, the first embodiment will be described with reference to the drawings. [1-1. Configuration] [1-1-1. Refrigerator configuration] FIG. 1 is a vertical cross-sectional view of a refrigerator in the first embodiment. In the description of this specification, when referring to the front, back, left and right of the refrigerator 1, the terms will be used based on Fig. 1. In other words, the left and right of Fig. 1 will be described as corresponding to the front and back of the refrigerator 1.

[0011] As shown in Fig. 1, the refrigerator 1 includes a box-shaped housing 10 with an open front. A compressor 5 is mounted on the rear upper surface of the housing 10. A refrigerator compartment 11 with a temperature of about 2°C to 4°C is formed in the upper part of the housing 10 as a storage compartment, and a freezer compartment 12 with a temperature of about -18°C is formed in the lower part of the housing 10. A switchable compartment 13 is formed between the refrigerator compartment 11 and the freezer compartment 12. The switchable compartment 13 can be used as a low-temperature compartment with a temperature of about -5°C to about 1°C or as the freezer compartment 12 by operating a selector switch (not shown).

[0012] In the refrigerator 1, a revolving door 14 is provided at the opening on the front side of the refrigeration compartment 11 so as to be able to be opened and closed freely. At the bottom inside the refrigerator compartment 11, there are provided a vegetable compartment 15 as a storage compartment located on the upper level, and a micro-freezing compartment 16 as a storage compartment located on the lower level. The vegetable compartment 15 is provided with a vegetable compartment pull-out case 17, and the micro-freezing compartment 16 is provided with a micro-freezing compartment pull-out case 18.

[0013] A freezer compartment drawer door 19 is provided at the opening on the front side of the freezer compartment 12 so as to be able to be opened and closed freely, and a freezer compartment drawer case 20 having multiple stages for storing food therein is provided. A switchable compartment drawer door 21 is provided at the opening on the front surface of the switchable compartment 13 so as to be able to be opened and closed freely, and a switchable compartment drawer case 22 is provided which is linked to the opening and closing of the switchable compartment drawer door 21.

[0014] As shown in FIG. 1, a refrigeration cooling compartment 30 is provided on the rear side of the refrigeration compartment 11 of the refrigerator 1. The refrigerator compartment 11 and the refrigerator cooling compartment 30 are separated by a first partition plate 31, and a first molded insulation material 32 having approximately the same outline as the first partition plate 31 is provided on the back side of the first partition plate 31. A refrigeration duct 33 is formed on the surface of the first molded heat insulating material 32 facing the first partition plate 31.

[0015] A second partition plate 50 and a third partition plate 51 are provided between the vegetable compartment 15 and the micro-freezing compartment 16 and the refrigerating cooling compartment 30. A second molded insulating material 52 is provided between the second partition plate 50 and the third partition plate 51. The second partition plate 50, the third partition plate 51 and the second molded insulating material 52 constitute the partition portion of the present disclosure.

[0016] A refrigeration inlet 53 communicating with the slight freezing chamber 16 is formed at the lower ends of the second partition plate 50, the second molded insulating material 52 and the third partition plate 51. A refrigeration cooler 54 is provided below the rear surface side of the second partition plate 50. A blower fan 70 is provided above the second partition plate 50.

[0017] A freezing cooling compartment 60 is provided on the rear side of the freezing compartment 12 and the switchable compartment 13 of the refrigerator 1. The freezing chamber 12 and the freezing cooling chamber 60 are separated by a fourth partition plate 61. The fourth partition plate 61 is formed with a freezing suction port 62 that communicates with the freezing chamber 12 and takes in the cold air from the freezing chamber 12 into the freezing cooling chamber 60. The fourth partition plate 61 is formed with a freezer air outlet 63 communicating with the freezer compartment 12 and a switchable compartment air outlet 64 communicating with the switchable compartment 13.

[0018] The freezing cooling chamber 60 accommodates a freezing cooler 65 . The freezing cooler 65 is, for example, a fin tube type cooler. The fin tube type cooler is, for example, a cooler composed of a circular pipe and flat fins. A freezing fan 66 is disposed above the freezing cooler 65 to send the cold air cooled by the freezing cooler 65 into the freezing chamber 12.

[0019] For example, an axial fan is used as the refrigeration fan 66. The axial fan is disposed at an incline so that the blowing side faces upward so that the cold air cooled by the refrigeration cooler 65 can be efficiently blown out into the freezing chamber 12. The refrigeration fan 66 may be, for example, a centrifugal fan. Below the cryocooler 65, a heater 67 such as a glass tube heater is disposed for removing frost adhering to the cryocooler 65. A freezer dew tray 68 is disposed below the freezer cooler 65 .

[0020] [1-1-2. Vibration-proof structure] Fig. 2 is a schematic plan view of the refrigerator showing the support structure for the compressor, and Fig. 3 is a schematic front view of the support structure for the compressor. Support members 6 for supporting the compressor 5 are provided integrally with the compressor 5 at the four corners of the compressor 5 . The compressor 5 is supported between the support member 6 and the housing 10 via vibration-isolating members 80. Between the vibration-isolating members 80 and the housing 10, a base member 81 that supports the vibration-isolating members 80 is provided.

[0021] The vibration-proof members 80 are arranged two on each side in the front and rear directions of the refrigerator 1. When the compressor 5 is driven, vibrations are generated, and when these vibrations are transmitted to the housing 10 of the refrigerator 1, vibrations based on a predetermined resonance frequency are generated in the front-rear and left-right directions of the housing 10. This vibration is a combination of vibration caused by a predetermined resonant frequency in a direction in which the housing 10 falls in the forward / backward direction, and vibration caused by a predetermined resonant frequency in a direction in which the housing 10 twists in the left / right direction. Such behavior of the housing 10 causes the door 14 to vibrate.

[0022] Here, FIG. 4 is a schematic diagram showing the input and transmission forces from the compressor 5. As shown in FIG. When the mass of the compressor 5 is m, the spring constant of the vibration-proof member 80 is k, the magnitude of the input is Fin, the magnitude of the force transmitted from the compressor 5 to the housing 10 is Ftr, and the vibration displacement of the compressor 5 is x, the force input is expressed as Fin·sinωt. Also, the transmitted force is expressed as Ftr·sinωt. 5 shows an equation for calculating the natural frequency fn of the vibration system formed by the compressor 5 and the vibration-isolating member 80. Here, k is the spring constant (N / m) of the vibration-isolating member 80, and m is the mass (kg) of the compressor 5. Based on this, the force transmission rate T of the vibration-proof member 80 is expressed by the formula shown in FIG.

[0023] FIG. 7 is a graph showing the relationship between frequency and force transmissibility using the equation of FIG. 7, it can be seen that the vibration system consisting of the compressor 5 and the vibration-proof member 80 can obtain a vibration-proof effect in a frequency range equal to or greater than the root twice the natural frequency fn. In other words, by setting the spring constant of the vibration-proof member 80 according to the input frequency, it is possible to reduce the transmission of force to the housing 10 and reduce the vibration of the housing 10.

[0024] Fig. 8 is an equation showing vibration displacement taking into account phase, and Fig. 9 is a graph showing the relationship between frequency and phase using the equation in Fig. 8. It can be seen that when f / fn<1, that is, when the input frequency is smaller than the natural frequency, the phase is the same on the input side and the transmission side, whereas when f / fn>1, that is, when the frequency is greater than the natural frequency, the phase is reversed on the input side and the transmission side. 10 is an explanatory diagram showing the input from the compressor 5 and the transmission of vibration to the door 14. The input from the compressor 5 is transmitted through the housing 10 via the vibration-proof member 80 and is amplified and attenuated, causing the door 14 to vibrate in each of the directions: front-back, left-right, and up-down. 11 shows an example of a graph showing the relationship between the drive frequency of the compressor 5 and the door vibration in each direction. It can be seen that the door vibration increases as the frequency decreases, and the vibration in the front-rear direction of the door 14 is particularly large.

[0025] FIG. 12 is an explanatory diagram showing the relationship between the vibration of the door 14 in the front-rear direction, the input (N) from the compressor 14, the force transmission rate of the vibration-proof member 80, and the transfer function (μm / N) of the housing 10. The front-rear vibration of the door 14 at each drive frequency of the compressor 5 is the product of the input (N) from the compressor 14, the force transmission rate of the vibration-proof member 80, and the transfer function (μm / N) of the housing 10. Fig. 13 is an explanatory diagram showing input from compressor 5 in each direction and vibration transmission to door 14. Fig. 10 shows only one direction of input from compressor 5 and vibration transmission to door 14 for simplicity, but in reality, input from compressor 5 in each direction is transmitted through housing 10 via vibration-proof member 80 and amplified or attenuated, causing door 14 to vibrate in each of the directions: front-back, left-right, and up-down.

[0026] 14 is an explanatory diagram showing the relationship between the front-rear vibration of the door 14 in response to input from the compressor 5 in each direction, the input (N) from the compressor 14, the force transmission rate of the vibration-proof member 80, and the transfer function (μm / N) of the housing 10. The sum of the vibrations generated by the inputs from the compressor 5 in the front-rear, left-right, and top-bottom directions becomes the front-rear vibration of the door. Fig. 15(a) is a schematic diagram of vibration of the housing in embodiment 1 at 18 Hz, and Fig. 15(b) is a schematic diagram of vibration of the housing in embodiment 1 at 8 Hz. As shown in Fig. 14, in vibrations in the front-rear direction of the door 14 at around 18 Hz, the transfer function of the housing 10 due to the left-right input of the compressor 5 is maximum at 18 Hz, which shows that the left-right input has a large effect. Note that, as shown in Fig. 15(a), the vibration of the housing 10 at 18 Hz due to the left-right input of the compressor 5 is a twisting phenomenon of the housing 10, and is caused by the left-right input of the compressor 5 disposed at the upper rear part of the housing 10. Therefore, in order to reduce the left-right vibrations at around 18 Hz, it is preferable to set the force transmission rate of the vibration-proof member 80 so that the natural frequency of the vibration-proof member 80 is about 10 Hz, so that the vicinity of 18 Hz is a vibration-proof region.

[0027] Furthermore, in vibrations in the front-rear direction of the door 14 in a frequency range lower than 18 Hz, the transfer function of the housing 10 due to the input in the front-rear direction of the compressor 5 is maximum at 8 Hz, which shows that the influence of the input in the front-rear direction is large. As shown in FIG. 15(b), the vibration of the housing 10 at 8 Hz due to the input in the front-rear direction of the compressor 5 is a phenomenon in which the housing 10 falls forward and backward, and is caused by the input in the up-down direction of the compressor 5 disposed at the upper rear part of the housing 10. Therefore, in order to reduce the vibration in the front-rear direction near 8 Hz, it is preferable to set the force transmissibility of the vibration-proof member 80 so that the natural frequency of the vibration-proof member 80 is higher than 8 Hz (for example, about 40 Hz) so that the vicinity of 8 Hz does not become a resonance region. In this way, by changing the natural vibration frequencies of the vibration-damping member 80 in the left-right and front-back directions in accordance with the transfer function (transmission characteristics) of the housing 10, in other words, by setting the spring constants of the vibration-damping member 80 to be different, it is possible to achieve a reduction in the vibration of the door 14 from low frequencies to high frequencies.

[0028] Incidentally, the influence of input in the vertical direction of the housing 10 is small and does not pose any particular problem.

[0029] For this reason, in this embodiment, the spring constant of the vibration-proofing member 80 located on the rear side of the housing 10 is set to be softer than the spring constant of the vibration-proofing member 80 located on the front side of the housing 10. As a result, as shown in Fig. 14, the natural frequency (10 Hz) of the vibration-proofing member 80 for input in the left-right direction can be made smaller than the natural frequency (40 Hz) of the vibration-proofing member 80 for input in the front-back direction, so that vibration of the door 14 can be reduced from low to high frequencies. This can be achieved by changing the material hardness of the vibration-proofing member 80 located on the front side of the housing 10 and the vibration-proofing member 80 located on the rear side.

[0030] As a means for changing the spring constant of the vibration-damping member 80 located at the front side of the housing 10 and the vibration-damping member 80 located at the rear side, for example, the shape of the vibration-damping member 80 may be formed into a circular or elliptical shape in a plan view, and the spring constant may be changed by such a shape change. Furthermore, the spring constant may be changed by forming a notch or the like in a part of the vibration-proof member 80.

[0031] In addition, the vibration-proof member 80 may further have a buffer member (not shown) placed between it and the compressor 5, and the spring constant may be changed by adjusting the presence or absence of this buffer member or the hardness, thickness, etc. of the buffer member. Furthermore, the spring constant may be changed by forming ribs or the like on the base member 81 that supports the vibration-isolating member 80 to change the support strength of the vibration-isolating member 80.

[0032] [1-2. Effect] Next, the operation of the refrigerator 1 in the first embodiment will be described. As shown in FIG. 14, the left-right resonant frequency of vibration-proof member 80 is lower than the left-right resonant frequency of housing 10, and the front-rear resonant frequency of vibration-proof member 80 is higher than the front-rear resonant frequency of housing 10. In this embodiment, the spring constant of the vibration-proofing member 80 located on the rear side of the housing 10 is set to be smaller than the spring constant of the vibration-proofing member 80 located on the front side of the housing 10. Therefore, by setting the spring constant of the rear vibration-damping member 80 to a small value, the transmission characteristics of the vibration-damping member 80 to the housing 10 in response to inputs in the front-to-back and left-to-right directions can be changed, thereby reducing vibrations from low frequencies to high frequencies.

[0033] Furthermore, when the drive frequency of compressor 5 is around 15 Hz, as shown in FIG. 15, a vibration phenomenon occurs in which a forward / backward input causes housing 80 to tip forward / backward, which has a resonant frequency of 8 Hz (FIG. 15(b)), and a left / right input causes housing 80 to twist, which has a resonant frequency of 18 Hz (FIG. 15(a)). FIG. 16 is an explanatory diagram of the vibration cancellation phenomenon caused by the antiphase of vibration transmission in the front-rear and left-right directions.

[0034] With respect to an input in the front-rear direction of the compressor 5, at a frequency lower than the resonant frequency (40 Hz) of the vibration-proof member 80, vibration is transmitted with the same phase as the phase of the input to the compressor 5. On the other hand, for input in the left-right direction, at frequencies higher than the resonant frequency (10 Hz) of the vibration-proof member 80, the input is transmitted with its phase reversed relative to the phase of the input to the compressor 5. In other words, the vibrations transmitted from the compressor 5 in the front-rear direction and the left-right direction are in opposite phases, so that the vibrations cancel each other out and are offset, thereby reducing the vibration of the door 14 in the front-rear direction. As a result, when the compressor driving frequency is around 15 Hz, the forward / rearward vibrations transmitted from the compressor 5 to the housing 10 can be offset, and the vibrations transmitted from the compressor 5 to the door 14 can be reduced.

[0035] [1-3. Effects, etc.] As described above, refrigerator 1 of the present embodiment includes compressor 5 arranged at the upper rear of refrigerator 1 and vibration-isolating member 80 supporting compressor 5, and vibration-isolating member 80 is set to have a different spring constant depending on the vibration direction of compressor 5. Thus, by setting the spring constant of the vibration-proof member 80 to be different depending on the vibration direction of the compressor 5, it is possible to reduce the vibration transmitted from the compressor 5 to the refrigerator 1. Therefore, it is possible to reduce the vibration of the door 14 caused by the vibration of the housing 10.

[0036] In addition, in the refrigerator 1 of this embodiment, the vibration-damping members 80 are arranged on the front and rear sides of the compressor 5, and the spring constants of the front vibration-damping member 80 and the rear vibration-damping member 80 are set to be different. Thus, by setting the spring constant according to the transmission state of the vibrations in the front-rear direction and the left-right direction of the compressor 5, it is possible to reduce the vibrations according to the resonance frequency due to the vibrations in the front-rear direction and the resonance frequency due to the vibrations in the left-right direction. Therefore, it is possible to reduce the vibrations of the door 14 due to the vibrations of the housing 10.

[0037] In addition, in refrigerator 1 of the present embodiment, the spring constant of vibration-proofing member 80 on the rear side is set to be lower than the spring constant of vibration-proofing member 80 on the front side. Thus, by setting the spring constant according to the transmission state of the vibrations in the front-rear direction and the left-right direction of the compressor 5, it is possible to reduce the vibrations according to the resonance frequency due to the vibrations in the front-rear direction and the resonance frequency due to the vibrations in the left-right direction. Therefore, it is possible to reduce the vibrations of the door 14 due to the vibrations of the housing 10.

[0038] In addition, in refrigerator 1 of the present embodiment, vibration-proofing member 80 is made of an elastic material, and the spring constant of vibration-proofing member 80 is set by adjusting the elasticity of vibration-proofing member 80. Thus, by adjusting the elasticity of the elastic material constituting the vibration-proof member 80, the spring constant can be set according to the transmission state of vibration in the front-rear and left-right directions of the compressor 5. Therefore, vibration can be reduced according to the resonance frequency due to vibration in the front-rear direction and the resonance frequency due to vibration in the left-right direction.

[0039] In addition, in refrigerator 1 of the present embodiment, vibration-proof members 80 on the front side and vibration-proof members 80 on the rear side are formed in different shapes, so that they have different spring constants. As a result, by forming the front vibration-proof member 80 and the rear vibration-proof member 80 in different shapes, it is possible to set the spring constant according to the transmission state of vibration in the front-rear direction and the left-right direction of the compressor 5. Therefore, it is possible to reduce vibration according to the resonance frequency due to vibration in the front-rear direction and the resonance frequency due to vibration in the left-right direction.

[0040] In addition, in the refrigerator 1 of this embodiment, the vibration-proof member 80 further has a cushioning member arranged between the vibration-proof member 80 and the compressor 5, and the spring constants are varied by adjusting the hardness, thickness, etc. of the cushioning member. In this way, by adjusting the hardness and thickness of the buffer member to form a different spring constant when the vibration-proof member 80 and the buffer member are combined, it is possible to set the spring constant according to the transmission state of vibration in the front-rear direction and the left-right direction of the compressor 5. Therefore, it is possible to reduce vibration according to the resonance frequency due to vibration in the front-rear direction and the resonance frequency due to vibration in the left-right direction.

[0041] Moreover, refrigerator 1 of the present embodiment includes base member 81 that supports vibration-proof member 80, and is formed so that the spring constant is changed by changing the shape of base member 81. As a result, by changing the shape of the base member 81 to form different spring constants, it is possible to set the spring constants according to the transmission state of vibrations in the front-rear and left-right directions of the compressor 5. Therefore, it is possible to reduce vibrations according to the resonance frequency due to vibrations in the front-rear direction and the resonance frequency due to vibrations in the left-right direction.

[0042] (Other embodiments) Note that the first embodiment has been described as an example of the technology disclosed in the present application. However, the technology in the present disclosure is not limited to this, and can be applied to embodiments in which modifications, substitutions, additions, omissions, etc. are made.

[0043] (Additional Note) The above description of the embodiments discloses the following techniques.

[0044] (Technology 1) A refrigerator comprising a compressor arranged at the upper rear of the refrigerator and a vibration-isolating member supporting the compressor, the vibration-isolating member being set to have a different spring constant depending on the vibration direction of the compressor. With this configuration, the spring constant of the vibration-proof member is set to be different depending on the vibration direction of the compressor, so that the vibration transmitted from the compressor to the refrigerator can be reduced. Therefore, the vibration of the door due to the vibration of the housing can be reduced.

[0045] (Technology 2) A refrigerator according to Technology 1, in which the vibration-damping members are respectively arranged on the front and rear sides of the compressor, and the spring constants of the front vibration-damping member and the rear vibration-damping member are set to be different. With this configuration, by setting the spring constant according to the transmission state of the vibration in the front-rear direction and the left-right direction of the compressor, it is possible to reduce the vibration according to the resonance frequency due to the vibration in the front-rear direction and the resonance frequency due to the vibration in the left-right direction, thereby reducing the vibration of the door due to the vibration of the housing.

[0046] (Technology 3) The refrigerator according to Technology 2, wherein the spring constant of the vibration-isolating member on the rear side is set lower than the spring constant of the vibration-isolating member on the front side. With this configuration, by setting the spring constant according to the transmission state of the vibration in the front-rear direction and the left-right direction of the compressor, it is possible to reduce the vibration according to the resonance frequency due to the vibration in the front-rear direction and the resonance frequency due to the vibration in the left-right direction, thereby reducing the vibration of the door due to the vibration of the housing.

[0047] (Technology 4) The refrigerator according to any one of Technology 1 to Technology 3, wherein the vibration-isolating member is made of an elastic material, and the spring constant of the vibration-isolating member is set by adjusting the elasticity of the vibration-isolating member. With this configuration, the elasticity of the elastic material constituting the vibration-proof member can be adjusted to set the spring constant according to the state of transmission of vibration in the front-rear and left-right directions of the compressor, thereby reducing vibration according to the resonance frequency due to vibration in the front-rear direction and the resonance frequency due to vibration in the left-right direction.

[0048] (Technology 5) The refrigerator according to Technology 4, wherein the vibration-isolating members are formed in different shapes at the front and rear sides, so that the spring constants are different. With this configuration, by forming the front vibration-proofing member and the rear vibration-proofing member in different shapes, the spring constant can be set according to the transmission state of vibration in the front-rear direction and the left-right direction of the compressor, and therefore vibration can be reduced according to the resonance frequency due to vibration in the front-rear direction and the resonance frequency due to vibration in the left-right direction.

[0049] (Technology 6) The refrigerator according to Technology 4, wherein the vibration-proof member further has a cushioning member arranged between the vibration-proof member and the compressor, and the spring constants are varied by adjusting the amount of the cushioning member. With this configuration, by adjusting the amount of the cushioning material to form different spring constants when the vibration-isolating material and the cushioning material are combined, the spring constants can be set according to the transmission state of vibrations in the front-rear and left-right directions of the compressor, and therefore vibrations can be reduced according to the resonance frequency due to vibrations in the front-rear direction and the left-right direction.

[0050] (Technology 7) The refrigerator according to any one of Technology 1 to Technology 6, further comprising a base member supporting the vibration-isolating member, and the shape of the base member is changed to make the spring constant different. With this configuration, by changing the shape of the base member to form different spring constants, it is possible to set the spring constants according to the transmission state of vibrations in the front-rear and left-right directions of the compressor, thereby reducing vibrations according to the resonance frequencies due to vibrations in the front-rear direction and left-right direction. [Industrial Applicability]

[0051] As described above, the refrigerator according to the present disclosure can be suitably used as a refrigerator that can reduce vibration transmitted from the compressor to the refrigerator housing and reduce vibration of the door caused by vibration of the housing. [Explanation of symbols]

[0052] 1. Refrigerator 5. Compressor 6 Supporting member 10. Chassis 11 Refrigerator 12 Freezer 13. Switch Room 14 Doors 15 Vegetable compartment 16 Microfreezing chamber 17 Vegetable drawer case 18. Drawer case for micro-freezing chamber 30 Refrigerator Cooling Room 33 Refrigeration Duct 54 Refrigerator Cooler 60 Refrigeration cooling room 62 Refrigeration intake 63 Refrigeration outlet 64 Switching room air outlet 65 Refrigeration cooler 66 Refrigeration Fan 67 Heater 70 Blower fan 71 Rotating Fan 80 Anti-vibration material 81 Base material

Claims

1. A refrigerator comprising a compressor disposed at an upper rear portion of the refrigerator and a vibration isolating member supporting the compressor, The vibration-proof member is set to have a different spring constant depending on the vibration direction of the compressor. refrigerator.

2. The vibration-proof members are disposed on the front and rear sides of the compressor, The spring constants of the front vibration-proof member and the rear vibration-proof member are set to be different from each other.

2. The refrigerator according to claim 1.

3. The spring constant of the rear vibration-proof member is set lower than the spring constant of the front vibration-proof member.

3. The refrigerator according to claim 2.

4. The vibration-isolating member is made of an elastic material, The spring constant of the vibration-isolating member is set by adjusting the elasticity of the vibration-isolating member. The refrigerator according to claim 3.

5. The vibration-proofing members are formed so that the spring constants are different between the front side vibration-proofing member and the rear side vibration-proofing member by forming them in different shapes.

5. The refrigerator according to claim 4.

6. The vibration-proof member further includes a buffer member disposed between the vibration-proof member and the compressor, The amount of the buffer member is adjusted to vary the spring constant.

5. The refrigerator according to claim 4.

7. a base member supporting the vibration-isolating member; The spring constant is changed by changing the shape of the base member.

5. The refrigerator according to claim 4.

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