Compressor mounting structure and compressor

Abstract

Disclosed is an attachment structure for attaching a compressor to an attachment surface of a vehicle. The compressor is provided with a rotating body including a rotating shaft and a compression mechanism provided on at least one end of the rotating shaft in the axial direction. The compressor is further provided with a radial bearing that supports the rotating shaft, a thrust bearing that supports the rotating shaft, and a housing that accommodates the rotating body, the radial bearing, and the thrust bearing. The radial bearing and the thrust bearing are gas bearings. The mounting structure is provided with a mounting foot which is fixed to the housing and the mounting surface and is composed of an elastic member. The resonant frequency of the mounting foot is less than the resonant frequency of the radial bearing and less than the resonant frequency of the thrust bearing.

Description

Technical Field

[0001] The present disclosure relates to a mounting structure of a compressor and a compressor. Background Art

[0002] Japanese Patent Publication No. 2017-44313 describes a mounting structure for mounting a compressor on a mounting surface of a vehicle. The compressor, for example, includes a rotating body, a bearing, and a housing. The rotating body, for example, includes a rotating shaft and a compression mechanism that is arranged at least at one end in the axial direction of the rotating shaft and compresses a fluid by rotating together with the rotating shaft. The bearings, for example, include a radial bearing that supports the rotating shaft in a radial direction so that it can rotate and a thrust bearing that supports the rotating shaft in a thrust direction so that it can rotate. The housing, for example, accommodates the rotating body, the radial bearing, and the thrust bearing. The mounting structure described in the above-mentioned publication includes a mounting foot. The mounting foot is, for example, fixed to the housing of the compressor and the mounting surface of the vehicle. Summary of the invention

[0003] Problems to be solved by the invention

[0004] As the vehicle vibrates, the vibration is transmitted from the vehicle to the compressor, so that the compressor may vibrate. When the compression mechanism vibrates greatly, for example, components constituting the compression mechanism may collide with each other, which is not preferred. Therefore, it is desirable to suppress the vibration of the compression mechanism generated by the vibration of the vehicle.

[0005] Solutions to Solve Problems

[0006] In one embodiment of the present disclosure, a mounting structure for mounting a compressor on a mounting surface of a vehicle is disclosed. The compressor comprises: a rotating body, which includes a rotating shaft and at least one end arranged in the axial direction of the rotating shaft and is configured as a compression mechanism that compresses a fluid by rotating together with the rotating shaft; a radial bearing that supports the rotating shaft in a radial direction so that it can rotate; a thrust bearing that supports the rotating shaft in a thrust direction so that it can rotate; and a housing that accommodates the rotating body, the radial bearing, and the thrust bearing. The radial bearing and the thrust bearing are gas bearings. The mounting structure comprises a mounting foot that is fixed to the housing and the mounting surface and is composed of an elastic member. The resonance frequency of the mounting foot is lower than the resonance frequency of the radial bearing and lower than the resonance frequency of the thrust bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1 It is a schematic diagram showing a compressor and a mounting structure of the compressor.

[0008] Figure 2 It is shown Figure 1 Schematic diagram of the compressor.

[0009] Figure 3It is shown Figure 2 A cross-sectional view of a portion of a compressor.

[0010] Figure 4 It is a graph showing the relationship between the excitation frequency and the vibration amount of the rotating body. DETAILED DESCRIPTION

[0011] Hereinafter, an embodiment of the present disclosure will be described with reference to the drawings. The compressor 10 of the present embodiment is an electric compressor. The compressor 10 of the present embodiment is used in, for example, a vehicle air conditioner.

[0012] <Compressor>

[0013] like Figure 1 As shown, the compressor 10 includes a housing 11. The housing 11 is, for example, cylindrical. The housing 11 is made of metal. The housing 11 is, for example, made of aluminum. The direction in which the axis m of the housing 11 extends is the axial direction X. The housing 11 may be composed of a plurality of housing components that can be divided along the axial direction X.

[0014] like Figure 2 As shown, the compressor 10 includes a rotating body 19 and a bearing 18. The rotating body 19 includes a rotating shaft 12 and a compression mechanism 13. The compression mechanism 13 includes a compression portion 13a. The bearing 18 includes one or more radial bearings 15 and a thrust bearing 16. That is, the compressor 10 includes one or more radial bearings 15 and a thrust bearing 16. The housing 11 accommodates the rotating body 19, one or more radial bearings 15, and the thrust bearing 16.

[0015] like Figure 3 As shown, the housing 11 includes a shield surface 11 b. The shield surface 11 b is in the shape of a truncated cone. The compression portion 13 a is located in a space surrounded by the shield surface 11 b. That is, the housing 11 accommodates the compression portion 13 a.

[0016] like Figure 2 As shown, the rotating shaft 12 extends in the same direction as the axis m of the housing 11. That is, the axial direction X corresponds to the axial direction of the rotating shaft 12. The rotating axis L, which is the axis of the rotating shaft 12, extends in the axial direction X. The rotating shaft 12 is, for example, cylindrical. In the axial direction X, one end of the rotating shaft 12 is set as the first end 12a, and the other end of the rotating shaft 12 is set as the second end 12b. The second end 12b is the end of the rotating shaft 12 on the opposite side to the first end 12a. In the axial direction X, the side where the first end 12a is located is set as the first side X1 relative to any reference position between the first end 12a and the second end 12b, and the side where the second end 12b is located is set as the second side X2 relative to the reference position.

[0017] like Figure 2 as well as Figure 3As shown, the compression mechanism 13 is arranged at least at one end in the axial direction X of the rotating shaft 12. In the present embodiment, the compression mechanism 13 is arranged at the first end 12a of the rotating shaft 12, and is not arranged at the second end 12b of the rotating shaft 12. The compression portion 13a is, for example, an impeller. That is, the compression mechanism 13 includes an impeller. The compression portion 13a is in the shape of a truncated cone. The compression portion 13a is covered by the shroud surface 11b of the casing 11. The compression portion 13a is separated from the shroud surface 11b. As a result, a tip gap 11c is formed between the compression portion 13a and the shroud surface 11b. When the rotating shaft 12 rotates, the compression portion 13a rotates integrally with the rotating shaft 12.

[0018] like Figure 2 As shown, the compressor 10 includes an electric motor 14. The electric motor 14 is mounted on the rotating shaft 12. The electric motor 14 is driven by being supplied with electric power from an inverter (not shown). As the electric motor 14 is driven, the rotating shaft 12 rotates.

[0019] One or more radial bearings 15 support the rotating shaft 12 in a radial direction so that it can rotate. In the present embodiment, the bearing 18 includes two radial bearings 15. The two radial bearings 15 include a first radial bearing 15a and a second radial bearing 15b. The first radial bearing 15a supports the portion between the first end 12a of the rotating shaft 12 and the electric motor 14. The second radial bearing 15b supports the portion between the electric motor 14 and the second end 12b of the rotating shaft 12. In the present embodiment, the center of gravity C1 of the compressor 10 is located between the two radial bearings 15 in the axial direction X. The two radial bearings 15 are fixed to the housing 11. The two radial bearings 15 support the rotating shaft 12 so that it can rotate relative to the housing 11.

[0020] The rotating body 19 includes a support portion 19a. The support portion 19a protrudes in the radial direction from the outer peripheral surface of the rotating shaft 12. The support portion 19a is in the shape of a disk. The support portion 19a rotates integrally with the rotating shaft 12.

[0021] In the present embodiment, the bearing 18 includes a thrust bearing 16. The thrust bearing 16 includes bearing bodies arranged in pairs with a support portion 19a sandwiched therebetween in the axial direction X. The thrust bearing 16 supports the support portion 19a in a thrust direction so that it can rotate. Thus, the thrust bearing 16 supports the rotating shaft 12 in a thrust direction so that it can rotate. The thrust direction is the axial direction X of the rotating shaft 12. The thrust bearing 16 supports the rotating shaft 12 so that it can rotate relative to the housing 11.

[0022] The radial bearing 15 and the thrust bearing 16 are gas bearings. The bearing 18, which is a gas bearing, contacts the rotating shaft 12 until the rotation speed of the rotating shaft 12 reaches a predetermined rotation speed. When the rotation speed of the rotating shaft 12 reaches the predetermined rotation speed, an air film is formed between the rotating shaft 12 and the bearing 18 by the air introduced by the rotation of the rotating shaft 12. The rotating shaft 12 floats under the action of the dynamic pressure of the air film formed between the rotating shaft 12 and the bearing 18. Therefore, when the rotation speed of the rotating shaft 12 reaches the predetermined rotation speed, the bearing 18 does not contact the rotating shaft 12 but supports the rotating shaft 12 via the air film. By adopting a gas bearing as the bearing 18, it is possible to suppress the rotating shaft 12 and the housing 11 from contacting each other.

[0023] The compression mechanism 13 compresses a fluid by rotating together with the rotating shaft 12. In the present embodiment, the fluid is a refrigerant. The compression mechanism 13 compresses the refrigerant sucked into the housing 11 as the electric motor 14 is driven.

[0024] like Figure 1 As shown, the compressor 10 includes a plurality of protrusions 11d. The protrusions 11d protrude from the outer surface 11a of the shell 11. The protrusions 11d are integrated with the shell 11. Therefore, the protrusions 11d are made of the same metal as the shell 11. The plurality of protrusions 11d extend from the outer surface 11a of the shell 11 in the same direction as each other. The plurality of protrusions 11d are, for example, cylindrical and extend from the outer surface 11a of the shell 11 toward the mounting surface 100a. The compressor 10 in this embodiment includes two protrusions 11d. The two protrusions 11d are separated from each other in the axial direction X.

[0025] like Figure 2 As shown, one of the two protrusions 11d is provided on the first side X1 relative to the first radial bearing 15a in the axial direction X. The other of the two protrusions 11d is provided on the second side X2 relative to the electric motor 14 in the axial direction X. Alternatively, both of the two protrusions 11d may be located on the second side X2 relative to the compression portion 13a in the axial direction X.

[0026] The center of gravity C1 of the compressor 10 is located, for example, on the rotating shaft 12. An imaginary line extending from the center of gravity C1 of the compressor 10 in a direction perpendicular to the axial direction X of the rotating shaft 12 is referred to as an imaginary line VL. A plane including the center of gravity C1 of the compressor 10 and perpendicular to the axial direction X of the rotating shaft 12 is referred to as an imaginary plane VP. The imaginary line VL extends on the imaginary plane VP.

[0027] A direction orthogonal to the axial direction X is also referred to as a first orthogonal direction Y. A direction orthogonal to the axial direction X and the first orthogonal direction Y is also referred to as a second orthogonal direction Z. The second orthogonal direction Z is a direction in which the imaginary line VL extends. The first orthogonal direction Y is a direction in which an imaginary straight line orthogonal to the rotation axis L of the rotation shaft 12 and the imaginary line VL extends.

[0028] The imaginary plane VP is located between the two protrusions 11d in the axial direction X. At least one of the plurality of protrusions 11d is located on the first side X1 relative to the imaginary plane VP, and at least one of the protrusions 11d is located on the second side X2 relative to the imaginary plane VP. In the present embodiment, one protrusion 11d is located on the first side X1 relative to the imaginary plane VP, and one protrusion 11d is located on the second side X2 relative to the imaginary plane VP.

[0029] <Compressor Installation Structure>

[0030] like Figure 1 As shown, the compressor 10 is mounted on the mounting surface 100a of the vehicle 100 via the mounting structure 30. In other words, the mounting structure 30 is used to mount the compressor 10 on the mounting surface 100a of the vehicle 100. The mounting surface 100a is, for example, a part of a frame 101 constituting the vehicle 100. The combination of the compressor 10 and the mounting structure 30 is referred to as a compressor unit or a compressor system.

[0031] The mounting structure 30 includes a plurality of mounting feet 20. The mounting feet 20 are fixed to the plurality of protrusions 11d, respectively. That is, the mounting feet 20 are fixed to the housing 11. The mounting structure 30 in this embodiment includes two mounting feet 20. The two mounting feet 20 are separated from each other in the axial direction X.

[0032] The mounting foot 20 is composed of an elastic member. The elastic member is formed of, for example, a rubber member or a urethane member as a resin member capable of elastic deformation. The mounting foot 20 is installed, for example, at the front end portion of the protrusion 11d, that is, the end portion of the protrusion 11d on the side opposite to the outer surface 11a of the shell 11. The mounting foot 20 is, for example, cylindrical and extends from the front end portion of the protrusion 11d toward the mounting surface 100a. The mounting foot 20 is mounted on the mounting surface 100a using fastening members such as bolts. Thus, the mounting foot 20 is fixed to the mounting surface 100a. In the present embodiment, the mounting surface 100a for mounting a plurality of mounting feet 20 is the same plane.

[0033] like Figure 1 as well as Figure 2As shown in the figure, one of the two mounting feet 20 is fixed to one of the two protrusions 11d, and the other of the two mounting feet 20 is fixed to the other of the two protrusions 11d. Therefore, one of the two mounting feet 20 is connected to the housing 11 on the first side X1 relative to the first radial bearing 15a in the axial direction X. The other of the two mounting feet 20 is connected to the housing 11 on the second side X2 relative to the electric motor 14 in the axial direction X. The imaginary plane VP is located between the two mounting feet 20 in the axial direction X. One of the two mounting feet 20 is located on the first side X1 relative to the imaginary plane VP, and the other of the two mounting feet 20 is located on the second side X2 relative to the imaginary plane VP.

[0034] <Resonance frequency magnitude relationship>

[0035] The resonant frequency of each mounting foot 20 is set to the mounting foot resonant frequency F1. The resonant frequency of each radial bearing 15 is set to the radial bearing resonant frequency F2. The resonant frequency of the thrust bearing 16 is set to the thrust bearing resonant frequency F3. All the mounting feet 20 provided in the mounting structure 30 may have the same mounting foot resonant frequency F1 or different mounting foot resonant frequencies F1.

[0036] The above-mentioned mounting foot resonance frequency F1 is one of a plurality of mounting foot resonance frequencies F1. The plurality of mounting foot resonance frequencies F1 include a mounting foot resonance frequency F1 in a translation direction and a mounting foot resonance frequency F1 in a rotation direction. The mounting foot resonance frequency F1 in the translation direction includes three types: a mounting foot resonance frequency F1 in a translation direction along an imaginary axis extending in the axial direction X, a mounting foot resonance frequency F1 in a translation direction along an imaginary axis extending in the first orthogonal direction Y, and a mounting foot resonance frequency F1 in a translation direction along an imaginary axis extending in the second orthogonal direction Z. The mounting foot resonance frequency F1 in a rotation direction includes three types: a mounting foot resonance frequency F1 in a rotation direction centered on an imaginary axis extending in the axial direction X, a mounting foot resonance frequency F1 in a rotation direction centered on an imaginary axis extending in the first orthogonal direction Y, and a mounting foot resonance frequency F1 in a rotation direction centered on an imaginary axis extending in the second orthogonal direction Z. Among the six types of mounting foot resonance frequencies F1 described above, the mounting foot resonance frequency F1 in the translation direction along the imaginary axis extending in the first orthogonal direction Y is exemplified below.

[0037] In the compressor 10, the radial bearing resonance frequency F2 is set to the same number as the number of radial bearings 15 provided in the compressor 10. Therefore, in the compressor 10 in the present embodiment, two resonance frequencies are set as the radial bearing resonance frequency F2.

[0038] In the compressor 10, the thrust bearing resonance frequency F3 is set to the same number as the number of thrust bearings 16 provided in the compressor 10. Therefore, in the compressor 10 in the present embodiment, one resonance frequency is set as the thrust bearing resonance frequency F3.

[0039] The weight of the housing 11 is set to the housing weight M1. The weight of the rotating body 19 is set to the rotating body weight M2. The total rigidity of the plurality of mounting feet 20 is set to the mounting foot rigidity K1. The total rigidity of the radial bearing 15 is set to the radial bearing rigidity K2. The total rigidity of the thrust bearing 16 is set to the thrust bearing rigidity K3. The mounting foot rigidity K1, the radial bearing rigidity K2, and the thrust bearing rigidity K3 are values ​​expressed in units of N / m. The mounting foot rigidity K1, the radial bearing rigidity K2, and the thrust bearing rigidity K3 are rigidities in the direction in which the imaginary line VL extends. The direction in which the imaginary line VL extends is the direction of vibration acting on the compressor 10 from the vehicle 100 via the mounting foot 20.

[0040] The rigidity of the mounting foot 20 is a value inherent to the mounting foot 20 and is determined by the shape and / or material of the mounting foot 20. The rigidities of the two mounting feet 20 provided in the mounting structure 30 may be the same value or different values. With regard to the total rigidity of the plurality of mounting feet 20, the total rigidity in the radial direction and the total rigidity in the thrust direction are the same value.

[0041] The rigidity of the radial bearing 15 is a value inherent to the radial bearing 15, which is determined by the shape and / or material of the radial bearing 15. The rigidities of the two radial bearings 15 provided in the compressor 10 may be the same value or different values. The rigidity of the thrust bearing 16 is a value inherent to the thrust bearing 16, which is determined by the shape and / or material of the thrust bearing 16.

[0042] The mounting foot resonance frequency F1 can be expressed by the following equation (1).

[0043]

[0044] The radial bearing resonance frequency F2 can be expressed by the following equation (2).

[0045]

[0046] The thrust bearing resonance frequency F3 can be expressed by the following equation (3).

[0047]

[0048] The mount foot resonance frequency F1 is smaller than the radial bearing resonance frequency F2 and smaller than the thrust bearing resonance frequency F3. Therefore, based on the above equations (1), (2) and (3), the following equations (4) and (5) hold.

[0049]

[0050] The mounting foot resonance frequency F1 for which the above-mentioned equations (4) and (5) are satisfied is the mounting foot resonance frequency F1 in the translation direction of the imaginary axis extending in the first orthogonal direction Y. It may be that at least one of the six mounting foot resonance frequencies F1 is smaller than the radial bearing resonance frequency F2 and smaller than the thrust bearing resonance frequency F3. The six mounting foot resonance frequencies F1 include, in addition to the mounting foot resonance frequency F1 in the translation direction of the imaginary axis extending in the first orthogonal direction Y, the mounting foot resonance frequency F1 in the translation direction of the imaginary axis extending in the axial direction X, the mounting foot resonance frequency F1 in the translation direction of the imaginary axis extending in the second orthogonal direction Z, the mounting foot resonance frequency F1 in the rotation direction centered on the imaginary axis extending in the axial direction X, the mounting foot resonance frequency F1 in the rotation direction centered on the imaginary axis extending in the first orthogonal direction Y, and the mounting foot resonance frequency F1 in the rotation direction centered on the imaginary axis extending in the second orthogonal direction Z.

[0051] <Data Comparison>

[0052] Next, the relationship between the excitation frequency and the vibration amount of the rotating body 19 was obtained through experiments for the mounting structure 30 in the first embodiment and the mounting structure 30 in the first comparative example. The results are shown in FIG. Figure 4 In Figure 4 In FIG. 1 , the horizontal axis represents the excitation frequency, and the vertical axis represents the vibration amount of the rotating body 19. The excitation frequency is the frequency of the vibration applied to the compressor 10 from the outside of the compressor 10. The vibration amount of the rotating body 19 is the vibration amount of the compression part 13a. The vibration amount of the compression part 13a is, for example, the displacement amount of the compression part 13a in the radial direction of the rotating shaft 12. Figure 4 In , the trajectory of the values ​​in the first embodiment is represented by a solid line. Figure 4 , the locus of the numerical values ​​in the first comparative example is indicated by a single-dot chain line.

[0053] The mounting structure 30 in the first embodiment has a mounting foot resonance frequency F1 that is smaller than the radial bearing resonance frequency F2, similarly to the embodiment. The mounting structure 30 in the first comparative example has a mounting foot resonance frequency F1 that is larger than the radial bearing resonance frequency F2, unlike the embodiment.

[0054] like Figure 4As shown, the excitation frequency that generates the peak value of the vibration amount of the rotating body 19 in the first embodiment is smaller than the excitation frequency that generates the peak value of the vibration amount of the rotating body 19 in the first comparative example. The peak value of the vibration amount of the rotating body 19 in the first comparative example is generated when the excitation frequency is near the radial bearing resonance frequency F2, whereas the peak value of the vibration amount of the rotating body 19 in the first embodiment is generated when the excitation frequency is smaller than the radial bearing resonance frequency F2. Therefore, when the excitation frequency is the radial bearing resonance frequency F2, the vibration amount of the rotating body 19 in the first embodiment is smaller than the vibration amount of the rotating body 19 in the first comparative example.

[0055] When the excitation frequency is the radial bearing resonance frequency F2, the radial bearing 15 resonates with the vibration applied to the compressor 10, so that the rotating body 19 vibrates the most. Therefore, in order to suppress the vibration of the compression part 13a, it is desirable to reduce the vibration amount of the rotating body 19 when the excitation frequency is the radial bearing resonance frequency F2. Figure 4 It is shown that if the mounting foot resonance frequency F1 is lower than the radial bearing resonance frequency F2 as in the mounting structure 30 in the first embodiment, the vibration of the compression portion 13a can be suppressed.

[0056] In the case of the thrust bearing resonance frequency F3, it can also be said to be the same as the case of the radial bearing resonance frequency F2 described above. That is, the mounting structure 30 in the second embodiment has a mounting foot resonance frequency F1 that is smaller than the thrust bearing resonance frequency F3. The mounting structure 30 in the second comparative example has a mounting foot resonance frequency F1 that is larger than the thrust bearing resonance frequency F3. In this case, the peak value of the vibration amount of the rotating body 19 in the second comparative example is generated when the excitation frequency is near the thrust bearing resonance frequency F3, whereas the peak value of the vibration amount of the rotating body 19 in the second embodiment is generated when the excitation frequency is smaller than the thrust bearing resonance frequency F3. Therefore, when the excitation frequency is the thrust bearing resonance frequency F3, the vibration amount of the rotating body 19 in the second embodiment is smaller than the vibration amount of the rotating body 19 in the second comparative example.

[0057] When the excitation frequency is the thrust bearing resonance frequency F3, the thrust bearing 16 resonates with the vibration applied to the compressor 10, so that the rotating body 19 vibrates greatly. Therefore, in order to suppress the vibration of the compression part 13a, it is desirable to reduce the vibration amount of the rotating body 19 when the excitation frequency is the thrust bearing resonance frequency F3. Therefore, if the mounting structure 30 in the second embodiment is installed so that the resonance frequency F1 is smaller than the thrust bearing resonance frequency F3, the vibration of the compression part 13a can be suppressed.

[0058] [Functions and Effects of Implementation Methods]

[0059] The functions and effects of the embodiment will be described.

[0060] (1) The mounting foot resonance frequency F1 is smaller than the radial bearing resonance frequency F2 and smaller than the thrust bearing resonance frequency F3. Therefore, when the radial bearing 15 resonates when the rotating body 19 vibrates the most, the vibration amount of the rotating body 19 can be reduced. Therefore, the vibration of the compression mechanism 13 caused by the vibration of the vehicle 100 can be suppressed.

[0061] (2) The compression mechanism 13 is provided at the first end 12a of the rotating shaft 12, but not at the second end 12b. Therefore, compared with the case where the compression mechanism 13 is provided at both ends of the rotating shaft 12, the vibration amount of the rotating body 19 is likely to increase due to the deviation of the center of gravity of the rotating body 19. Even in such a case where the vibration of the rotating body 19 is more concerned, the vibration of the compression mechanism 13 caused by the vibration of the vehicle 100 can be suppressed by adopting the mounting structure 30 of this embodiment.

[0062] (3) The compression mechanism 13 includes a compression portion 13a as an impeller. In this case, the compression portion 13a is not in contact with the housing 11, so the vibration amount of the compression portion 13a becomes a problem. That is, since the size of the blade tip gap 11c formed between the shroud surface 11b of the housing 11 and the compression portion 13a is small, when the compression mechanism 13 vibrates greatly, the compression portion 13a is likely to collide with the housing 11. Even in such a case, by suppressing the vibration of the compression mechanism 13 generated by the vibration of the vehicle 100, it is possible to suppress the collision of the compression portion 13a with the housing 11.

[0063] (4) The compressor 10 is mounted on the mounting surface 100a of the vehicle 100 by means of the mounting structure 30. The fluid compressed by the compression mechanism 13 is a refrigerant. The refrigerant has a higher load density than air, and therefore, compared with the case where air is assumed to be used as the fluid compressed by the compression mechanism 13, it is less likely that the rotating shaft 12 will collide with the radial bearing 15 and the thrust bearing 16 when vibration acts on the housing 11. On the other hand, the vibration of the compression mechanism 13, which is concerned because the rotating shaft 12 does not collide with the radial bearing 15 and the thrust bearing 16 when vibration acts on the housing 11, can be suppressed by adopting the mounting structure 30.

[0064] (5) The radial bearing 15 and the thrust bearing 16 are gas bearings. The rigidity of the gas bearing tends to be lower than that of the rolling bearing. Therefore, when the radial bearing 15 and the thrust bearing 16 are gas bearings, the radial bearing resonance frequency F2 and the thrust bearing resonance frequency F3 become smaller than when the radial bearing 15 and the thrust bearing 16 are assumed to be rolling bearings. In this way, even when the radial bearing resonance frequency F2 and the thrust bearing resonance frequency F3 are likely to become values ​​close to the mounting foot resonance frequency F1, by adopting the mounting structure 30 of this embodiment, the vibration of the compression mechanism 13 caused by the vibration of the vehicle 100 can be suppressed. In addition, the radial bearing 15 and the thrust bearing 16, which are gas bearings, are non-contact with the rotating shaft 12, so the vibration amount of the compression mechanism 13 becomes a problem. Such vibration of the compression mechanism 13 can be suppressed by adopting the mounting structure 30.

[0065] (6) The mounting foot 20 is formed of an elastic member. Therefore, the vibration attenuation effect brought about by the mounting foot 20 is improved compared to the case where the mounting foot 20 is formed of a metal member, so that the vibration of the compressor 10 when the vehicle 100 vibrates can be suppressed. Therefore, the vibration of the compression mechanism 13 caused by the vibration of the vehicle 100 can be further suppressed. In addition, by adopting the mounting foot 20 formed of an elastic member, the mounting rigidity of the mounting foot 20 relative to the housing 11 and the mounting surface 100a can be reduced, for example, compared to the mounting foot 20 formed of a metal member. Therefore, the mounting foot rigidity K1 can be reduced, so that the mounting foot resonance frequency F1 can be made smaller than the radial bearing resonance frequency F2 and smaller than the thrust bearing resonance frequency F3.

[0066] (7) The compressor 10 is mounted on the vehicle 100. Therefore, the vibration of the vehicle 100 is transmitted to the compressor 10, and thus, for example, the vibration applied to the compressor 10 from the outside is larger than that in the case where the compressor 10 is installed at a location other than the vehicle 100. By adopting the mounting structure 30 of the present embodiment to the compressor 10 that is subjected to large vibration from the outside, the vibration of the compression mechanism 13 can be suppressed.

[0067] [Change example]

[0068] The embodiment can be implemented by changing as follows. The embodiment and the following modified examples can be implemented in combination with each other within the range that there is no technical contradiction.

[0069] The number of the mounting feet 20 provided in the mounting structure 30 may be one or three or more. The number of the protrusions 1id provided on the housing 11 may be changed according to the number of the mounting feet 20.

[0070] The mounting foot 20 may be directly fixed to the outer surface 11 a of the housing 11 without passing through the protrusion 11 d. In this case, the protrusion 11 d may be omitted from the compressor 10 .

[0071] ○ In the case where the mounting structure 30 includes a plurality of mounting feet 20, the mounting surfaces 100a to which the plurality of mounting feet 20 are fixed are not limited to the same plane. The mounting surface 100a to which at least one mounting foot 20 among the plurality of mounting feet 20 is fixed and the mounting surface 100a to which at least one other mounting foot 20 is fixed may extend in different directions from each other. In this case, the axial direction of the mounting foot 20 extending from the housing 11 toward the mounting surface 100a may also be different for each mounting foot 20.

[0072] ○ When the mounting structure 30 includes a plurality of mounting feet 20, two or more mounting feet 20 may be located on the first side X1 relative to the imaginary plane VP, and two or more mounting feet 20 may be located on the second side X2 relative to the imaginary plane VP. All mounting feet 20 included in the mounting structure 30 may be located on the first side X1 relative to the imaginary plane VP, and all mounting feet 20 included in the mounting structure 30 may be located on the second side X2 relative to the imaginary plane VP.

[0073] The compressor 10 may include one radial bearing 15 or three or more radial bearings 15. The compressor 10 may include two or more thrust bearings 16.

[0074] The compression mechanism 13 may be provided at both ends of the rotating shaft 12 in the axial direction X.

[0075] The compression mechanism 13 is not limited to a compression mechanism including an impeller as the compression portion 13a. For example, the compressor 10 may be a piston type, a scroll type, or the like.

[0076] The compressor 10 is used in a vehicle air conditioning device, but is not limited thereto. The compressor 10 may be any compressor that compresses a refrigerant, and the purpose of the compressor 10 may be changed as appropriate.

[0077] The compression mechanism 13 may be a compression mechanism that compresses a fluid other than the refrigerant. For example, the compression mechanism 13 may be a compression mechanism that compresses air.

Claims

1. A mounting structure for mounting a compressor on a mounting surface of a vehicle, wherein: The compressor comprises: a rotating body including a rotating shaft and a compression mechanism disposed at at least one end in the axial direction of the rotating shaft and configured to compress a fluid by rotating together with the rotating shaft; a radial bearing that supports the rotating shaft in a radial direction so as to be rotatable; a thrust bearing that rotatably supports the rotating shaft in a thrust direction; and a housing that accommodates the rotating body, the radial bearing, and the thrust bearing, The radial bearing and the thrust bearing are gas bearings, The mounting structure includes a mounting foot fixed to the housing and the mounting surface and formed of an elastic member. The resonant frequency of the mounting foot is lower than the resonant frequency of the radial bearing and lower than the resonant frequency of the thrust bearing.

2. The mounting structure according to claim 1, wherein: The compression mechanism is provided at one end of the rotating shaft in the axial direction, and is not provided at the other end of the rotating shaft.

3. The mounting structure according to claim 1 or 2, wherein: The compression mechanism includes an impeller.

4. A compressor, which is mounted on the mounting surface by the mounting structure according to claim 1 or 2, wherein: The fluid is a refrigerant.

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