Mounting structure for compressor and compressor

Abstract

A mounting structure for mounting a compressor on a mounting surface of a vehicle is disclosed. The compressor comprises a rotating body including a rotating shaft and a compression mechanism formed at least one end in the axial direction of the rotating shaft. The compressor also comprises a radial bearing supporting the rotating shaft, a thrust bearing supporting 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 comprises mounting legs made of an elastic member that are fixed to the housing and the mounting surface. The resonance frequency of the mounting legs is lower than the resonance frequency of the radial bearing and also lower than the resonance frequency of the thrust bearing.

Description

Technology Field

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

[0002] Japanese Patent Publication No. 2017-44313 describes a mounting structure for mounting a compressor on a mounting surface of a vehicle. The compressor comprises, for example, a rotating body, a bearing, and a housing. The rotating body comprises, for example, a rotating shaft and a compression mechanism formed at least one end in the axial direction of the rotating shaft and compressing a fluid by rotating together with the rotating shaft. The bearing comprises, for example, a radial bearing that supports the rotating shaft in a radial direction to allow rotation, and a thrust bearing that supports the rotating shaft in a thrust direction to allow rotation. The housing accommodates, for example, the rotating body, the radial bearing, and the thrust bearing. The mounting structure described in the above publication comprises mounting legs. The mounting legs are, for example, fixed to the housing of the compressor and the mounting surface of the vehicle. The problem to be solved

[0003] There are cases where the compressor vibrates as vibrations from the vehicle are transmitted to it. If the compression mechanism vibrates significantly, it is undesirable because, for example, the components constituting the compression mechanism may collide with each other. Therefore, it has been desired to suppress the vibration of the compression mechanism that occurs in conjunction with vehicle vibrations. means of solving the problem

[0004] In one aspect 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 including a rotating shaft and a compression mechanism formed 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 supporting the rotating shaft rotatably in a radial direction, a thrust bearing supporting the rotating shaft rotatably 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 comprises mounting legs made of an elastic member that are fixed to the housing and the mounting surface. The resonance frequency of the mounting legs is lower than the resonance frequency of the radial bearing and also lower than the resonance frequency of the thrust bearing. Brief explanation of the drawing

[0005] Figure 1 is a schematic diagram showing a compressor and the mounting structure of the compressor. Figure 2 is a schematic diagram showing the compressor of Figure 1. Figure 3 is a cross-sectional view showing a part of the compressor of Figure 2. Figure 4 is a graph showing the relationship between the vibration frequency and the amount of shaking of the rotating body. Specific details for implementing the invention

[0006] Hereinafter, embodiments 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, for example, in a vehicle air conditioning system.

[0007] <Compressor>

[0008] As shown in FIG. 1, the compressor (10) is provided with 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 defined as 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.

[0009] As shown in FIG. 2, the compressor (10) is equipped with 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 section (13a). The bearing (18) includes one or more radial bearings (15) and a thrust bearing (16). That is, the compressor (10) is equipped with 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 a thrust bearing (16).

[0010] As shown in FIG. 3, the housing (11) is provided with a shroud surface (11b). The shroud surface (11b) is in the shape of a truncated cone. A compression section (13a) is located in the space enclosed by the shroud surface (11b). That is, the housing (11) accommodates the compression section (13a).

[0011] As shown in FIG. 2, the rotation axis (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 rotation axis (12). The rotation axis line L, which is the axis of the rotation axis (12), extends in the axial direction X. The rotation axis (12) is, for example, cylindrical. In the axial direction X, one end of the rotation axis (12) is designated as the first end (12a), and the other end of the rotation axis (12) is designated as the second end (12b). The second end (12b) is the end of the rotation axis (12) opposite to the first end (12a). In the axial direction X, the side where the first stage (12a) is located for any reference position between the first stage (12a) and the second stage (12b) is designated as the first side X1, and the side where the second stage (12b) is located for the reference position is designated as the second side X2.

[0012] As shown in FIGS. 2 and 3, the compression mechanism (13) is formed at least one end in the axial X of the rotation axis (12). In this embodiment, the compression mechanism (13) is formed at the first end (12a) of the rotation axis (12) and is not formed at the second end (12b) of the rotation axis (12). The compression part (13a) is, for example, an impeller. That is, the compression mechanism (13) includes an impeller. The compression part (13a) is in the shape of a truncated cone. The compression part (13a) is covered by the shroud surface (11b) of the housing (11). The compression part (13a) is separated from the shroud surface (11b). Thus, a tip clearance (11c) is formed between the compression part (13a) and the shroud surface (11b). When the rotation axis (12) rotates, the compression part (13a) rotates integrally with the rotation axis (12).

[0013] As shown in FIG. 2, the compressor (10) is equipped with an electric motor (14). The electric motor (14) is mounted on a rotating shaft (12). The electric motor (14) is driven by power supplied from an inverter not shown. As the electric motor (14) is driven, the rotating shaft (12) rotates.

[0014] One or more radial bearings (15) support the rotation axis (12) in a radial direction so that it can rotate. In this 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 of the rotation axis (12) between the first stage (12a) and the electric motor (14). The second radial bearing (15b) supports the portion of the rotation axis (12) between the electric motor (14) and the second stage (12b). In this embodiment, the center of gravity C1 of the compressor (10) is located between the two radial bearings (15) in the axial direction X. Two radial bearings (15) are fixed to the housing (11). The two radial bearings (15) rotatably support the rotation axis (12) with respect to the housing (11).

[0015] The rotating body (19) is provided with a support member (19a). The support member (19a) protrudes radially from the outer surface of the rotation axis (12). The support member (19a) is disc-shaped. The support member (19a) rotates integrally with the rotation axis (12).

[0016] In this embodiment, the bearing (18) includes one thrust bearing (16). The thrust bearing (16) includes bearing bodies arranged in pairs in the axial direction X with the support member (19a) in between. The thrust bearing (16) supports the support member (19a) in the thrust direction so that it can be rotated. Thus, the thrust bearing (16) supports the rotation axis (12) in the thrust direction so that it can be rotated. The thrust direction is the axial direction X of the rotation axis (12). The thrust bearing (16) supports the rotation axis (12) rotatably with respect to the housing (11).

[0017] 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 rotational speed of the rotating shaft (12) reaches a predetermined rotational speed. When the rotational speed of the rotating shaft (12) reaches a predetermined rotational speed, an air film is formed between the rotating shaft (12) and the bearing (18) by the air drawn in by the rotation of the rotating shaft (12). The rotating shaft (12) rises due to the dynamic pressure of the air film formed between the rotating shaft (12) and the bearing (18). Because of this, when the rotational speed of the rotating shaft (12) reaches a predetermined rotational speed, the bearing (18) supports the rotating shaft (12) through the air film without contacting the rotating shaft (12). By employing a gas bearing as the bearing (18), contact between the rotating shaft (12) and the housing (11) can be suppressed.

[0018] The compression mechanism (13) compresses the fluid by rotating together with the rotation shaft (12). In this embodiment, the fluid is a refrigerant. The compression mechanism (13) compresses the refrigerant sucked into the housing (11) in conjunction with the driving of the electric motor (14).

[0019] As shown in FIG. 1, the compressor (10) is provided with a plurality of protrusions (11d). The protrusions (11d) protrude from the outer surface (11a) of the housing (11). The protrusions (11d) are integrated with the housing (11). Therefore, the protrusions (11d) are made of the same metal as the housing (11). The plurality of protrusions (11d) extend from the outer surface (11a) of the housing (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 housing (11) toward the mounting surface (100a). The compressor (10) in this embodiment is provided with two protrusions (11d). The two protrusions (11d) are separated from each other in the axial direction X.

[0020] As shown in FIG. 2, one of the two protrusions (11d) is formed on the first side X1 with respect to the first radial bearing (15a) in the axial direction X. The other of the two protrusions (11d) is formed on the second side X2 with respect to the electric motor (14) in the axial direction X. Both of the two protrusions (11d) may be on the second side X2 with respect to the compression part (13a) in the axial direction X.

[0021] The center of gravity C1 of the compressor (10) is located, for example, on the axis of rotation (12). A virtual line extending from the center of gravity C1 of the compressor (10) in one direction orthogonal to the axial direction X of the axis of rotation (12) is denoted as virtual line VL. A plane containing the center of gravity C1 of the compressor (10) and also orthogonal to the axial direction X of the axis of rotation (12) is denoted as virtual plane VP. The virtual line VL extends on the virtual plane VP.

[0022] One direction orthogonal to the axis direction X is also called the first orthogonal direction Y. The direction orthogonal to the axis direction X and the first orthogonal direction Y is also called the second orthogonal direction Z. The second orthogonal direction Z is the direction in which the virtual line VL is extended. The first orthogonal direction Y is the direction in which a virtual straight line orthogonal to the axis of rotation L of the axis of rotation (12) and the virtual line VL is extended.

[0023] The virtual surface VP is located between two protrusions (11d) in the axial direction X. Among the plurality of protrusions (11d), at least one protrusion (11d) is located on the first side X1 with respect to the virtual surface VP, and at least one protrusion (11d) is located on the second side X2 with respect to the virtual surface VP. In the present embodiment, one protrusion (11d) is located on the first side X1 with respect to the virtual surface VP, and one protrusion (11d) is located on the second side X2 with respect to the virtual surface VP.

[0024] <Compressor Mounting Structure>

[0025] As shown in FIG. 1, the compressor (10) is mounted on the mounting surface (100a) of the vehicle (100) by means of a mounting structure (30). In other words, the mounting structure (30) is intended to mount the compressor (10) on the mounting surface (100a) of the vehicle (100). The mounting surface (100a) is, for example, part of the frame (101) that constitutes the vehicle (100). The combination of the compressor (10) and the mounting structure (30) is called a compressor unit or a compressor system.

[0026] The mounting structure (30) is provided with a plurality of mounting legs (20). The mounting legs (20) are fixed to each of the plurality of protrusions (11d). That is, the mounting legs (20) are fixed to the housing (11). In this embodiment, the mounting structure (30) is provided with two mounting legs (20). The two mounting legs (20) are separated from each other in the axial direction X.

[0027] The mounting leg (20) is made of an elastic member. The elastic member is formed by, for example, a rubber member or a urethane material which is an elastically deformable resin member. The mounting leg (20) is mounted, for example, at the tip of the protrusion (11d), that is, at the end of the protrusion (11d) opposite to the outer surface (11a) of the housing (11). The mounting leg (20) is, for example, cylindrical and extends from the tip of the protrusion (11d) toward the mounting surface (100a). The mounting leg (20) is mounted to the mounting surface (100a) using a fastening member such as a bolt. Thus, the mounting leg (20) is fixed to the mounting surface (100a). In this embodiment, the mounting surface (100a) on which a plurality of mounting legs (20) are mounted is a single plane.

[0028] As shown in FIGS. 1 and 2, one of the two mounting legs (20) is fixed to one of the two protrusions (11d), and the other of the two mounting legs (20) is fixed to the other of the two protrusions (11d). Accordingly, one of the two mounting legs (20) is connected to the housing (11) on the first side X1 with respect to the first radial bearing (15a) in the axial direction X. The other of the two mounting legs (20) is connected to the housing (11) on the second side X2 with respect to the electric motor (14) in the axial direction X. The virtual plane VP is located between the two mounting legs (20) in the axial direction X. Of the two mounting legs (20), one is located on the first side X1 with respect to the virtual plane VP, and the other is located on the second side X2 with respect to the virtual plane VP.

[0029] <Relationship between Resonant Frequencies>

[0030] The resonant frequency of each mounting leg (20) is set as the mounting leg resonant frequency F1. The resonant frequency of each radial bearing (15) is set as the radial bearing resonant frequency F2. The resonant frequency of the thrust bearing (16) is set as the thrust bearing resonant frequency F3. All mounting legs (20) formed in the mounting structure (30) may have the same mounting leg resonant frequency F1 or different mounting leg resonant frequencies F1.

[0031] The above mounting leg resonance frequency F1 is one of a plurality of mounting leg resonance frequencies F1. The plurality of mounting leg resonance frequencies F1 include a mounting leg resonance frequency F1 in the translational direction and a mounting leg resonance frequency F1 in the rotational direction. The mounting leg resonance frequency F1 in the translational direction includes three types: a mounting leg resonance frequency F1 in the translational direction following a virtual axis extending in the axial direction X, a mounting leg resonance frequency F1 in the translational direction following a virtual axis extending in the first orthogonal direction Y, and a mounting leg resonance frequency F1 in the translational direction following a virtual axis extending in the second orthogonal direction Z. The rotational mounting leg resonance frequency F1 includes three types: a rotational mounting leg resonance frequency F1 centered on a virtual axis extending in the axial direction X, a rotational mounting leg resonance frequency F1 centered on a virtual axis extending in the first orthogonal direction Y, and a rotational mounting leg resonance frequency F1 centered on a virtual axis extending in the second orthogonal direction Z. Among these six types of mounting leg resonance frequencies F1, the translational mounting leg resonance frequency F1 along the virtual axis extending in the first orthogonal direction Y is exemplified below.

[0032] In the compressor (10), the radial bearing resonance frequency F2 is set to be equal to the number of radial bearings (15) formed in the compressor (10). Therefore, in the compressor (10) of the present embodiment, two resonance frequencies are set as the radial bearing resonance frequency F2.

[0033] In the compressor (10), the thrust bearing resonance frequency F3 is set to be equal to the number of thrust bearings (16) formed in the compressor (10). Therefore, in the compressor (10) of the present embodiment, one resonance frequency is set as the thrust bearing resonance frequency F3.

[0034] The weight of the housing (11) is set as housing weight M1. The weight of the rotating body (19) is set as rotating body weight M2. The sum of the stiffness of the plurality of mounting legs (20) is set as mounting leg stiffness K1. The sum of the stiffness of the radial bearings (15) is set as radial bearing stiffness K2. The sum of the stiffness of the thrust bearings (16) is set as thrust bearing stiffness K3. Mounting leg stiffness K1, radial bearing stiffness K2, and thrust bearing stiffness K3 are values ​​expressed in units of N / m. Mounting leg stiffness K1, radial bearing stiffness K2, and thrust bearing stiffness K3 are stiffness in the direction in which the virtual line VL extends. The direction in which the virtual line VL extends is the direction of vibration acting on the compressor (10) from the vehicle (100) via the mounting legs (20).

[0035] The rigidity of the mounting leg (20) is a value unique to the mounting leg (20), determined by the shape and / or material of the mounting leg (20). The rigidity of the two mounting legs (20) formed in the mounting structure (30) may be the same value or different value. With respect to the sum of the rigidity of the plurality of mounting legs (20), the sum of the rigidity in the radial direction and the sum of the rigidity in the thrust direction are the same value.

[0036] The stiffness of the radial bearing (15) is a value unique to the radial bearing (15), determined by the shape and / or material of the radial bearing (15). The stiffness of the two radial bearings (15) formed in the compressor (10) may be the same value or different value. The stiffness of the thrust bearing (16) is a value unique to the thrust bearing (16), determined by the shape and / or material of the thrust bearing (16).

[0037] The mounting leg resonance frequency F1 can be expressed by the following equation (1).

[0038]

[0039] The radial bearing resonance frequency F2 can be expressed by the following equation (2).

[0040]

[0041] The thrust bearing resonance frequency F3 can be expressed by the following equation (3).

[0042]

[0043] The mounting leg resonance frequency F1 is smaller than the radial bearing resonance frequency F2 and also smaller than the thrust bearing resonance frequency F3. Therefore, from the above equations (1), (2), and (3), the following equations (4) and (5) are established.

[0044]

[0045]

[0046] The mounting leg resonance frequency F1 for which the above equations (4) and (5) hold is the mounting leg resonance frequency F1 in the translational direction along the virtual axis extending in the first orthogonal direction Y. At least one of the six types of mounting leg resonance frequencies F1 may be smaller than the radial bearing resonance frequency F2 and also smaller than the thrust bearing resonance frequency F3. Six types of mounting leg resonance frequencies F1 include, in addition to the mounting leg resonance frequency F1 in the translational direction along a virtual axis extending in the first orthogonal direction Y, a mounting leg resonance frequency F1 in the translational direction along a virtual axis extending in the axial direction X, a mounting leg resonance frequency F1 in the translational direction along a virtual axis extending in the second orthogonal direction Z, a mounting leg resonance frequency F1 in the rotational direction centered on a virtual axis extending in the axial direction X, a mounting leg resonance frequency F1 in the rotational direction centered on a virtual axis extending in the first orthogonal direction Y, and a mounting leg resonance frequency F1 in the rotational direction centered on a virtual axis extending in the second orthogonal direction Z.

[0047] <Comparison of Data>

[0048] Next, regarding the mounting structure (30) in the first embodiment and the mounting structure (30) in the first comparative example, the relationship between the excitation frequency and the amount of shaking of the rotor (19) was obtained experimentally. The results are shown in FIG. 4. In FIG. 4, the horizontal axis represents the excitation frequency, and the vertical axis represents the amount of shaking of the rotor (19). The excitation frequency is the frequency of vibration applied to the compressor (10) from the outside of the compressor (10). The amount of shaking of the rotor (19) is the amount of shaking of the compression part (13a). The amount of shaking of the compression part (13a) is, for example, the amount of displacement of the compression part (13a) in the radial direction of the rotation axis (12). In FIG. 4, the trajectory of the numerical value in the first embodiment is shown as a solid line. In FIG. 4, the trajectory of the numerical value in the first comparative example is shown as a dotted line.

[0049] The mounting structure (30) in the first embodiment has a mounting leg resonance frequency F1 that is smaller than the radial bearing resonance frequency F2, just like the embodiment. The mounting structure (30) in the first comparative example has a mounting leg resonance frequency F1 that is larger than the radial bearing resonance frequency F2, unlike the embodiment.

[0050] As shown in FIG. 4, the excitation frequency at which the peak of the shaking amount of the rotor (19) in the first embodiment occurs is smaller than the excitation frequency at which the peak of the shaking amount of the rotor (19) in the first comparative example occurs. In the first comparative example, the peak of the shaking amount of the rotor (19) occurred when the excitation frequency was near the radial bearing resonance frequency F2, whereas in the first embodiment, the peak of the shaking amount of the rotor (19) occurred when the excitation frequency was smaller than the radial bearing resonance frequency F2. Therefore, when the excitation frequency is the radial bearing resonance frequency F2, the shaking amount of the rotor (19) in the first embodiment is smaller than the shaking amount of the rotor (19) in the first comparative example.

[0051] When the excitation frequency is the radial bearing resonance frequency F2, the radial bearing (15) resonates in conjunction with the vibration applied to the compressor (10), causing the rotating body (19) to vibrate the most. Therefore, in order to suppress the vibration of the compression part (13a), it is desirable to reduce the amount of shaking of the rotating body (19) when the excitation frequency is the radial bearing resonance frequency F2. FIG. 4 shows that, as with the mounting structure (30) in the first embodiment, if the mounting leg resonance frequency F1 is smaller than the radial bearing resonance frequency F2, the vibration of the compression part (13a) can be suppressed.

[0052] For the case of the thrust bearing resonance frequency F3, it can be said to be the same as for the radial bearing resonance frequency F2 above. That is, the mounting structure (30) in the second embodiment has a mounting leg 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 leg resonance frequency F1 that is larger than the thrust bearing resonance frequency F3. In this case, the peak of the shaking amount of the rotor (19) in the second comparative example occurs when the excitation frequency is near the thrust bearing resonance frequency F3, whereas the peak of the shaking amount of the rotor (19) in the second embodiment occurs when the excitation frequency is smaller than the thrust bearing resonance frequency F3. As a result, when the frequency is the thrust bearing resonance frequency F3, the amount of shaking of the rotating body (19) in the second embodiment becomes smaller than the amount of shaking of the rotating body (19) in the second comparative example.

[0053] When the excitation frequency is the thrust bearing resonance frequency F3, the thrust bearing (16) resonates according to the vibration applied to the compressor (10), causing the rotor (19) to vibrate significantly. Therefore, in order to suppress the vibration of the compression part (13a), it is desirable to reduce the amount of shaking of the rotor (19) when the excitation frequency is the thrust bearing resonance frequency F3. Accordingly, as with the mounting structure (30) in the second embodiment, if the mounting leg resonance frequency F1 is smaller than the thrust bearing resonance frequency F3, the vibration of the compression part (13a) can be suppressed.

[0054] [Actions and Effects of the Embodiment]

[0055] The operation and effects of the embodiment are explained.

[0056] (1) The mounting leg resonance frequency F1 is smaller than the radial bearing resonance frequency F2 and also smaller than the thrust bearing resonance frequency F3. Therefore, the amount of shaking of the rotating body (19) can be reduced during the resonance of the radial bearing (15), which is when the rotating body (19) vibrates the most. Thus, the vibration of the compression mechanism (13) that occurs along with the vibration of the vehicle (100) can be suppressed.

[0057] (2) The compression mechanism (13) is formed at the first stage (12a) of the rotating shaft (12) and is not formed at the second stage (12b). Therefore, compared to the case where the compression mechanism (13) is formed at both ends of the rotating shaft (12), the amount of shaking of the rotating body (19) is likely to increase due to the center of the rotating body (19) being offset. Thus, even in cases where vibration of the rotating body (19) is a greater concern, by adopting the mounting structure (30) of this embodiment, the vibration of the compression mechanism (13) that occurs along with the vibration of the vehicle (100) can be suppressed.

[0058] (3) The compression mechanism (13) includes a compression part (13a) which is an impeller. In this case, since the compression part (13a) is not in contact with the housing (11), the amount of vibration of the compression part (13a) becomes a problem. That is, because the size of the tip clearance (11c) formed between the shroud surface (11b) of the housing (11) and the compression part (13a) is small, if the compression mechanism (13) vibrates significantly, the compression part (13a) is likely to collide with the housing (11). Even in this case, by suppressing the vibration of the compression mechanism (13) that occurs along with the vibration of the vehicle (100), the collision of the compression part (13a) with the housing (11) can be suppressed.

[0059] (4) The compressor (10) is mounted on the mounting surface (100a) of the vehicle (100) by means of a mounting structure (30). The fluid compressed by the compression mechanism (13) is a refrigerant. Since the refrigerant has a higher load density than air, compared to the case where air is used as the fluid compressed by the compression mechanism (13), the rotating shaft (12) is less likely to collide with the radial bearing (15) and thrust bearing (16) when vibration acts on the housing (11). Meanwhile, the vibration of the compression mechanism (13) that is a concern because the rotating shaft (12) does not collide with the radial bearing (15) and thrust bearing (16) when vibration acts on the housing (11) can be suppressed by using the mounting structure (30).

[0060] (5) Radial bearings (15) and thrust bearings (16) are gas bearings. The rigidity of gas bearings tends to be lower than that of rolling bearings. Therefore, when gas bearings are used for radial bearings (15) and thrust bearings (16), the radial bearing resonance frequency F2 and thrust bearing resonance frequency F3 are reduced compared to when rolling bearings are used for radial bearings (15) and thrust bearings (16). In this way, even in cases where the radial bearing resonance frequency F2 and thrust bearing resonance frequency F3 tend to be close to the mounting leg resonance frequency F1, by adopting the mounting structure (30) of this embodiment, the vibration of the compression mechanism (13) that occurs along with the vibration of the vehicle (100) can be suppressed. In addition, since the radial bearing (15) and thrust bearing (16), which are gas bearings, are in non-contact with respect to the rotation axis (12), the amount of shaking of the compression mechanism (13) becomes a problem. This vibration of the compression mechanism (13) can be suppressed by adopting a mounting structure (30).

[0061] (6) The mounting leg (20) is made of an elastic member. Because of this, the vibration damping effect of the mounting leg (20) is higher than when the mounting leg (20) is made of a metal member, so the vibration of the compressor (10) during the vibration of the vehicle (100) can be suppressed. Therefore, the vibration of the compression mechanism (13) that occurs along with the vibration of the vehicle (100) can be further suppressed. In addition, by adopting the mounting leg (20) made of an elastic member, the mounting rigidity of the mounting leg (20) with respect to the housing (11) and the mounting surface (100a) can be reduced compared to, for example, the mounting leg (20) made of a metal member. Therefore, since the mounting leg rigidity K1 can be reduced, the mounting leg resonance frequency F1 can be made smaller than the radial bearing resonance frequency F2 and also smaller than the thrust bearing resonance frequency F3.

[0062] (7) The compressor (10) is mounted on the vehicle (100). Because of this, vibrations from the vehicle (100) are transmitted to the compressor (10), so the vibrations applied to the compressor (10) from the outside are greater compared to, for example, when the compressor (10) is formed at a location other than the vehicle (100). By adopting the mounting structure (30) of the present embodiment for the compressor (10) which receives large vibrations from the outside in this way, the vibration of the compression mechanism (13) can be suppressed.

[0063] [Change Example]

[0064] The embodiments may be implemented by modifying them as follows. The embodiments and the following variations may be implemented in combination with one another to the extent that they are not technically contradictory.

[0065] The number of mounting legs (20) provided by the mounting structure (30) may be 1 or 3 or more. Depending on the number of mounting legs (20), the number of protrusions (11d) formed on the housing (11) may be changed.

[0066] ○ The mounting leg (20) may be fixed directly to the outer surface (11a) of the housing (11) without interposing the protrusion (11d). In this case, the protrusion (11d) from the compressor (10) may be omitted.

[0067] ○ When the mounting structure (30) is provided with a plurality of mounting legs (20), the mounting surface (100a) to which the plurality of mounting legs (20) are fixed is not limited to the same plane. The mounting surface (100a) to which at least one of the plurality of mounting legs (20) is fixed and the mounting surface (100a) to which at least one other mounting leg (20) is fixed may be extended in different directions from each other. In this case, the axial direction of the mounting leg (20) extending from the housing (11) toward the mounting surface (100a) may be different for each mounting leg (20).

[0068] ○ When the mounting structure (30) has a plurality of mounting legs (20), two or more mounting legs (20) may be located on the first side X1 with respect to the virtual plane VP, and two or more mounting legs (20) may be located on the second side X2 with respect to the virtual plane VP. All mounting legs (20) provided by the mounting structure (30) may be located on the first side X1 with respect to the virtual plane VP, or on the second side X2 with respect to the virtual plane VP.

[0069] ○ The radial bearing (15) provided by the compressor (10) may be one or three or more. The thrust bearing (16) provided by the compressor (10) may be two or more.

[0070] ○ The compression mechanism (13) may be formed at both ends in the axial direction X of the rotation axis (12).

[0071] ○ The compression mechanism (13) is not limited to including an impeller as the compression part (13a). For example, the compressor (10) may be of the piston type or scroll type.

[0072] ○ The compressor (10) was used in a vehicle air conditioning system, but is not limited to this. The compressor (10) only needs to compress the refrigerant, and the use of the compressor (10) can be appropriately changed.

[0073] ○ The compression mechanism (13) may compress a fluid other than a refrigerant. For example, the compression mechanism (13) may compress air.

Claims

Claim 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 formed 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 supporting the rotating shaft in a radial direction so as to be rotatable, a thrust bearing supporting the rotating shaft in a thrust direction so as to be rotatable, and a housing that accommodates the rotating body, the radial bearing, and the thrust bearing, wherein the radial bearing and the thrust bearing are gas bearings, and the mounting structure comprises a mounting leg made of an elastic member that is fixed to the housing and the mounting surface, wherein the resonance frequency of the mounting leg is smaller than the resonance frequency of the radial bearing and also smaller than the resonance frequency of the thrust bearing. Claim 2 In claim 1, the compression mechanism is a mounting structure formed at one end in the axial direction of the rotation axis and not formed at the other end of the rotation axis. Claim 3 In claim 1 or 2, the compression mechanism comprises a mounting structure including an impeller. Claim 4 A compressor mounted on the mounting surface by means of the mounting structure described in claim 1 or 2, wherein the fluid is a refrigerant.

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