Two-rotary scroll compressor

Abstract

To suppress vibration and noise which are generated resulting from a compression load acting on a drive axial core in a radial direction while providing an inverter circuit on an external peripheral face of a housing.SOLUTION: When assuming a plane orthogonal to a drive axial core X1, a middle point MP between a center of a drive-side base circle 34 and a center of a driven-side base circle 44 is stipulated as an action point of a compression load which is generated in a radial direction of the drive axial core X1, and a direction orthogonal to a virtual line VL for connecting a first tangent point P1 at which an outside face 33A of a drive spiral body 33 and an inside face 43B of a driven spiral body 43 contact with each other at the most external peripheral side, and a second tangent point P2 at which an inside face 33B of the drive spiral body 33 and an outside face 43A of the driven spiral body 43 contact with each other at the most external peripheral side is stipulated as a load direction LD of the compression load. When stipulating a range in which the load direction LD varies while a drive scroll 30 rotates one round as a variation range FR, an inverter circuit 12 provided at an external peripheral face of a cylindrical housing 60 is placed while avoiding the variation range FR in a circumferential direction of the drive axial core X1.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a double-rotary scroll compressor.

Background Art

[0002] Patent Document 1 discloses a conventional double-rotary scroll compressor (hereinafter simply referred to as a compressor). This compressor includes a drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a cylindrical housing.

[0003] The drive mechanism has an electric motor provided in the housing. The drive scroll is provided in the housing and is rotationally driven around the drive axis by the drive mechanism. The driven scroll is provided in the housing and is rotationally driven by the drive scroll and the driven mechanism around the driven axis while being eccentric with respect to the drive scroll.

[0004] The drive scroll has a drive end plate and a drive spiral body. The drive end plate extends in a direction intersecting the drive axis. The drive spiral body protrudes from the drive end plate toward the driven scroll and has a spiral shape.

[0005] The driven scroll has a driven end plate and a driven spiral body. The driven end plate extends in a direction intersecting the driven axis. The driven spiral body protrudes from the driven end plate toward the drive scroll and has a spiral shape.

[0006] The drive scroll and the driven scroll form a compression chamber with the drive spiral body and the driven spiral body facing each other, and change the volume of the compression chamber by rotational driving and rotational following.

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0008] During the operation of the compressor, a compression load is generated when the refrigerant is compressed in the compression chamber. This compression load mainly acts in the radial direction of the drive shaft center rather than in the axial direction of the drive shaft center. Therefore, there is a possibility that the housing vibrates when the radial compression load of the drive shaft center acts on the housing through bearings that support the drive scroll and the driven scroll.

[0009] However, in the conventional compressor described above, the vibration of the housing caused by such a compression load is not regarded as a problem. If an inverter circuit for driving an electric motor is provided on the outer peripheral surface of the housing to avoid the compressor from being enlarged in the axial direction of the drive shaft center, the vibration of the housing may be amplified by the thin-shaped casing that houses the inverter circuit and the inverter board, and the noise may also deteriorate.

[0010] The present invention has been made in view of the above conventional situation, and an object of the present invention is to provide a twin-rotary scroll compressor capable of suppressing vibration and noise generated due to a compression load acting in the radial direction of the drive shaft center while providing an inverter circuit on the outer peripheral surface of the housing.

Means for Solving the Problems

[0011] The twin-rotary scroll compressor of the present invention includes a drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a cylindrical housing. The drive scroll is provided in the housing and is rotationally driven around the drive shaft center by the drive mechanism. The driven scroll is provided in the housing and is rotationally driven by the drive scroll and the driven mechanism around the driven shaft center while being eccentric with respect to the drive scroll. The drive scroll has a drive end plate extending in a direction intersecting the drive shaft center, and a drive spiral body protruding from the drive end plate toward the driven scroll and having a spiral shape. The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven spiral body protruding from the driven end plate toward the driving scroll and having a spiral shape. In the twin rotary scroll compressor in which the driving scroll and the driven scroll form a compression chamber by facing each other with the driving spiral body and the driven spiral body, and change the volume of the compression chamber by the rotational drive and the rotational following, The drive mechanism has an electric motor provided in the housing and an inverter circuit provided on an outer peripheral surface of the housing for driving the electric motor. When assuming a plane orthogonal to the driving axis, The midpoint between the center of the driving-side basic circle forming the driving spiral body and the center of the driven-side basic circle forming the driven spiral body is defined as the action point of the compression load generated in the radial direction of the driving axis by the rotation of the driving scroll and the driven scroll. The load direction of the compression load is defined as the direction orthogonal to the virtual line connecting a first contact point where the outer surface of the driving spiral body and the inner surface of the driven spiral body are in contact on the outermost peripheral side and a second contact point where the inner surface of the driving spiral body and the outer surface of the driven spiral body are in contact on the outermost peripheral side, and when defining the range in which the load direction fluctuates while the driving scroll and the driven scroll make one rotation as the fluctuation range, the inverter circuit is characterized by being arranged to avoid the fluctuation range in the circumferential direction of the driving axis.

[0012] In a twin rotary scroll compressor, when the refrigerant is compressed in the compression chamber, a compression load mainly acting in the radial direction of the driving axis is generated.

[0013] Even in a scroll compressor having a fixed scroll and a orbiting scroll, a compression load acts in the radial direction of the rotating shaft that rotates the orbiting scroll. The direction of the compression load acting in the radial direction of this rotating shaft rotates with the rotation of the orbiting scroll and changes 360 degrees. In the following description, unless otherwise specified, the compression load means a compression load acting in the radial direction of the drive shaft center or the rotating shaft center.

[0014] On the other hand, in a twin-rotary scroll compressor, the drive scroll and the driven scroll rotate at the same angular velocity while being eccentric. For this reason, the direction of the compression load does not change significantly during the operation of the compressor in the circumferential direction of the drive shaft center. That is, the range of the compression load generated during the operation of the compressor is limited to a predetermined small angular range in the circumferential direction of the drive shaft center. The inventors of the present invention completed the present invention by paying attention to this point.

[0015] That is, when the direction of the compression load rotates with the rotation of the orbiting scroll and changes 360 degrees, if an inverter circuit is provided on the outer peripheral surface of the housing, every time the orbiting scroll makes one rotation, the compression load will surely act on the entire angular range occupied by the inverter circuit in the circumferential direction. For this reason, there is a possibility that the vibration of the housing generated by the influence of the compression load will be greatly amplified.

[0016] In this regard, in the twin-rotary scroll compressor of the present invention, the inverter circuit provided on the outer peripheral surface of the housing is arranged so as to avoid the above-described variation range in the circumferential direction of the drive shaft center. For this reason, it is possible to suppress the amplification of the vibration of the housing caused by the compression load by the thin-shaped casing that houses the inverter circuit and the inverter substrate, and as a result, it is also possible to suppress the deterioration of the noise.

[0017] Therefore, the twin-rotary scroll compressor of the present invention can suppress vibration and noise generated due to the compression load acting in the radial direction of the drive shaft center while providing an inverter circuit on the outer peripheral surface of the housing.

[0018] The electric motor has a stator fixed to the housing and a rotor disposed within the stator and rotatable together with the drive scroll. It is preferable that the drive scroll is built into the rotor and the inverter circuit is disposed on the outer periphery of the stator.

[0019] In this case, the inverter circuit will be disposed on the outer periphery of the drive scroll. If the drive scroll and the inverter circuit are arranged in the radial direction of the drive axis, the influence of the compressive load acting on the drive scroll and the driven scroll is likely to reach the housing and the inverter circuit provided on its outer peripheral surface via bearings that support them. For this reason, the problem that the vibration of the housing is amplified by the inverter circuit becomes particularly prominent, but this problem can be effectively solved by the present invention.

[0020] Also, since the inverter circuit is disposed on the outer periphery of the stator, it is advantageous for simplifying the wiring structure for power supply from the inverter circuit to the stator.

[0021] Furthermore, since the drive scroll is also built into the rotor, the stator, the rotor, and the inverter circuit are arranged in the radial direction of the drive axis with respect to the drive scroll and the driven scroll. For this reason, the compressor can be miniaturized in the drive axis direction as compared with the case where the stator, the rotor, and the inverter circuit are arranged in the drive axis direction with respect to the drive scroll and the driven scroll.

Effect of the Invention

[0022] The double-rotary scroll type compressor of the present invention can suppress vibrations and noises generated due to the compressive load acting in the radial direction of the drive axis while providing an inverter circuit on the outer peripheral surface of the housing.

Brief Description of the Drawings

[0023]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

MODE FOR CARRYING OUT THE INVENTION

[0024] Hereinafter, embodiments embodying the present invention will be described with reference to the drawings.

[0025] (Embodiment) As shown in Fig. 1, the double-rotary scroll compressor 1 of the embodiment (hereinafter simply referred to as the compressor 1) is an example of a specific aspect of the present invention. The compressor 1 includes a housing 60. The housing 60 has a housing main body 61 and a cover 65.

[0026] The housing main body 61 is a bottomed cylindrical member having an outer peripheral wall 62 and a bottom wall 63. The outer peripheral wall 62 has a cylindrical inner peripheral surface 62C centered on the drive axis X1. The bottom wall 63 extends in a substantially circular flat plate shape orthogonal to the drive axis X1.

[0027] The outer peripheral edge of the bottom wall 63 is connected to the base end of the outer peripheral wall 62 away from the cover 65. A cylindrical shaft support portion 64 centered on the drive axis X1 is protruding from the center of the inner surface of the bottom wall 63. The outer ring of the bearing 71 is fitted into the shaft support portion 64.

[0028] The cover 65 extends in a substantially circular flat plate shape orthogonal to the drive axis X1. The cover 65 closes the housing main body 61 by being fastened to the outer peripheral wall 62 by bolts (not shown) in a state where the outer peripheral edge thereof abuts against the tip of the outer peripheral wall 62 of the housing main body 61.

[0029] A cylindrical shaft support portion 66 centered on the driven axis X2 is protruding from the center of the inner surface of the cover 65. The driven axis X2 extends parallel to the drive axis X1 while being eccentric with a predetermined eccentricity with respect to the drive axis X1. The outer ring of the needle bearing 72 is fitted into the shaft support portion 66.

[0030] The cover 65 has a suction hole 67 and a discharge hole 68. The suction hole 67 is located between the outer peripheral edge and the shaft support portion 66 of the cover 65 and penetrates the cover 65 in a direction parallel to the drive axis X1. The discharge hole 68 is located at the center of the cover 65 and penetrates the cover 65 in a direction parallel to the drive axis X1.

[0031] As shown in Figs. 1 and 2, the compressor 1 includes a drive mechanism 10, a driven mechanism 20, a drive scroll 30, and a driven scroll 40.

[0032] The drive mechanism 10 rotationally drives the drive scroll 30 around the drive axis X1. The drive mechanism 10 includes an electric motor 11 and an inverter circuit 12 that drives the electric motor 11. The electric motor 11 includes a stator 13 and a rotor 14.

[0033] The inverter circuit 12 is provided on the outer peripheral side surface of the cylindrical housing body 61, that is, on the outer peripheral surface of the outer peripheral wall 62. The inverter circuit 12 is built into the inverter case 15. In the circumferential direction of the outer peripheral wall 62, the portion of the outer peripheral wall 62 where the inverter case 15 is attached is a thick portion 62A that is thicker than other thin-walled general portions 62B. The outer surface of this thick portion 62A is a flat surface 62D. The inverter case 15 is fixed to the flat surface 62D by bolts (not shown). The inverter substrate constituting the inverter circuit 12 is disposed substantially parallel to the flat surface 62D.

[0034] As shown in FIG. 2, the inverter case 15 is disposed in the circumferential direction of the drive axis X1 and the driven axis X2 in the direction in which the drive axis X1 and the driven axis X2 are aligned, that is, in the linear direction connecting the drive axis X1 and the drive axis X2. Note that the inverter case 15 is disposed in the circumferential direction of the drive axis X1 and the driven axis X2 in the direction of the virtual line VL described later. Further, as will be described later, the inverter case 15 is disposed in the circumferential direction of the drive axis X1 and the driven axis X2 so as to avoid the variation range FR of the load direction LD of the compressive load and the generation range GR of the compressive load.

[0035] The stator 13 is cylindrical with the drive axis X1 as the center and has windings 16. The stator 13 is fixed to the housing 60 around the drive axis X1 by fitting into the inner peripheral surface 62C of the outer peripheral wall 62 of the housing body 61.

[0036] The rotor 14 is cylindrical around the drive axis X1. The rotor 14 is composed of a plurality of permanent magnets (not shown) corresponding to the stator 13 and a laminated steel plate (not shown) for fixing each permanent magnet. The rotor 14 is disposed on the inner circumference of the stator 13 and is rotatable within the stator 13.

[0037] The drive scroll 30 is built into the rotor 14. A drive peripheral wall 32 (described later) of the drive scroll 30 is fitted to the inner peripheral surface 14A of the rotor 11. Thereby, the rotor 14 and the drive scroll 30 are integrally rotated. Thus, the drive scroll 30 is rotationally driven around the drive axis X1 by the drive mechanism 10.

[0038] As shown in FIG. 1, the drive scroll 30 has a drive end plate 31, a drive peripheral wall 32, and a drive spiral body 33.

[0039] The drive end plate 31 extends in a substantially circular flat plate shape orthogonal to the drive axis X1. At the center of the surface of the drive end plate 31 facing the bottom wall 63 of the housing body 61, a cylindrical shaft support portion 34 centered on the drive axis X1 is protruding.

[0040] The inner ring of the bearing 71 is externally fitted to the shaft support portion 34. Thereby, the drive scroll 30 is supported by the housing body 61 so as to be rotatable around the drive axis X1.

[0041] The drive peripheral wall 32 protrudes from the outer peripheral edge 31F of the drive end plate 31 toward the driven scroll 40 in parallel with the drive axis X1 and is cylindrical around the drive axis X1.

[0042] As shown in FIGS. 1 and 2, the drive spiral body 33 is located radially inside the drive axis X1 than the drive peripheral wall 32. The drive spiral body 33 protrudes from the drive end plate 31 toward the driven scroll 40 in parallel with the drive axis X1 and is spiral around the drive axis X1.

[0043] The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0044] The driven end plate 41 extends in a substantially circular flat plate shape orthogonal to the driven axis X2. At the center of the surface of the driven end plate 41 facing the cover 65, a cylindrical shaft support portion 44 centered on the driven axis X2 protrudes.

[0045] The inner ring of the needle bearing 72 is externally fitted to the shaft support portion 44. Thereby, the driven scroll 40 is supported by the cover 65 so as to be rotatable around the driven axis X2.

[0046] The driven end plate 41 has an intake port 47 (see FIG. 2) and a discharge port 48.

[0047] The intake port 47 is located radially outside the driven axis X2 from the outer peripheral surface of the shaft support portion 66 and penetrates the driven end plate 41 in a direction parallel to the driven axis X2. Two intake ports 47 are formed on the driven end plate 41 with a 180-degree phase difference.

[0048] The discharge port 48 is located radially inside the driven axis X2 from the inner peripheral surface of the shaft support portion 44 and penetrates the driven end plate 41 in a direction parallel to the driven axis X2.

[0049] The space surrounded by the inner peripheral surface of the shaft support portion 44 and sandwiched between the cover 65 and the driven end plate 41 is defined as a discharge chamber 55.

[0050] The driven end plate 41 is provided with a discharge valve 58 that is located on the discharge chamber 55 side and opens and closes the discharge port 48, and a retainer 59 that regulates the opening degree of the discharge valve 58.

[0051] As shown in FIGS. 1 and 2, the driven scroll 43 protrudes parallel to the driven axis X2 from the driven end plate 41 toward the drive scroll 30 and forms a spiral shape around the driven axis X2.

[0052] The drive scroll 30 and the driven scroll 40 face each other, and the drive scroll 33 and the driven scroll 43 mesh with each other to form a compression chamber 50.

[0053] The driven mechanism 20 includes a plurality of sets (three or more sets in the pin-ring system) of pins 21 and rings 22. Each set of pins 21 and rings 22 transmits the driving force from the driving scroll 30 to the driven scroll 40.

[0054] Each pin 21 is a cylindrical member that projects from the tip of the driving peripheral wall 32 toward the driven end plate 41 at appropriate intervals in the circumferential direction of the driving axis X1.

[0055] Each ring 22 is provided on the side of the driven end plate 41 so as to face each pin 21. Each ring 22 is fitted into a circular bottomed hole recessed in the driven end plate 41. Each pin 21 is movable in a state of being in sliding contact with the inner peripheral surface of each ring 22.

[0056] When the driving scroll 30 is rotationally driven around the driving axis X1 by the driving mechanism 10, each pin 21 relatively rotates each ring 22 around the center of each pin 21 while slidingly contacting the inner peripheral surface of each ring 22, thereby transmitting the torque of the driving scroll 30 to the driven scroll 40. The turning radius of the ring 22 is equal to the amount of eccentricity of the driven axis X2 of the driven scroll 40 with respect to the driving axis X1 of the driving scroll 30.

[0057] As a result, the driven scroll 40 is rotationally driven by the driving scroll 30 and the driven mechanism 20 around the driven axis X2 parallel to the driving axis X1 while being eccentric with respect to the driving scroll 30. The driving scroll 30 and the driven scroll 40 change the volume of the compression chamber 50 by the relative revolution of the driven scroll 40 around the driving axis X1 with respect to the driving scroll 30 due to their rotational driving and rotational following.

[0058] Although illustration is omitted, this compressor 1 constitutes a refrigeration circuit of a vehicle air conditioner together with an evaporator, an expansion valve, and a condenser. An evaporator is connected to the suction hole 67 by a pipe. A condenser is connected to the discharge hole 68 by a pipe. The expansion valve is connected to the evaporator and the condenser by pipes.

[0059] The refrigerant supplied from the evaporator flows into the housing 60 through the suction hole 67 and is introduced into the compression chamber 50 via the suction port 47. The refrigerant compressed to the discharge pressure in the compression chamber 50 is discharged into the discharge chamber 55 via the discharge port 48 and is discharged from the discharge hole 68 to the condenser. Thus, the air conditioning of the vehicle air conditioner is performed.

[0060] <Range of variation in the load direction> During the operation of the compressor 1, a compression load is generated in the compression chamber 50 due to the rotation of the drive scroll 30 and the driven scroll 40.

[0061] Figs. 3 to 11 are views assuming a plane orthogonal to the drive axis X1 and the driven axis X2. Figs. 3 to 9 show the load direction LD of the compression load generated in the compression chamber 50 at intervals of 60 degrees of rotation during one rotation of the drive scroll 30 and the driven scroll 40 during the operation of the compressor 1.

[0062] In Figs. 3 to 11, only the drive spiral body 33 and the driven spiral body 43 of the drive scroll 30 and the driven scroll 40, which substantially contribute to the formation of the compression chamber 50, are schematically shown. In Figs. 3 to 9, a drive-side base circle (the base circle of the involute curve) 34 that forms the outer surface 33A and the inner surface 33B of the drive spiral body 33 and a driven-side base circle (the base circle of the involute curve) 44 that forms the outer surface 43A and the inner surface 43B of the driven spiral body 43 are shown. Among the circles indicated by the two-dot chain line, the upper one in the figure is the drive-side base circle 34, and the lower one in the figure is the driven-side base circle 44. The center of the drive-side base circle 34 and the center of the driven-side base circle 44 are offset by a predetermined amount in a direction orthogonal to the drive axis X1. In Figs. 3 to 9, the central one of the three black circles is the midpoint MP between the center of the drive-side base circle 34 and the center of the driven-side base circle 44. In Fig. 3, the upper one of the two white circles indicates the position of the drive axis X1, and the lower one indicates the position of the driven axis X2. In Figs. 4 to 9, the position of the drive axis X1 is shown, but the driven axis X2 is omitted.

[0063] Figure 3 shows the state at the moment when the two compression chambers 50, 50 on the outermost peripheral side are closed (at the time of confinement, 0 deg). At this time, the outer surface 33A of the driving scroll 33 and the inner surface 43B of the driven scroll 43 are in contact with each other at the first contact point P1 on the outermost peripheral side, and the inner surface 33B of the driving scroll 33 and the outer surface 43A of the driven scroll 43 are in contact with each other at the second contact point P2 on the outermost peripheral side.

[0064] A virtual line VL connecting the first contact point P1 and the second contact point P2, which are two contact points where the driving scroll 33 and the driven scroll 43 are in contact with each other on the outermost peripheral side, is defined. The length of the virtual line VL can be regarded as the radial width RW of the entire two compression chambers 50. The midpoint MP can be regarded as the center of the entire two compression chambers 50. A surface that includes the virtual line VL and extends in the axial direction of the driving axis X1 and the driven axis X2 is defined as the pressure receiving surface of the compression load. The midpoint MP between the center of the driving-side base circle 34 and the center of the driven-side base circle 44 is defined as the action point of the compression load. In a plane orthogonal to the driving axis X1 and the driven axis X2, the direction orthogonal to the virtual line VL is defined as the load direction (action direction) LD of the compression load.

[0065] Note that the first contact point P1 is located on one tangent line that is in contact with both the driving-side base circle 34 and the driven-side base circle 44. The second contact point P2 is located on the other tangent line that is in contact with both the driving-side base circle 34 and the driven-side base circle 44. These tangent lines extend parallel to the virtual line VL.

[0066] Figure 4 shows the state when rotated 60 degrees from the time of confinement. Figure 5 shows the state when rotated 120 degrees from the time of confinement. Figure 6 shows the state when rotated 180 degrees from the time of confinement. Figure 7 shows the state when rotated 240 degrees from the time of confinement. Figure 8 shows the state when rotated 300 degrees from the time of confinement. Figure 9 shows the state immediately before rotating 360 degrees from the time of confinement.

[0067] As shown in Figures 4 to 9, as the rotation of the driving scroll 30 and the driven scroll 40 progresses, the first contact point P1 and the second contact point P2 are displaced toward the inner peripheral side. Along with this, the length of the virtual line VL, that is, the radial width RW of the entire two compression chambers 50, also gradually decreases.

[0068] The driving axis X1 of the driving scroll 30 and the driven axis X2 of the driven scroll 40 are eccentric with a predetermined amount of eccentricity. As the driving scroll 30 and the driven scroll 40 rotate, the first contact point P1 and the second contact point P2 move, so that the load direction LD of the compression load with the midpoint MP as the point of action also fluctuates. The range in which the load direction LD fluctuates while the driving scroll 30 and the driven scroll 40 make one rotation is defined as the fluctuation range FR.

[0069] Assuming a horizontal line in FIGS. 3 to 9, the angle of the load direction LD with respect to the horizontal line is defined as the load angle θ. The minimum load angle θmin is obtained at the time of confinement shown in FIG. 3, and the maximum load angle θmax is obtained at the time immediately before rotating 360 degrees from the time of confinement shown in FIG. 9.

[0070] As shown in FIG. 10, the fluctuation range FR of the load direction LD is the angular range of the difference between the minimum load angle θmin and the maximum load angle θmax. In FIG. 10, the load direction LD at the time of confinement is indicated by a solid line arrow, and the load direction LD at the time immediately before rotating 360 degrees from the time of confinement is indicated by a two-dot chain line.

[0071] <Range of generation of compression load> At the time of confinement shown in FIG. 3, the size of the entire two compression chambers 50 becomes the maximum. At this time, in the radial direction of the driving axis X1 and the driven axis X2, that is, in the plane orthogonal to the driving axis X1 and the driven axis X2, the range of the compression load generated in the compression chamber 50 becomes the maximum.

[0072] As shown in FIG. 11, the range extending in the load direction LD at this time with a width equal to the distance between the first contact point P1 and the second contact point P2 at the time of confinement, that is, the length of the virtual line VL, is defined as the generation range GR of the compression load.

[0073] As shown in FIG. 2, in this compressor 1, the inverter case 15 incorporating the inverter circuit 12 is arranged so as to avoid the fluctuation range FR of the load direction LD of the compression load and the generation range GR of the compression load in the circumferential direction of the driving axis X1 and the driven axis X2.

[0074] <Effect> As described above, in the compressor 1 of the embodiment, the inverter case 15 provided on the outer peripheral wall 62 of the housing body 61 is arranged so as to avoid the fluctuation range FR of the load direction LD of the compression load in the circumferential direction of the drive shaft center X1 and the driven shaft center X2. The load direction LD of the compression load with the midpoint MP between the center of the drive-side base circle 34 and the center of the driven-side base circle 44 as the action point is the direction of the compression load acting outside the compression chamber 50 at the center of the entire two compression chambers 50. By arranging the inverter case 15 so as to avoid the fluctuation range FR in which this load direction LD fluctuates during the operation of the compressor 1, it is possible to suppress the influence of the compression load generated in the compressor 50 from reaching the inverter case 15.

[0075] The distance between the first contact point P1 and the second contact point P2, that is, the length of the virtual line VL, can be regarded as the radial width RW of the entire two compression chambers. The size of the entire two compression chambers 50 is the largest at the time of confinement. The distance between the first contact point P1 and the second contact point P2 at the time of confinement, that is, the length of the virtual line VL, can be regarded as the length at which the radial width RW of the entire two compression chambers 50 is the largest. By arranging the inverter case 15 with a width equal to the distance between the first contact point P1 and the second contact point P2 (the length of the virtual line VL) at the time of confinement and avoiding the generation range GR of the compression load extending in the load direction LD at this time, it is possible to further suppress the influence of the compression load generated in the compressor 50 from reaching the inverter case 15.

[0076] For this reason, in the compressor 1 of the embodiment, it is possible to suppress the vibration of the housing 60 caused by the compression load generated in the compression chamber 50 from being amplified by the inverter circuit 12 and the inverter case 15, and as a result, it is also possible to suppress the deterioration of the noise.

[0077] Therefore, the double-rotary scroll compressor 1 of the embodiment can suppress the vibration and noise generated due to the compression load acting in the radial direction of the drive shaft center X1 while providing the inverter circuit 12 on the outer peripheral surface of the housing 60.

[0078] In this compressor 1, a drive scroll 30 and a driven scroll 40 are incorporated in an electric motor 11 provided within a housing 60, and an inverter case 15 including an inverter circuit 12 is disposed on the outer peripheral side thereof, that is, radially outward of the drive axis X1.

[0079] In this case, the inverter case 15 is disposed on the outer periphery of the drive scroll 30. If the drive scroll 30 and the inverter case 15 are arranged in the radial direction of the drive axis X1, the influence of the compression load acting on the drive scroll 30 and the driven scroll 40 easily reaches the housing 60, the inverter case 15 provided on its outer peripheral surface, and the inverter circuit 12 through bearings or the like that support them. For this reason, the problem that the vibration of the housing 60 is amplified by the inverter circuit 12 and the inverter case 15 becomes particularly prominent, but this compressor 1 can effectively solve this problem.

[0080] Further, since the inverter circuit 12 is disposed on the outer periphery of the stator 13, it is advantageous for simplifying the wiring structure for supplying power from the inverter circuit 12 to the stator 13.

[0081] Furthermore, since the electric motor 11 and the inverter case 15 are arranged in the radial direction of the drive axis X1 with respect to the drive scroll 30 and the driven scroll 40, the compressor 1 can be miniaturized in the direction of the drive axis X1 as compared with the case where the electric motor 11 and the inverter case 15 are arranged in the direction of the drive axis X1 with respect to the drive scroll 30 and the driven scroll 40.

[0082] As described above, the present invention has been described with reference to the embodiments, but it goes without saying that the present invention is not limited to the above embodiments and can be appropriately modified and applied without departing from the spirit thereof.

[0083] In the embodiment, the inverter circuit 12 and the inverter case 12 are arranged in the circumferential direction of the drive axis X1 and the driven axis X2 in the linear direction connecting the drive axis X1 and the driven axis X2 or in the direction of the virtual line VL, the inverter circuit 12 exists on these straight lines, and the inverter circuit 12 is arranged so as to be substantially orthogonal to these straight lines. However, the present invention is not limited to this configuration. The position and angle of the inverter circuit 12 in the circumferential direction of the drive axis X1 can be set as appropriate as long as the variation range FR of the load direction LD can be avoided.

[0084] In the embodiment, the electric motor 11 and the inverter circuit 12 are arranged in the radial direction of the drive axis X1 with respect to the drive scroll 30 and the driven scroll 40. However, the present invention is not limited to this configuration. For example, the electric motor 11 may be arranged in the direction of the drive axis X1 with respect to the drive scroll 30 and the driven scroll 40, and the inverter circuit 12 may be provided on the outer peripheral surface of the housing 60 at the position of the electric motor 11. Further, with respect to the drive scroll 30 and the driven scroll 40, only the electric motor 11 may be arranged in the radial direction of the drive axis X1, and the inverter circuit 12 may be provided on the outer peripheral surface of the housing 60 at a position shifted in the direction of the drive axis X1.

[0085] In the embodiment, the drive spiral 33 and the driven spiral 43 are slightly less than two turns. However, the number of turns of the drive spiral 33 and the driven spiral 43 is not limited to this. For example, the number of turns of the drive spiral 33 and the driven spiral 43 may be increased to increase the number of compression chambers 50. Also, the number of turns of the drive spiral 33 and the driven spiral 43 may be made different. Even in this case, the moment when the two compression chambers 50 are closed on the outermost peripheral side can be set as the above-mentioned confinement time of 0 deg.

[0086] In the embodiment, regarding the variation range FR, the minimum load angle θmin is obtained at the time of confinement, and the maximum load angle θmax is obtained immediately before rotating 360 degrees from the time of confinement. However, depending on the scroll shape, the time when the minimum load angle θmin is obtained may be shifted from the time of confinement, or the time when the maximum load angle θmax is obtained may be shifted from immediately before rotating 360 degrees from the time of confinement.

[0087] In the embodiment, the driven mechanism 20 is composed of a pin 21 and a ring 22, but the present invention is not limited to this configuration. For example, the driven mechanism 20 may be configured by a pin-ring-pin method in which two pins are in sliding contact with the inner peripheral surface of a free ring, a pin-pin method in which the outer peripheral surfaces of two pins are in sliding contact with each other, a method using an Oldham coupling, or the like.

[0088] As described above, the embodiments of the present invention have been described. The technical idea that can be grasped from the above embodiments is described below.

[0089] (Appendix 1) A driving mechanism, a driving scroll, a driven mechanism, a driven scroll, and a cylindrical housing are provided, The driving scroll is provided in the housing and is rotationally driven around a driving axis by the driving mechanism, The driven scroll is provided in the housing and is rotationally driven by the driving scroll and the driven mechanism around a driven axis while being eccentric with respect to the driving scroll, The driving scroll has a driving end plate extending in a direction intersecting the driving axis and a driving spiral body protruding from the driving end plate toward the driven scroll and having a spiral shape, The driven scroll has a driven end plate extending in a direction intersecting the driven axis and a driven spiral body protruding from the driven end plate toward the driving scroll and having a spiral shape, In the double-rotary scroll type compressor in which the driving scroll and the driven scroll form a compression chamber by opposing the driving spiral body and the driven spiral body to each other and change the volume of the compression chamber by the rotational driving and the rotational following, The driving mechanism has an electric motor provided in the housing and an inverter circuit provided on the outer peripheral surface of the housing and driving the electric motor, When assuming a plane orthogonal to the driving axis, The midpoint between the center of the drive-side base circle forming the drive scroll body and the center of the driven-side base circle forming the driven scroll body is defined as the acting point of the compression load generated in the radial direction of the drive axis by the rotation of the drive scroll and the driven scroll, and, When the direction orthogonal to the virtual line connecting the first contact point where the outer surface of the drive scroll and the inner surface of the driven scroll are in contact on the outermost peripheral side and the second contact point where the inner surface of the drive scroll and the outer surface of the driven scroll are in contact on the outermost peripheral side at the moment when the compression chamber formed on the outermost peripheral side is closed is defined as the load direction of the compression load, the inverter circuit is arranged so as to avoid a range extending in the load direction with a width equal to the distance between the first contact point and the second contact point in the circumferential direction of the drive axis. A twin-rotary scroll compressor characterized by this.

[0090] (Appendix 2) A drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a cylindrical housing are provided, the drive scroll is provided in the housing and is rotationally driven around the drive axis by the drive mechanism, the driven scroll is provided in the housing and is rotationally driven by the drive scroll and the driven mechanism around the driven axis while being eccentric with respect to the drive scroll, the drive scroll has a drive end plate extending in a direction intersecting the drive axis and a drive scroll body protruding from the drive end plate toward the driven scroll and having a spiral shape, the driven scroll has a driven end plate extending in a direction intersecting the driven axis and a driven scroll body protruding from the driven end plate toward the drive scroll and having a spiral shape, In a twin-rotary scroll compressor in which the drive scroll and the driven scroll form a compression chamber by facing each other, and the volume of the compression chamber is changed by the rotational drive and the rotational following, The drive mechanism includes an electric motor provided in the housing and an inverter circuit provided on the outer peripheral surface of the housing for driving the electric motor. When assuming a plane orthogonal to the drive axis, when defining a second virtual line connecting the center of the drive-side basic circle forming the drive scroll body and the center of the driven-side basic circle forming the driven scroll body, the inverter circuit is disposed on the second virtual line in the circumferential direction of the drive axis in both rotary scroll compressors.

[0091] (Appendix 3) A drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a cylindrical housing are provided, the drive scroll is provided in the housing and is rotationally driven around the drive axis by the drive mechanism, the driven scroll is provided in the housing and is rotationally driven around the driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll, the drive scroll has a drive end plate extending in a direction intersecting the drive axis and a drive scroll body protruding from the drive end plate toward the driven scroll and having a spiral shape, the driven scroll has a driven end plate extending in a direction intersecting the driven axis and a driven scroll body protruding from the driven end plate toward the drive scroll and having a spiral shape, in both rotary scroll compressors in which the drive scroll and the driven scroll form a compression chamber by opposing the drive scroll body and the driven scroll body to each other and change the volume of the compression chamber by the rotational drive and the rotational following drive, the drive mechanism includes an electric motor provided in the housing and an inverter circuit provided on the outer peripheral surface of the housing for driving the electric motor. When assuming a plane orthogonal to the drive axis, When the compression chamber formed on the outermost peripheral side is closed, a third virtual line connecting a first contact point where the outer surface of the driving scroll and the inner surface of the driven scroll are in contact on the outermost peripheral side, and a second contact point where the inner surface of the driving scroll and the outer surface of the driven scroll are in contact on the outermost peripheral side is defined. The inverter circuit is a twin-rotary scroll compressor arranged on the third virtual line in the circumferential direction of the drive axis.

[0092] (Appendix 4) The twin-rotary scroll compressor according to Appendix 2 or Appendix 3, wherein the center of the inverter circuit is located on the second virtual line or the third virtual line in the circumferential direction of the drive axis.

Industrial Applicability

[0093] The present invention can be used, for example, in an air conditioner for a vehicle.

Explanation of Reference Numerals

[0094] 1... Twin-rotary scroll compressor 10... Driving mechanism 11... Electric motor 12... Inverter circuit 13... Stator 14... Rotor 20... Driven mechanism 30... Driving scroll 31... Driving end plate 33... Driving scroll body 34... Driving side base circle 40... Driven scroll 41... Driven end plate 43... Driven scroll body 44... Driven side base circle 50... Compression chamber 60... Housing X1... Drive axis X2... Driven axis MP... Midpoint P1... First contact point P2... Second contact point VL... Virtual line LD... Load direction FR... Variation range

Claims

1. A drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a cylindrical housing are provided, The drive scroll is provided in the housing and is rotationally driven around a drive axis by the drive mechanism, The driven scroll is provided in the housing and is rotationally driven by the drive scroll and the driven mechanism around a driven axis while being eccentric with respect to the drive scroll, The drive scroll has a drive end plate extending in a direction intersecting the drive axis, and a drive scroll body protruding from the drive end plate toward the driven scroll and having a spiral shape, The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll body protruding from the driven end plate toward the drive scroll and having a spiral shape, In the double-rotary scroll type compressor in which the drive scroll and the driven scroll form a compression chamber by facing each other with the drive scroll body and the driven scroll body, and change the volume of the compression chamber by the rotational drive and the rotational following, The drive mechanism has an electric motor provided in the housing and an inverter circuit provided on an outer peripheral surface of the housing for driving the electric motor, When assuming a plane orthogonal to the drive axis, The midpoint between the center of the drive-side basic circle forming the drive scroll body and the center of the driven-side basic circle forming the driven scroll body is defined as the action point of the compression load generated in the radial direction of the drive axis by the rotation of the drive scroll and the driven scroll, The direction orthogonal to the virtual line connecting the first contact point where the outer surface of the drive scroll body and the inner surface of the driven scroll body are in contact on the outermost peripheral side and the second contact point where the inner surface of the drive scroll body and the outer surface of the driven scroll body are in contact on the outermost peripheral side is defined as the load direction of the compression load, and When defining the range in which the load direction fluctuates while the drive scroll and the driven scroll make one rotation as the fluctuation range, The inverter circuit is arranged to avoid the fluctuation range in the circumferential direction of the drive axis. A double-rotary scroll type compressor characterized by this.

2. The electric motor has a stator fixed to the housing and a rotor arranged in the stator and rotatable together with the drive scroll, The drive scroll is built in the rotor, The inverter circuit is disposed on the outer periphery of the stator. The double-rotary scroll compressor according to claim 1.

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