Rolling piston type electric compressor

Abstract

To provide a rolling piston type electric compressor having high reliability.SOLUTION: A compression mechanism includes a rotation shaft and a plate member. The plate member has a bearing part through which the rotation shaft is inserted in a first direction. In an outer peripheral surface of the rotation shaft, a first recess 116 and a second recess 117 are provided. When the rotation shaft is at a first rotation angle A1, lubrication oil is supplied to the first recess 116, and can be stored in the first recess 116. When the rotation shaft is at a second rotation angle A2, the lubrication oil stored in the first recess 116 can be supplied to a first bearing groove 148. When the rotation shaft is at a third rotation angle A3, the lubrication oil is supplied to a second recess 117, and can be stored in the second recess 117. When the rotation shaft is at a fourth rotation angle A4, the lubrication oil stored in the second recess 117 can be supplied to a second bearing groove 149.SELECTED DRAWING: Figure 19

Description

[Technical Field]

[0001] The present disclosure relates to a rolling piston type electric compressor. [Background technology]

[0002] Japanese Patent Application Laid-Open Publication No. 2017-53277 (Patent Document 1) is a prior art document that discloses a rotary compressor. The rotary compressor described in Patent Document 1 includes a compression mechanism and a shaft. Lubricating oil is supplied to the compression mechanism through a vertical oil feed hole and a horizontal oil feed hole provided in the shaft. The lubricating oil lubricates the gaps between the components of the compression mechanism. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2017-53277 Summary of the Invention [Problem to be solved by the invention]

[0004] In the rotary compressor described in Patent Document 1, lubricating oil is continuously supplied to the gaps between the components. In this case, reducing the cross-sectional area of ​​a portion of the flow path to prevent excessive supply of lubricating oil can cause clogging of the lubricating oil, or fluctuations in the supply pressure of the lubricating oil can cause fluctuations in the amount of lubricating oil supplied. This can lead to instability in the amount of lubricating oil supplied, which can reduce the reliability of the compressor.

[0005] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a rolling piston type electric compressor that is highly reliable. [Means for solving the problem]

[0006] A rolling piston type electric compressor according to the present disclosure includes a case, an electric motor, a compression mechanism, and an oil separator. The case has a suction path and a discharge path. The electric motor is housed in the case. The compression mechanism is housed in the case and is arranged horizontally alongside the electric motor. The compression mechanism draws in refrigerant that has been drawn in through the suction path and passed through the electric motor, compresses it, and discharges it to the discharge path. The oil separator is provided on the discharge path and separates lubricating oil mixed in the refrigerant from the refrigerant. The compression mechanism includes a rotating shaft, a piston, vanes, a cylinder, and a plate member. The rotating shaft is driven by the electric motor and has an axis extending in a first direction. The piston is rotatable eccentrically with respect to the axis as the rotating shaft rotates. The vane abuts against the piston in a direction intersecting the first direction. The cylinder houses the piston and vane, and a compression chamber that compresses the refrigerant is formed between the piston and the vane. The plate member abuts against the cylinder in the first direction and contacts the compression chamber. An oil reservoir capable of storing lubricating oil is provided inside the case. A first supply path is formed branching from the discharge path and capable of supplying lubricating oil separated from the oil separator to the oil reservoir. A second supply path is formed and capable of supplying lubricating oil from the oil reservoir to a sliding position of the compression mechanism. The plate member has a bearing portion through which the rotating shaft is inserted in the first direction. The bearing portion is provided with a first bearing groove and a second bearing groove. The first bearing groove continues in the first direction from the center of the bearing portion to the end on the compression chamber side. The second bearing groove continues in the first direction from the center to the end on the opposite side from the compression chamber. The first bearing groove and the second bearing groove are arranged at a distance from each other in the first direction. A first recess and a second recess are provided on the outer peripheral surface of the rotating shaft. The first recess and the second recess are arranged at a distance from each other in the circumferential direction of the rotating shaft and are recessed toward the axis center. When the rotating shaft is at a first rotation angle, lubricating oil is supplied from the second supply path to the first recess and can be stored in the first recess. When the rotating shaft is at a second rotation angle, the lubricating oil stored in the first recess can be supplied to the first bearing groove. When the rotating shaft is at a third rotation angle, lubricating oil is supplied from the second supply path to the second recess and can be stored in the second recess.When the rotation shaft is at the fourth rotation angle, the lubricating oil stored in the second recess can be supplied to the second bearing groove.

[0007] In one embodiment of the present disclosure, the first bearing groove and the vane at the end of the bearing portion on the compression chamber side are arranged at approximately the same position in the circumferential direction of the rotary shaft.

[0008] In one embodiment of the present disclosure, the first recess and the second recess are arranged on the outer circumferential surface of the rotating shaft at positions facing each other with the axis as the center. [Effects of the Invention]

[0009] According to the present disclosure, it is possible to provide a highly reliable rolling piston type electric compressor. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is a top view illustrating a configuration of a rolling piston type electric compressor according to an embodiment of the present disclosure. FIG. [Figure 2] 2 is a front view of the rolling piston type electric compressor of FIG. 1, as viewed from the direction of the arrow II. FIG. [Figure 3] 3 is a partial cross-sectional view of the rolling piston type electric compressor of FIG. 1, seen from the direction of the arrows along line III-III. [Figure 4] 4 is a cross-sectional view of the rolling piston type electric compressor of FIG. 3, seen from the direction of the arrows along line IV-IV. [Figure 5] FIG. 1 is an exploded perspective view showing a path through which a refrigerant is compressed in a rolling piston type electric compressor according to an embodiment of the present disclosure. [Figure 6] 6 is a cross-sectional view of the rolling piston type electric compressor of FIG. 1, seen from the direction of the arrows along line VI-VI. [Figure 7] FIG. 2 is an exploded perspective view showing a lubricating oil supply path in the rolling piston type electric compressor according to the embodiment of the present disclosure. [Figure 8]8 is a partial cross-sectional view of the rolling piston type electric compressor of FIG. 1, as viewed from the direction of the arrows along the line VIII-VIII. [Figure 9] 9 is a cross-sectional view of the rolling piston type electric compressor of FIG. 3, seen from the direction of the arrows along line IX-IX. [Figure 10] 4 is a cross-sectional view of the rolling piston type electric compressor of FIG. 3, seen from the direction of the arrow XX. [Figure 11] 1. FIG. 1 is a partial cross-sectional view of the rolling piston type electric compressor of FIG. 1, taken along the line XI-XI. [Figure 12] 12 is an enlarged cross-sectional view of a portion XII in FIG. 11 showing the configuration of a lubricating oil supply path. FIG. [Figure 13] 1. FIG. 3 is a partial cross-sectional view of the rolling piston type electric compressor of FIG. 1, taken along the line XIII-XIII. [Figure 14] 14 is an enlarged cross-sectional view of a portion XIV in FIG. 13, showing the configuration of a lubricating oil supply path. FIG. [Figure 15] FIG. 4 is a schematic diagram showing the angular position of a bearing portion in a compression mechanism. [Figure 16] 16 is a partial cross-sectional view of the configuration of the compression mechanism of FIG. 15, as viewed from the direction of the arrow XVI. [Figure 17] 17 is a partial cross-sectional view of the configuration of the compression mechanism of FIG. 15, as viewed from the direction of the arrow XVII. [Figure 18] FIG. 2 is a development view showing the configuration of the lubricating oil supply path and the bearing groove by expanding the bearing portion in the circumferential direction of the rotating shaft. [Figure 19] FIG. 2 is a development view showing the bearing portion in the circumferential direction of the rotating shaft, illustrating the positional relationship between the recess of the rotating shaft and the lubricating oil supply path and bearing groove of the bearing portion for each rotation angle of the rotating shaft. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following description of the embodiments, the same or corresponding parts are denoted by the same reference characters, and description thereof may not be repeated.

[0012] In the drawings, the direction perpendicular to the direction in which the axis of the rotating shaft extends and the vertical direction is designated as the X direction, the vertical direction is designated as the Y direction, and the direction in which the axis of the rotating shaft extends is designated as the Z direction. Also, in the drawings, some parts, such as the connection structure between components, are omitted. Furthermore, for the sake of convenience, cross-sectional portions are not hatched in Figures 4 and 10.

[0013] First, the overall configuration of a rolling piston type electric compressor will be described. Fig. 1 is a top view showing the configuration of a rolling piston type electric compressor according to an embodiment of the present disclosure. Fig. 2 is a front view of the configuration of the rolling piston type electric compressor of Fig. 1, as seen from the direction of the arrows along line II. Fig. 3 is a partial cross-sectional view of the configuration of the rolling piston type electric compressor of Fig. 1, as seen from the direction of the arrows along line III-III.

[0014] As shown in Figures 1 to 3, rolling piston type electric compressor 1 can be mounted on, for example, an automobile. Rolling piston type electric compressor 1 is used, for example, in automobile air conditioning. Rolling piston type electric compressor 1 in this embodiment is driven using, for example, carbon dioxide (CO2) as a refrigerant.

[0015] The rolling piston type electric compressor 1 in this embodiment includes a case 10, a compression mechanism 20, an electric motor 30, and an oil separator 40.

[0016] The case 10 forms the outer shape of the rolling piston type electric compressor 1. The material of the case 10 is, for example, aluminum or an aluminum alloy.

[0017] The case 10 includes a first case 11 and a second case 12. The first case 11 and the second case 12 are aligned in a first direction (Z direction).

[0018] The first case 11 is provided with an intake port 13 through which a refrigerant (not shown) is drawn in. The intake port 13 penetrates an inner peripheral surface 15. The second case 12 is provided with a discharge port 14 through which the refrigerant is discharged. The discharge port 14 is located in a thick portion at the end of the case 10 in the first direction (Z direction).

[0019] Case 10 is provided with suction path 2 and discharge path 3. Refrigerant is drawn into case 10 through suction path 2. Suction port 13 constitutes part of suction path 2. Refrigerant is discharged to the outside of case 10 through discharge path 3. Discharge port 14 constitutes part of discharge path 3.

[0020] The compression mechanism 20 is housed in the case 10. In the present embodiment, the compression mechanism 20 is mainly disposed inside the second case 12. The compression mechanism 20 is arranged horizontally alongside the electric motor 30. The compression mechanism 20 is capable of drawing in and compressing the refrigerant that has been drawn in through the suction path 2 and passed through the electric motor 30, and discharging the compressed refrigerant from the discharge path 3. The members constituting the compression mechanism 20 are made of a material such as an aluminum alloy or an iron alloy, for example.

[0021] The compression mechanism 20 includes a rotary shaft 21, a piston, a vane, a cylinder, and a plate member 25. The piston is rotatable eccentrically with respect to an axis C as the rotary shaft 21 rotates. The vane abuts against the piston in a direction intersecting the first direction. The cylinder houses the piston and the vane, and a compression chamber that compresses the refrigerant is formed between the piston and the vane. The plate member 25 abuts against the cylinder in the first direction and is in contact with the compression chamber.

[0022] The piston in this embodiment includes a first piston and a second piston spaced apart from each other in a first direction. The vane in this embodiment includes a first vane and a second vane. The cylinder in this embodiment includes a first cylinder and a second cylinder. The compression chamber includes a first compression chamber and a second compression chamber.

[0023] The electric motor 30 is housed in a case 10. In this embodiment, the electric motor 30 is housed in a first case 11.

[0024] The electric motor 30 includes a stator 31 and a rotor 32. The stator 31 is formed by stacking a plurality of electromagnetic steel plates (not shown) in the Z direction. The stator 31 is fixed to the inner circumferential surface 15 of the first case 11. The rotor 32 is formed by stacking a plurality of electromagnetic steel plates (not shown) in the Z direction. The rotor 32 is disposed on the inner circumferential side of the stator 31 with a gap therebetween.

[0025] The oil separator 40 is provided on the discharge path 3. The oil separator 40 is provided on the discharge path 3 adjacent to the discharge port 14. The refrigerant contains lubricating oil (not shown) to maintain the sliding properties of the compression mechanism 20. The oil separator 40 separates the lubricating oil mixed in the refrigerant from the refrigerant.

[0026] Next, a detailed description will be given of the compression mechanism 20. Fig. 4 is a cross-sectional view of the rolling piston type electric compressor of Fig. 3, as viewed from the direction of the arrows along line IV-IV.

[0027] 3 and 4, the compression mechanism 20 includes a rotary shaft 21, a first compression section 22, a second compression section 23, and a plate member 25. In the present embodiment, the plate member 25 has a front side plate 140, a middle side plate 160, and a rear side plate 190.

[0028] The rotating shaft 21 is driven by an electric motor 30. The rotating shaft 21 has an axis C extending in a first direction (Z direction). Since the first direction (Z direction) is horizontal, the rolling piston type electric compressor 1 in this embodiment is a horizontally placed compressor whose horizontal width is greater than its vertical height. Note that the axis C of the rotating shaft 21 is not limited to a configuration extending horizontally.

[0029] The rotating shaft 21 has a fixed portion 110 , a first shaft portion 111 , a second shaft portion 112 , a third shaft portion 113 , a first eccentric shaft portion 114 , and a second eccentric shaft portion 115 .

[0030] The fixed portion 110 is fixed to the inner peripheral surface 33 of the rotor 32. As a result, when the electric motor 30 is driven, the rotation of the rotor 32 causes the rotation shaft 21 to rotate about the axis C.

[0031] The first shaft 111 is inserted through the front side plate 140. The second shaft 112 is inserted through the rear side plate 190. The third shaft 113 is inserted through the middle side plate 160.

[0032] Each of the first eccentric shaft portion 114 and the second eccentric shaft portion 115 is eccentric in a direction perpendicular to the first direction (Z direction) with respect to the axis C of the rotating shaft 21. The first eccentric shaft portion 114 is inserted through the first compression portion 22. The second eccentric shaft portion 115 is inserted through the second compression portion 23.

[0033] As shown in FIG. 4, the first compression section 22 has a first piston 120 , a first vane 122 , and a first cylinder 125 .

[0034] The first piston 120 is rotatable in an eccentric state with respect to the axis C in accordance with the rotation of the rotary shaft 21. The first piston 120 is fitted to the first eccentric shaft portion 114 in a state in which it can rotate around its own axis in the circumferential direction in the first direction (Z direction).

[0035] The first vane 122 abuts against the first piston 120 in a direction (Y direction) intersecting the first direction. A tip end 123 of the first vane 122 abuts against the outer circumferential surface 121 of the first piston 120 in the direction (Y direction) intersecting the first direction. The first vane 122 is movable in the Y direction while abutting against the first piston 120 in accordance with the rotation of the first piston 120.

[0036] The first cylinder 125 accommodates the first piston 120 and the first vane 122. The first piston 120, which rotates eccentrically, slides on an inner circumferential surface 126 of the first cylinder 125. A vane groove 127 is provided so as to be continuous with the inner circumferential surface 126. The vane groove 127 extends in the Y direction. The first vane 122 is accommodated in the vane groove 127. The side surface 124 of the first vane 122 is provided so as to slide in the vane groove 127.

[0037] A through-hole 128 is provided in the outer peripheral surface of the first cylinder 125. The through-hole 128 penetrates to the first vane 122 in the vertical direction (Y direction) perpendicular to the first direction. An elastic member 129 is inserted into the through-hole 128. The elastic member 129 biases the first vane 122 toward the first piston 120. A plate-shaped member 130 and a fastening member 131 are provided on the outer peripheral surface of the first cylinder 125. The plate-shaped member 130 is disposed with a gap from the through-hole 128. The plate-shaped member 130 supports the elastic member 129. The fastening member 131 fixes the plate-shaped member 130 to the first cylinder 125.

[0038] In the first cylinder 125, a first compression chamber 26 is formed between the first piston 120 and the first vane 122, in which the refrigerant is compressed.

[0039] Refrigerant is introduced into first compression chamber 26 through first suction port 143, which will be described later. As first piston 120 rotates in an eccentric state, the space in first compression chamber 26 gradually narrows, compressing the refrigerant. The compressed refrigerant is discharged from first discharge port 164, which will be described later.

[0040] As shown in FIG. 3, the second compression section 23 includes a second piston 150 , a second vane 151 , and a second cylinder 152 .

[0041] The second piston 150 is disposed at a distance from the first piston 120 on the side opposite to the side on which the front side plate 140 is disposed in the first direction (Z direction). The second piston 150 is rotatable in an eccentric state with respect to the axis C in conjunction with the rotation of the rotary shaft 21. The second piston 150 is fitted to the second eccentric shaft portion 115 in a state in which it can rotate around its own axis in the circumferential direction in the first direction (Z direction).

[0042] The second vane 151 abuts against the second piston 150 in a direction (Y direction) intersecting the first direction. The second cylinder 152 accommodates the second piston 150 and the second vane 151 in a direction intersecting the first direction.

[0043] In second compression section 23, second vane 151, second cylinder 152, and second piston 150 form second compression chamber 27 for compressing refrigerant.

[0044] Refrigerant is introduced into second compression chamber 27 through second suction port 180, which will be described later. As second piston 150 rotates in an eccentric state, the space in second compression chamber 27 gradually narrows, compressing the refrigerant. The compressed refrigerant is discharged through second discharge port 192, which will be described later.

[0045] The front side plate 140 abuts against the first cylinder 125 in the first direction (Z direction). In this embodiment, the front side plate 140 abuts against the first cylinder 125 from the side where the electric motor 30 is disposed. The front side plate 140 abuts against the first compression chamber 26 in the first direction (Z direction).

[0046] The front side plate 140 has an outer periphery 141 and a first bearing portion 142. The outer periphery 141 is a portion that is sandwiched between the first case 11 and the second case 12 in the first direction (Z direction). The front side plate 140 is connected to the first case 11 and the second case 12 at the outer periphery 141 by bolts or the like. The first bearing portion 142 is formed by a through hole that penetrates the front side plate 140 in the first direction (Z direction). The first bearing portion 142 supports the first shaft portion 111. The first shaft portion 111 slides relative to the first bearing portion 142 as the rotating shaft 21 rotates.

[0047] An oil reservoir 28 is disposed in the front side plate 140. The oil reservoir 28 is capable of storing lubricating oil. Details of the oil reservoir 28 will be described later.

[0048] The middle side plate 160 is disposed between the first cylinder 125 and the second cylinder 152 in the first direction (Z direction), and separates the first compression chamber 26 and the second compression chamber 27 from each other.

[0049] The middle side plate 160 has a first member 161 and a second member 178 .

[0050] The first member 161 has a disk shape extending in a direction intersecting the first direction. The first member 161 abuts against the first cylinder 125 in the first direction (Z direction). The third shaft portion 113 of the rotating shaft 21 is inserted into an inner circumferential surface 162 of the first member 161. The third shaft portion 113 slides relative to the inner circumferential surface 162 as the rotating shaft 21 rotates.

[0051] The second member 178 has a disk shape extending in a direction intersecting the first direction. The second member 178 abuts against the second cylinder 152 and the first member 161 in the first direction (Z direction). The third shaft portion 113 of the rotating shaft 21 is inserted into an inner circumferential surface 179 of the second member 178. The third shaft portion 113 slides relative to the inner circumferential surface 179 as the rotating shaft 21 rotates.

[0052] The rear side plate 190 abuts against the second cylinder 152 from the side opposite to the side on which the front side plate 140 is disposed in the first direction (Z direction). ... compression chamber 27 in the first direction (Z direction). The rear side plate 190 is disposed opposite the front side plate 140 in the first direction (Z direction), with the first compression chamber 26 and the second compression chamber 27 sandwiched therebetween.

[0053] The rear side plate 190 has a second bearing portion 191. The second bearing portion 191 is configured as a through-hole that penetrates the rear side plate 190 in the first direction (Z direction). The second bearing portion 191 supports the second shaft portion 112. The second shaft portion 112 slides relative to the second bearing portion 191 as the rotary shaft 21 rotates.

[0054] Next, a description will be given of the refrigerant path in the rolling piston electric compressor 1. Fig. 5 is an exploded perspective view showing the path through which the refrigerant is compressed in a rolling piston electric compressor according to one embodiment of the present disclosure. For the sake of convenience, Fig. 5 shows only the components necessary for the explanation, and omits the illustration of other components (such as through holes for supplying lubricating oil).

[0055] As shown in FIG. 5, the suction path 2 and the discharge path 3 through which the refrigerant passes are provided to pass through the front side plate 140, the first cylinder 125, the middle side plate 160, the second cylinder 152, and the rear side plate 190.

[0056] A first intake port 143 is provided in the front side plate 140. The first intake port 143 penetrates the front side plate 140 in a first direction (Z direction). The first intake port 143 has an elongated hole shape in a direction perpendicular to the first direction (Z direction).

[0057] The first cylinder 125 is provided with a communication hole 132. The communication hole 132 passes through the first cylinder 125 in the first direction (Z direction).

[0058] A communication hole 170 is provided in the first member 161 of the middle side plate 160. The communication hole 170 penetrates the first member 161 in the first direction (Z direction).

[0059] The first member 161 is provided with a first discharge port 164. The first discharge port 164 penetrates the first member 161 in the first direction (Z direction). A first groove 163 is provided in the end face of the first member 161 on the side that abuts against the second member 178. The first groove 163 is recessed in the first direction (Z direction). The first discharge port 164 is connected to the bottom of the first groove 163. The first discharge port 164 communicates with the first compression chamber 26. The first discharge port 164 discharges the refrigerant compressed between the first member 161 and the second member 178. In this embodiment, the refrigerant compressed is discharged into the internal space of the first groove 163.

[0060] A discharge valve 165 is provided in the first discharge port 164. The first discharge port 164 is opened and closed by the discharge valve 165. A gap 169 communicating with the first groove 163 is provided in an outer peripheral surface 168 of the first member 161. The refrigerant discharged from the first discharge port 164 can be discharged from the gap 169 in a direction perpendicular to the first direction (Z direction).

[0061] A second intake port 180 is provided in the second member 178 of the middle side plate 160. The second intake port 180 penetrates the second member 178 in the first direction (Z direction).

[0062] A second discharge port 192 is provided in the rear side plate 190. The second discharge port 192 penetrates the rear side plate 190 in the first direction (Z direction). The second discharge port 192 is opened and closed by a discharge valve 193.

[0063] The suction path 2 is composed of a path through which the refrigerant flows from the suction port 13 of the case 10 to the first suction port 143, and a path through which the refrigerant flows from the first suction port 143 in the compression mechanism 20 to the first compression chamber 26 and the second compression chamber 27.

[0064] The discharge path 3 is composed of a path through which the refrigerant flows from the first compression chamber 26 in the compression mechanism 20 to the first discharge port 164, a path through which the refrigerant flows from the second compression chamber 27 to the second discharge port 192, and a path through which the refrigerant flows from the first discharge port 164 and the second discharge port 192 to the oil separator 40.

[0065] The suction path 2 includes a first suction path 4 and a second suction path 5. The discharge path 3 includes a first discharge path 6 and a second discharge path .

[0066] The first suction path 4 is a path that introduces the refrigerant into the first compression chamber 26. The first suction path 4 introduces the refrigerant that has flowed into the inside of the case 10 from the suction port 13 into the first compression chamber 26 via the first suction port 143.

[0067] The first discharge path 6 is a path that discharges the refrigerant compressed in the first compression chamber 26. The first discharge path 6 passes through a first discharge port 164 and a gap 169 and is connected to a first communication hole 16 of the case 10, which will be described later. The first discharge path 6 connects the first compression chamber 26 and the oil separator 40.

[0068] The second suction path 5 is a path that introduces the refrigerant into the second compression chamber 27. The second suction path 5 branches off from the first suction path 4 at the first suction port 143. The second suction path 5 introduces the refrigerant into the second compression chamber 27 via the first suction port 143, the communication holes 132 and 170, and the second suction port 180.

[0069] The second discharge path 7 is a path that discharges the refrigerant compressed in the second compression chamber 27. The second discharge path 7 passes through the second discharge port 192 and is connected to the first communication hole 16 of the case 10. The second discharge path 7 connects the second compression chamber 27 and the oil separator 40.

[0070] The above-described suction path 2 and discharge path 3 create a pressure difference in the refrigerant inside the case 10. As shown in Fig. 3, a suction pressure region 2A is defined inside the case 10, where the suctioned refrigerant exists. Also, a discharge pressure region 3A is defined in part of the inside of the case 10, where the refrigerant discharged from the compression chamber between the inner circumferential surface 15 of the case 10 and the outer circumferential surface of the compression mechanism 20 exists.

[0071] The suction pressure region 2A is an internal space of the case 10 that includes a path through which the refrigerant flows from the suction port 13 of the case 10 to the first suction port 143 of the front side plate 140. The suction pressure region 2A communicates with the suction path 2.

[0072] The discharge pressure region 3A is a space between the inner circumferential surface 15 of the case 10 and the outer circumferential surface of the compression mechanism 20. The discharge pressure region 3A includes a part of the path through which the refrigerant flows from the first discharge port 164 and the second discharge port 192 to the oil separator 40. The discharge pressure region 3A is in communication with the discharge path 3.

[0073] The front side plate 140 divides the suction pressure region 2A and the discharge pressure region 3A so that they are aligned in the first direction (Z direction). The front side plate 140 is configured to withstand the pressure of the discharge pressure region 3A. Therefore, the front side plate 140 is thicker than the rear side plate 190 in the first direction (Z direction).

[0074] Specifically, the front side plate 140 has a thickness T1 in a portion other than the outer circumferential portion 141 and the first bearing portion 142. The thickness T1 is the thickness between one end face and the other end face of the front side plate 140 at a position aligned with the cylinder in the first direction (Z direction). The rear side plate 190 has a thickness T2 in a portion other than the second bearing portion 191. The thickness T2 is the minimum thickness of the rear side plate 190. The thickness T1 of the front side plate 140 is greater than the thickness T2 of the rear side plate 190.

[0075] FIG. 6 is a cross-sectional view of the rolling piston type electric compressor of FIG. 1, seen from the direction of the arrows along line VI-VI.

[0076] As shown in Fig. 6, a first communication hole 16 and an inner diameter portion 19 are provided in a thick portion of the case 10. The first communication hole 16 connects the discharge pressure region 3A with the inner diameter portion 19. The inner diameter portion 19 extends along the Y direction. The inner diameter portion 19 constitutes a part of the discharge path 3.

[0077] The oil separator 40 is in communication with the discharge pressure region 3A via the first communication hole 16 and the inner diameter portion 19. The oil separator 40 has a cylindrical portion 41. The cylindrical portion 41 is disposed inside the inner diameter portion 19. The cylindrical portion 41 is disposed opposite the direction in which the refrigerant is discharged from the first communication hole 16.

[0078] When the refrigerant mixed with lubricating oil is discharged onto the outer peripheral surface of cylindrical portion 41, the momentum of the discharge causes the refrigerant mixed with lubricating oil to circulate between the outer peripheral surface of cylindrical portion 41 and inner diameter portion 19, and the lubricating oil is centrifuged from the refrigerant. The refrigerant is discharged from discharge port 14 to the outside of rolling piston type electric compressor 1. Meanwhile, the lubricating oil moves downward in the Y direction (direction DR1 in FIG. 6) along inner diameter portion 19.

[0079] Next, the lubricating oil supply path in the rolling piston electric compressor 1 will be described. Fig. 7 is an exploded perspective view showing the lubricating oil supply path in a rolling piston electric compressor according to one embodiment of the present disclosure. Fig. 8 is a partial cross-sectional view of the configuration of the rolling piston electric compressor in Fig. 1, as viewed from the direction of the arrows VIII-VIII. For convenience, Fig. 7 shows only the configuration necessary for explanation, and omits the depiction of other configurations (such as the suction path or the discharge path).

[0080] As shown in FIGS. 7 and 8, the lubricating oil supply path 8 through which the lubricating oil separated from the oil separator 40 flows is formed to pass through the case 10 and the compression mechanism 20.

[0081] The lubricating oil supply path 8 includes a first supply path 50 and a second supply path 60. The first supply path 50 branches off from the discharge path 3. The first supply path 50 can supply the lubricating oil separated from the oil separator 40 to the oil reservoir 28. The second supply path 60 can supply the lubricating oil from the oil reservoir 28 to a sliding position of the compression mechanism 20.

[0082] 8, a second communication hole 17 communicating with the inner diameter portion 19 is provided in the case 10. The second communication hole 17 extends in the first direction (Z direction).

[0083] 7 and 8, a first oil supply hole 196 is provided in rear side plate 190. First oil supply hole 196 penetrates rear side plate 190 in a first direction (Z direction). Similar to first oil supply hole 196, first oil supply holes 153, 181, 171, 133, and 144 are provided in second cylinder 152, second member 178, first member 161, first cylinder 125, and front side plate 140.

[0084] The first supply path 50 is made up of the second communication hole 17 and the first oil supply holes 196, 153, 181, 171, 133, and 144. The first supply path 50 supplies the lubricating oil separated by the oil separator 40 to the oil reservoir 28 (in the direction DR2 in FIG. 8).

[0085] The first supply path 50 directly connects the second communication hole 17 of the case 10 with the first oil supply holes 196, 153, 181, 171, 133, and 144 of the compression mechanism 20. There is no need to provide a dedicated part for supplying lubricating oil in the path that supplies lubricating oil to the oil reservoir 28. This makes it possible to configure a less expensive rolling piston type electric compressor 1 compared to a case in which a dedicated part for supplying lubricating oil is separately provided.

[0086] FIG. 9 is a cross-sectional view of the rolling piston type electric compressor of FIG. 3 as viewed from the direction of the arrows along line IX-IX.

[0087] 3 and 9, an oil reservoir 28 capable of storing lubricating oil is provided inside case 10. In the present embodiment, a recessed portion is provided in front side plate 140 of plate member 25, the interior of which serves as oil reservoir 28 capable of storing lubricating oil. Oil reservoir 28 is the interior of recessed portion 28A provided in front side plate 140.

[0088] Oil reservoir 28 is formed by recessing recess 28A from the suction pressure region 2A side in the first direction (Z direction) of front side plate 140. Recess 28A is sealed from the suction pressure region 2A side by lid 29 (see FIG. 3). In this way, oil reservoir 28 is formed in front side plate 140.

[0089] Oil reservoir chamber 28 is formed in an arc shape surrounding rotating shaft 21 when viewed from the first direction (Z direction). Lubricating oil supplied to oil reservoir chamber 28 from first oil supply hole 144 is stored in order from the bottom in the Y direction. Note that oil reservoir chamber 28 is not limited to an arc shape. The size and shape of oil reservoir chamber 28 are set within a range that can store the amount of lubricating oil to be supplied to sliding parts of compression mechanism 20.

[0090] FIG. 10 is a cross-sectional view of the rolling piston type electric compressor of FIG. 3 as viewed from the direction of the arrow XX.

[0091] 7 and 10, the front side plate 140 is provided with communication holes 145 and 146. The communication holes 145 and 146 communicate with the oil reservoir chamber .

[0092] A first throttling portion 145A and a second throttling portion 146A are provided in the second supply path 60. In the present embodiment, the first throttling portion 145A and the second throttling portion 146A are provided in the front side plate 140. The first throttling portion 145A and the second throttling portion 146A communicate with the communication holes 145, 146. In the present embodiment, the first throttling portion 145A and the second throttling portion 146A have a slit shape.

[0093] Lubricating oil is supplied from oil reservoir chamber 28 to sliding portions of compression mechanism 20 via communication holes 145, 146, first throttle portion 145A, and second throttle portion 146A.

[0094] Fig. 11 is a partial cross-sectional view of the rolling piston type electric compressor of Fig. 1, as seen from the direction of the arrows along line XI-XI. Fig. 12 is a cross-sectional view of an enlarged portion XII in Fig. 11, showing the configuration of a lubricating oil supply path.

[0095] 7, 11, and 12, a first path 147 is provided in the front side plate 140. The first path 147 constitutes a part of the second supply path 60. The first path 147 connects the first throttle portion 145A and the first bearing portion 142.

[0096] The second supply path 60 is configured to be able to supply lubricating oil to a sliding portion between the front side plate 140 and the rotary shaft 21. In the present embodiment, the second supply path 60 is configured to be able to supply lubricating oil to a sliding portion between the first bearing portion 142 and the first shaft portion 111 via the communication hole 145, the first throttle portion 145A, and the first path 147.

[0097] The first throttle section 145A reduces the flow path cross-sectional area of ​​the lubricating oil midway through the second supply path 60. This prevents excessive supply of lubricating oil to the path after the first throttle section 145A in the second supply path 60. The flow path cross-sectional area of ​​the first throttle section 145A can be set appropriately within a range in which clogging of the lubricating oil does not occur.

[0098] Fig. 13 is a partial cross-sectional view of the rolling piston type electric compressor of Fig. 1, as seen from the direction of the arrows along line XIII-XIII. Fig. 14 is a cross-sectional view of an enlarged portion XIV in Fig. 13, showing the configuration of a lubricating oil supply path.

[0099] As shown in Figures 7, 13, and 14, the first cylinder 125 is provided with a second oil supply hole 134. The first member 161 is provided with a second oil supply hole 172. The second member 178 is provided with a second oil supply hole 182. The second cylinder 152 is provided with a second oil supply hole 154. The rear side plate 190 is provided with a second path 197. The second path 197 is connected to the second bearing portion 191.

[0100] Second supply path 60 is configured to be able to supply lubricating oil to a sliding portion between rear side plate 190 and rotating shaft 21. In the present embodiment, the lubricating oil is configured to be able to be supplied to a sliding portion between second bearing 191 and second shaft 112 via communication hole 146, second throttle portion 146A, second oil supply holes 134, 172, 182, 154, and second path 197.

[0101] The second throttle section 146A reduces the cross-sectional area of ​​the lubricating oil flow path in the middle of the second supply path 60. This prevents excessive supply of lubricating oil to the path after the second throttle section 146A in the second supply path 60. The cross-sectional area of ​​the flow path of the second throttle section 146A can be set appropriately within a range in which clogging of the lubricating oil does not occur.

[0102] As shown in FIG. 7, compression mechanism 20 is provided with third oil supply holes 135, 155, 175, 184, a third passage 173, fourth passages 174, 183, and fifth passages 136, 156.

[0103] Lubricating oil is supplied between the first member 161 and the second member 178 and the third shaft portion 113 via the third path 173 of the middle side plate 160 .

[0104] Lubricating oil is supplied between the middle side plate 160 and the end face of the first piston 120 that contacts the middle side plate 160 via a fourth path 174 of the middle side plate 160. Lubricating oil is also supplied between the middle side plate 160 and the end face of the second piston 150 that contacts the middle side plate 160 via a fourth path 183 of the middle side plate 160.

[0105] Lubricating oil can be supplied between the first vane 122 and the vane groove 127 of the first cylinder 125 via a fifth path 136. Lubricating oil can also be supplied between the second vane 151 and the vane groove of the second cylinder 152 via a fifth path 156.

[0106] The supply of lubricating oil between the rotating shaft and the bearing will be described in detail below. Fig. 15 is a schematic diagram showing the angular position of the bearing in the compression mechanism. Fig. 16 is a partial cross-sectional view of the configuration of the compression mechanism in Fig. 15, seen from the direction of the arrow XVI. Fig. 17 is a partial cross-sectional view of the configuration of the compression mechanism in Fig. 15, seen from the direction of the arrow XVII. Fig. 18 is an exploded view of the bearing in the circumferential direction of the rotating shaft, showing the configuration of the lubricating oil supply path and bearing groove.

[0107] 15 to 18, plate member 25 has a bearing portion through which rotation shaft 21 is inserted in the first direction (Z direction). In this embodiment, the bearing portion is, for example, first bearing portion 142 of front side plate 140. In addition, second bearing portion 191 of rear side plate 190 is another bearing portion.

[0108] In order to explain the positional relationship between the lubricating oil supply path 8 and the bearing grooves and recesses described below, the angular positions of the bearings are indicated. As shown in Fig. 15, for the first bearing 142, when the compression mechanism 20 is viewed from the front side plate 140 side, the upward direction in the Y direction is defined as 0°, one side in the X direction as 90°, the downward direction in the Y direction as 180°, and the other side in the X direction as 270°. Also, for the second bearing 191, when the compression mechanism 20 is viewed from the rear side plate 190 side, the upward direction in the Y direction is defined as 0°, the other side in the X direction as 90°, the downward direction in the Y direction as 180°, and one side in the X direction as 270°.

[0109] 16 to 18, the first path 147 is disposed at an angular position of approximately 110° in the first bearing portion 142. The first bearing portion 142 is provided with a first bearing groove 148 and a second bearing groove 149.

[0110] The first bearing groove 148 continues from the center C1 of the first bearing portion 142 to the end F1 on the first compression chamber 26 side in the first direction (Z direction).

[0111] The first bearing groove 148 in the central portion C1 is disposed at an angular position of approximately 270°, and the first bearing groove 148 in the end portion F1 is disposed at an angular position of approximately 180°.

[0112] The first bearing groove 148 is inclined with respect to the first direction (Z direction) from the center C1 toward the end F1 of the first bearing part 142. The first bearing groove 148 is formed in a spiral shape.

[0113] The second bearing groove 149 continues from the center portion C1 to an end portion F2 on the opposite side from the first compression chamber 26 in the first direction (Z direction).

[0114] The second bearing groove 149 in the central portion C1 is disposed at an angle of approximately 90°, and the second bearing groove 149 in the end portion F2 is disposed at an angle of approximately 0°.

[0115] The second bearing groove 149 is inclined with respect to the first direction (Z direction) from the center C1 toward the end F2 of the first bearing part 142. The second bearing groove 149 is formed in a spiral shape.

[0116] When lubricating oil flows inside the first bearing groove 148 and the second bearing groove 149, the first bearing groove 148 and the second bearing groove 149 are inclined relative to the first direction (Z direction) as they move from the center C1 to the ends of the first bearing part 142, making it easier for the lubricating oil to flow from the center C1 to the ends due to the pumping action caused by the rotation of the rotating shaft 21.

[0117] The first bearing groove 148 and the second bearing groove 149 have approximately the same size. This makes it easier to supply lubricating oil uniformly over the entire axial direction (Z direction) of the first shaft portion 111 of the rotating shaft 21. Note that the first bearing groove 148 and the second bearing groove 149 may have different sizes.

[0118] The first bearing groove 148 and the first vane 122 at the end F1 of the first bearing portion 142 on the first compression chamber 26 side are arranged at approximately the same position in the circumferential direction of the rotary shaft 21. In the present embodiment, the first bearing groove 148 and the first vane 122 at the end F1 of the first bearing portion 142 on the first compression chamber 26 side are arranged at approximately the same position downward in the Y direction, that is, at an angular position of 180°.

[0119] The second path 197 is disposed at an angular position of approximately 110° in the second bearing portion 191. The second bearing portion 191 is provided with a third bearing groove 198 and a fourth bearing groove 199.

[0120] The third bearing groove 198 is continuous in the first direction (Z direction) from the center portion C2 of the second bearing portion 191 to the end portion F3 on the second compression chamber 27 side.

[0121] The third bearing groove 198 in the central portion C2 is disposed at an angular position of approximately 270°, and the third bearing groove 198 in the end portion F3 is disposed at an angular position of approximately 180°.

[0122] The third bearing groove 198 is inclined with respect to the first direction (Z direction) from the center C2 toward the end F3 of the second bearing portion 191. The third bearing groove 198 is formed in a spiral shape.

[0123] The fourth bearing groove 199 continues from the center portion C2 to an end portion F4 on the opposite side to the second compression chamber 27 in the first direction (Z direction).

[0124] The fourth bearing groove 199 in the central portion C2 is disposed at an angle of approximately 90°, and the fourth bearing groove 199 in the end portion F4 is disposed at an angle of approximately 0°.

[0125] The fourth bearing groove 199 is inclined with respect to the first direction (Z direction) from the center C2 toward the end F4 of the second bearing portion 191. The fourth bearing groove 199 is formed in a spiral shape.

[0126] When lubricating oil flows inside the third bearing groove 198 and the fourth bearing groove 199, the third bearing groove 198 and the fourth bearing groove 199 are inclined with respect to the first direction (Z direction) as they move from the center C2 of the second bearing part 191 toward the ends, so that the pumping action caused by the rotation of the rotating shaft 21 makes it easier for the lubricating oil to flow from the center C2 toward the ends.

[0127] The third bearing groove 198 and the fourth bearing groove 199 have approximately the same size. This makes it easier to supply lubricating oil uniformly over the entire axial direction (Z direction) of the second shaft portion 112 of the rotating shaft 21. Note that the third bearing groove 198 and the fourth bearing groove 199 may have different sizes.

[0128] Third bearing groove 198 and second vane 151 at end F3 of second bearing portion 191 on the second compression chamber 27 side are arranged at approximately the same position in the circumferential direction of rotating shaft 21. In the present embodiment, third bearing groove 198 and second vane 151 at end F3 of second bearing portion 191 on the second compression chamber 27 side are arranged at approximately the same position downward in the Y direction, that is, at an angular position of 180°.

[0129] The first shaft portion 111 of the rotating shaft 21 slides against a first bearing portion 142 formed by the inner circumferential surface of the front side plate 140. The second shaft portion 112 of the rotating shaft 21 slides against a second bearing portion 191 formed by the inner circumferential surface of the rear side plate 190.

[0130] The surface of the rotating shaft 21 is subjected to a surface treatment, such as a DLC (Diamond-Like Carbon) coating or a fluororesin coating.

[0131] A first recess 116 and a second recess 117 are provided on the outer peripheral surface of the first shaft portion 111 of the rotating shaft 21. The first recess 116 and the second recess 117 are each recessed toward the axis C. The first recess 116 and the second recess 117 are arranged at intervals from each other in the circumferential direction of the rotating shaft 21.

[0132] In this embodiment, the first recess 116 and the second recess 117 are arranged on the outer circumferential surface of the rotary shaft 21 at positions facing each other with the axis C as the center.

[0133] The first recess 116 and the second recess 117 have approximately the same size. This makes it easier to supply lubricating oil uniformly over the entire axial direction (Z direction) of the first shaft portion 111 of the rotating shaft 21. Note that the first recess 116 and the second recess 117 may have different sizes.

[0134] A third recess 118 and a fourth recess 119 are provided on the outer circumferential surface of the second shaft portion 112 of the rotating shaft 21. The third recess 118 and the fourth recess 119 are each recessed toward the axis C. The third recess 118 and the fourth recess 119 are arranged at intervals from each other in the circumferential direction of the rotating shaft 21.

[0135] In this embodiment, the third recess 118 and the fourth recess 119 are arranged on the outer circumferential surface of the rotary shaft 21 at positions facing each other with the axis C as the center.

[0136] The third recess 118 and the fourth recess 119 have approximately the same size. This makes it easier to supply lubricating oil uniformly over the entire axial direction (Z direction) of the second shaft portion 112 of the rotating shaft 21. The third recess 118 and the fourth recess 119 may have different sizes.

[0137] FIG. 19 is a development view showing the bearing portion in the circumferential direction of the rotating shaft, illustrating the positional relationship between the recessed portion of the rotating shaft and the lubricating oil supply path and bearing groove of the bearing portion for each rotation angle of the rotating shaft.

[0138] 19, the rotating shaft 21 rotates in the R1 direction. When the first recess 116 is located at the top in the Y direction, the rotation angle of the rotating shaft 21 is set to 0°. The rotating shaft 21 rotates in the R1 direction relative to the angular position of the first bearing portion 142, which is indicated by the vertical axis in the developed view of the first bearing portion 142. As a result, the first recess 116 and the second recess 117 move in the circumferential direction of the rotating shaft 21.

[0139] 19 , when the rotating shaft 21 rotates in the R1 direction and reaches a predetermined rotation angle, the positional relationship between the first path 147, the first bearing groove 148, the second bearing groove 149, the first recess 116, and the second recess 117 changes. As a result, lubricating oil is supplied from the first path 147 to the first bearing groove 148 and the second bearing groove 149.

[0140] Specifically, when the rotary shaft 21 is at a first rotation angle A1, the first path 147 and the first recess 116 are positioned substantially the same. The lubricating oil is supplied to the first recess 116 from the first path 147, which is the second supply path 60. This allows the lubricating oil to be stored in the first recess 116. The first rotation angle A1 is, for example, 270°.

[0141] When the rotating shaft 21 is at the second rotation angle A2, the first recess 116 and the first bearing groove 148 are positioned substantially the same. The lubricating oil stored in the first recess 116 can be supplied to the first bearing groove 148. The second rotation angle A2 is, for example, 90°.

[0142] When the rotary shaft 21 is at the third rotation angle A3, the first path 147 and the second recess 117 are positioned substantially the same. The lubricating oil is supplied to the second recess 117 from the first path 147, which is the second supply path 60. This allows the lubricating oil to be stored in the second recess 117. The third rotation angle A3 is, for example, 70°.

[0143] When the rotating shaft 21 is at the fourth rotation angle A4, the second recess 117 and the second bearing groove 149 are positioned substantially the same. The lubricating oil stored in the second recess 117 can be supplied to the second bearing groove 149. The fourth rotation angle A4 is, for example, 90°. In this embodiment, the second rotation angle A2 and the fourth rotation angle A4 are the same due to the relative positions of the first recess 116 and the second recess 117.

[0144] By repeating each of the above rotation angles, the lubricating oil is supplied from the first path 147 to the first bearing groove 148 and the second bearing groove 149 via the first recess 116 and the second recess 117. The lubricating oil supplied to the first bearing groove 148 and the second bearing groove 149 is supplied between the first bearing portion 142 and the first shaft portion 111.

[0145] Since the lubricating oil is temporarily stored in the first recess 116 and the second recess 117, the lubricating oil is supplied to the first bearing groove 148 and the second bearing groove 149 intermittently.

[0146] The first bearing groove 148 and the second bearing groove 149 are arranged at an interval from each other in the first direction (Z direction). The first bearing groove 148 and the second bearing groove 149 are supplied with lubricating oil only from either the first recess 116 or the second recess 117. As a result, a constant amount of lubricating oil stored in the first recess 116 is intermittently supplied to the first bearing groove 148 from the first recess 116. A constant amount of lubricating oil stored in the second recess 117 is intermittently supplied to the second bearing groove 149 from the second recess 117. This suppresses fluctuations in the amount of lubricating oil supplied to the first bearing groove 148 and the second bearing groove 149.

[0147] 3 and 17, the first bearing portion 142 penetrates the front side plate 140 in the first direction (Z direction). The end F2 of the first bearing portion 142 contacts the suction pressure region 2A. That is, the second bearing groove 149 contacts the suction pressure region 2A. This allows a pressure difference to be generated at the end of the high-pressure lubricating oil supply path 8 branching off from the discharge path 3, making it easier for the lubricating oil to flow through the path.

[0148] Regarding the supply of lubricating oil to the second bearing portion 191, when the rotating shaft 21 is at the fifth rotation angle, the second path 197 and the third recessed portion 118 are positioned substantially the same. The lubricating oil is supplied to the third recessed portion 118 from the second path 197, which is the second supply path 60. This makes it possible to store the lubricating oil in the third recessed portion 118.

[0149] When the rotating shaft 21 is at the sixth rotation angle, the third recess 118 and the third bearing groove 198 are positioned substantially the same. The lubricating oil stored in the third recess 118 can be supplied to the third bearing groove 198.

[0150] When the rotary shaft 21 is at the seventh rotation angle, the second path 197 and the fourth recessed portion 119 are positioned substantially the same. Lubricating oil is supplied from the second path 197, which is the second supply path 60, to the fourth recessed portion 119. This makes it possible to store lubricating oil in the fourth recessed portion 119.

[0151] When the rotating shaft 21 is at the eighth rotation angle, the fourth recess 119 and the fourth bearing groove 199 are positioned substantially the same. The lubricating oil stored in the fourth recess 119 can be supplied to the fourth bearing groove 199. In this embodiment, the sixth rotation angle and the eighth rotation angle are the same due to the relative positions of the third recess 118 and the fourth recess 119.

[0152] By repeating each of the above rotation angles, the lubricating oil is supplied from the second path 197 to the third bearing groove 198 and the fourth bearing groove 199 via the third recess 118 and the fourth recess 119. The lubricating oil supplied to the third bearing groove 198 and the fourth bearing groove 199 is supplied between the second bearing portion 191 and the second shaft portion 112.

[0153] Since the lubricating oil is temporarily stored in the third recess 118 and the fourth recess 119, the lubricating oil is supplied to the third bearing groove 198 and the fourth bearing groove 199 intermittently.

[0154] The third bearing groove 198 and the fourth bearing groove 199 are arranged at an interval from each other in the first direction (Z direction). The third bearing groove 198 and the fourth bearing groove 199 are supplied with lubricating oil from only one of the third recess 118 or the fourth recess 119. As a result, a constant amount of lubricating oil stored in the third recess 118 is intermittently supplied to the third bearing groove 198 from the third recess 118. The fourth bearing groove 199 is intermittently supplied with a constant amount of lubricating oil stored in the fourth recess 119 from the fourth recess 119. This suppresses fluctuations in the amount of lubricating oil supplied to the third bearing groove 198 and the fourth bearing groove 199.

[0155] As shown in FIG. 3, a through-hole 21H is provided in the central portion of the rotating shaft 21. The through-hole 21H extends to both ends of the rotating shaft 21 in the first direction (Z direction). The through-hole 21H communicates with the suction pressure region 2A. The second bearing portion 191 contacts the suction pressure region 2A via the through-hole 21H. That is, the fourth bearing groove 199 contacts the suction pressure region 2A. This allows a pressure difference to be generated at the end of the high-pressure lubricating oil supply path 8 branching off from the discharge path 3, making it easier for the lubricating oil to flow through the path.

[0156] In a rolling piston type electric compressor 1 according to an embodiment of the present disclosure, two recesses (a first recess 116 and a second recess 117) are provided in a first shaft portion 111 of a rotating shaft 21, and two grooves (a first bearing groove 148 and a second bearing groove 149) are provided in a first bearing portion 142 of a front side plate 140. The first bearing groove 148 extends from a center portion C1 of the first bearing portion 142 to an end portion F1 on the first compression chamber 26 side. The second bearing groove 149 extends from the center portion C1 to an end portion F2 on the opposite side from the first compression chamber 26. When the rotating shaft 21 is at a predetermined rotation angle, lubricating oil is stored in the first recess 116 and the second recess 117. The lubricating oil is supplied to the first bearing groove 148 and the second bearing groove 149 when the rotating shaft 21 is at the predetermined rotation angle. This allows the lubricating oil to be intermittently supplied to the first bearing groove 148 and the second bearing groove 149. Therefore, compared to a case where the lubricating oil is continuously supplied and the cross-sectional area of ​​part of the flow path is reduced to prevent an oversupply of lubricating oil, which can cause the lubricating oil to clog, or where the amount of lubricating oil supplied fluctuates due to fluctuations in the lubricating oil supply pressure, it is possible to stably supply a constant amount of lubricating oil to the sliding parts while preventing excessive supply of lubricating oil.As a result, it is possible to provide a highly reliable rolling piston type electric compressor 1.

[0157] In the rolling piston type electric compressor 1 according to one embodiment of the present disclosure, a constant amount of lubricating oil can be supplied intermittently. Therefore, when there is a high pressure difference in the lubricating oil supply path 8, the lubricating oil is continuously supplied, and the lubricating oil to be supplied runs out, preventing only refrigerant gas from flowing through the lubricating oil supply path 8 (gas path).

[0158] In the rolling piston type electric compressor 1 according to one embodiment of the present disclosure, the lubricating oil path is not configured to be extremely narrow, and therefore the lubricating oil path can be easily formed and processed, making it possible to provide an inexpensive rolling piston type electric compressor 1.

[0159] In a rolling piston type electric compressor 1 according to one embodiment of the present disclosure, the first bearing groove 148 at the end F1 of the first bearing portion 142 on the first compression chamber 26 side and the first vane 122 are arranged at approximately the same position in the circumferential direction of the rotating shaft 21, so that the lubricating oil supply position can be adjacent to the first vane 122, thereby maintaining the sliding characteristics of the vane.

[0160] In the rolling piston type electric compressor 1 according to one embodiment of the present disclosure, the first recess 116 and the second recess 117 are arranged on the outer peripheral surface of the rotating shaft 21 at positions facing each other around the axis C, thereby enabling the rotating shaft 21 to be balanced.

[0161] In a rolling piston type electric compressor 1 according to an embodiment of the present disclosure, two recesses (a third recess 118 and a fourth recess 119) are provided in a second shaft portion 112 of a rotating shaft 21, and two grooves (a third bearing groove 198 and a fourth bearing groove 199) are provided in a second bearing portion 191 of a rear side plate 190. The third bearing groove 198 extends from a center portion C2 of the second bearing portion 191 to an end portion F3 on the second compression chamber 27 side. The fourth bearing groove 199 extends from the center portion C2 to an end portion F4 on the opposite side from the second compression chamber 27. When the rotating shaft 21 is at a predetermined rotation angle, lubricating oil is stored in the third recess 118 and the fourth recess 119. The lubricating oil is supplied to the third bearing groove 198 and the fourth bearing groove 199 when the rotating shaft 21 is at the predetermined rotation angle. This allows the lubricating oil to be intermittently supplied to the third bearing groove 198 and the fourth bearing groove 199. Therefore, compared to a case where the lubricating oil is continuously supplied and the cross-sectional area of ​​part of the flow path is reduced to prevent an oversupply of lubricating oil, which can cause the lubricating oil to clog, or where the amount of lubricating oil supplied fluctuates due to fluctuations in the lubricating oil supply pressure, it is possible to stably supply a constant amount of lubricating oil to the sliding parts while preventing excessive supply of lubricating oil.As a result, it is possible to provide a highly reliable rolling piston type electric compressor 1.

[0162] The rolling piston electric compressor according to the present disclosure may include a two-stage compression mechanism in which refrigerant compressed by a first compression section is supplied to a second compression section for further compression. The rolling piston electric compressor according to the present disclosure may also include a single compression section including a piston, a vane, and a cylinder. When the rolling piston electric compressor includes a single compression section, the middle side plate may not be provided.

[0163] The rotating shaft may have one recess for each corresponding bearing for supplying lubricating oil, and the bearing may have one groove for supplying lubricating oil.

[0164] It should be noted that the above-described embodiments disclosed herein are illustrative in all respects and are not intended to be limiting. Therefore, the technical scope of the present disclosure should not be interpreted solely by the above-described embodiments. Furthermore, all modifications within the scope and meaning equivalent to the claims are included. In the description of the above-described embodiments, combinable configurations may be combined with each other. [Explanation of symbols]

[0165] 1 rolling piston type electric compressor, 2 suction path, 2A suction pressure region, 3 discharge path, 3A discharge pressure region, 4 first suction path, 5 second suction path, 6 first discharge path, 7 second discharge path, 8 lubricating oil supply path, 10 case, 11 first case, 12 second case, 13 suction port, 14 discharge port, 15 inner circumferential surface, 16 first communication hole, 17 second communication hole, 19 inner diameter portion, 20 compression mechanism, 21 rotating shaft, 21H through hole, 22 first compression section, 23 second compression section, 25 plate member, 26 first compression chamber, 27 second compression chamber, 28 oil storage chamber, 28A recess, 29 cover portion, 30 electric motor, 31 stator, 32 rotor, 33 inner circumferential surface, 40 oil separator, 41 cylindrical portion, 50 first supply path, 60 Second supply path, 110: fixing portion, 111: first shaft portion, 112: second shaft portion, 113: third shaft portion, 114: first eccentric shaft portion, 115: second eccentric shaft portion, 116: first recessed portion, 117: second recessed portion, 118: third recessed portion, 119: fourth recessed portion, 120: first piston, 121, 168: outer peripheral surface, 122: first vane, 123: tip portion, 124: side portion, 125: first cylinder, 126, 162, 179: inner peripheral surface, 127: vane groove, 128: through hole, 129: elastic member, 130: plate-shaped member, 131: fastening member, 132, 170: communication hole, 133, 144, 153, 171, 181, 196: first oil supply hole, 134, 154, 172, 182 Second oil supply hole, 135, 155, 175, 184 Third oil supply hole, 136, 156 Fifth passage, 140 Front side plate, 141 Outer periphery, 142 First bearing portion, 143 First intake port, 145, 146 Communication hole, 145A First throttle portion, 146A Second throttle portion, 147 First passage, 148 First bearing groove, 149 Second bearing groove, 150 Second piston, 151 Second vane, 152 Second cylinder, 160 Middle side plate, 161 First member, 163 First groove, 164 First discharge port, 165, 193 Discharge valve, 169 Gap, 173 Third passage, 174, 183 Fourth passage, 178 Second member, 180 Second intake port, 190 Rear side plate, 191 Second bearing portion, 192 Second discharge port, 197 second path, 198 third bearing groove, 199 fourth bearing groove, A1 first rotation angle, A2 second rotation angle, A3 third rotation angle, A4 fourth rotation angle, C shaft center, C1, C2 center, F1,F2, F3, F4 ends.

Claims

1. a case provided with an intake path and a discharge path; an electric motor housed in the case; a compression mechanism that is housed in the case and arranged horizontally alongside the electric motor, and that draws in refrigerant that has been drawn through the suction path and passed through the electric motor, compresses the refrigerant, and discharges the refrigerant to the discharge path; an oil separator provided on the discharge path to separate lubricating oil mixed in the refrigerant from the refrigerant; The compression mechanism includes: a rotating shaft driven by the electric motor and having an axis extending in a first direction; a piston that is rotatable in an eccentric state with respect to the axis as the rotary shaft rotates; a vane that abuts against the piston in a direction intersecting the first direction; a cylinder that accommodates the piston and the vane, and defines a compression chamber between the piston and the vane for compressing a refrigerant; a plate member that abuts against the cylinder in the first direction and that contacts the compression chamber, An oil storage chamber capable of storing lubricating oil is provided inside the case, a first supply path is formed that branches off from the discharge path and is capable of supplying the lubricating oil separated by the oil separator to the oil storage chamber; a second supply path is formed that can supply lubricating oil from the oil reservoir to a sliding position of the compression mechanism, the plate member has a bearing portion through which the rotation shaft is inserted in the first direction, the bearing portion is provided with a first bearing groove that continues from a center portion of the bearing portion to an end portion on a compression chamber side in the first direction, and a second bearing groove that continues from the center portion to an end portion on an opposite side to the compression chamber in the first direction, the first bearing groove and the second bearing groove are spaced apart from each other in the first direction, a first recess and a second recess are provided on an outer circumferential surface of the rotating shaft, the first recess and the second recess are spaced apart from each other in a circumferential direction of the rotating shaft, and are recessed toward an axial center; When the rotation shaft is at a first rotation angle, the lubricating oil is supplied from the second supply path to the first recessed portion, and the lubricating oil can be stored in the first recessed portion, When the rotation shaft is at a second rotation angle, the lubricating oil stored in the first recess can be supplied to the first bearing groove, When the rotation shaft is at a third rotation angle, the lubricating oil is supplied from the second supply path to the second recess so that the lubricating oil can be stored in the second recess, When the rotary shaft is at a fourth rotation angle, the lubricating oil stored in the second recess can be supplied to the second bearing groove.

2. 2. The rolling piston type electric compressor according to claim 1, wherein the first bearing groove and the vane at the end of the bearing portion on the compression chamber side are arranged at approximately the same position as each other in the circumferential direction of the rotary shaft.

3. 3. The rolling piston type electric compressor according to claim 1, wherein the first recess and the second recess are arranged on the outer circumferential surface of the rotary shaft at positions facing each other with respect to the axis of the rotary shaft.

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