Rotary Compressor

Abstract

To appropriately supply a lubricant to a clearance between a drive shaft and a bearing.SOLUTION: A drive shaft 15 comprises a main shaft portion 153, an intermediate shaft portion 154, and an upper eccentric shaft portion 152T disposed between the main shaft portion 153 and the intermediate shaft portion 154. In the drive shaft 15, there are formed: an oil supply longitudinal hole formed along a rotation axis; an eccentric longitudinal groove portion 44 which is formed on an eccentric part outer peripheral surface opposed to an inner peripheral surface of a hole formed in an upper piston 125T in the upper eccentric shaft portion 152, and connected to an upper eccentric shaft portion oil supply lateral hole 45; a longitudinal groove upper end portion 42 formed on an outer peripheral surface of the main shaft portion 153 and connected to one end of the eccentric longitudinal groove portion 44; a longitudinal groove lower end portion 43 formed on an outer peripheral surface of the intermediate shaft portion 154 and connected to the other end of the eccentric longitudinal groove portion 44; and the upper eccentric shaft portion oil supply lateral hole 45 connecting the oil supply longitudinal hole and the eccentric longitudinal groove portion 44.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to a rotary compressor. [Background technology]

[0002] A rotary compressor is known in which a drive shaft, a cylinder, and a piston are provided inside a compressor housing. The piston fits into an eccentric portion of the drive shaft and revolves inside a cylinder chamber formed inside the cylinder in response to the rotation of the drive shaft, compressing the refrigerant. A vertical oil feed hole and a horizontal oil feed hole are formed in the drive shaft. As the drive shaft rotates, the vertical oil feed hole draws up lubricating oil stored in the compressor housing, and the horizontal oil feed hole supplies a portion of the drawn up lubricating oil to a clearance between the piston and the eccentric portion (Patent Documents 1 and 2). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2003-176796 A [Patent Document 2] JP 2001-73977 A Summary of the Invention [Problem to be solved by the invention]

[0004] The rotary compressor further includes a bearing that rotatably supports the drive shaft. A clearance is formed between the drive shaft and the bearing. When the amount of lubricating oil supplied to the clearance is small, friction between the drive shaft and the bearing increases, resulting in a problem of reduced efficiency of the rotary compressor.

[0005] The disclosed technology has been made in consideration of the above points, and has an object to provide a rotary compressor that appropriately supplies lubricating oil to the clearance between the drive shaft and the bearing. [Means for solving the problem]

[0006] A rotary compressor according to one aspect of the present disclosure includes a compressor housing, a drive shaft disposed inside the compressor housing, a motor that rotates the drive shaft about a rotation axis, and a compression unit that compresses a refrigerant as the drive shaft rotates. Supported by a bearing for free rotation The compression section has a first shaft portion, a second shaft portion, and an eccentric shaft portion disposed between the first shaft portion and the second shaft portion. The compression section has a cylinder, and a piston that revolves inside a cylinder chamber formed inside the cylinder by the rotation of the drive shaft and has a hole that fits into the eccentric shaft portion. The drive shaft has an eccentric longitudinal groove portion formed on an outer peripheral surface of an eccentric portion that faces an inner peripheral surface of a hole formed in the piston of the eccentric shaft portion, and a piston that is connected to one end of the eccentric longitudinal groove portion formed on the outer peripheral surface of the first shaft portion. The bearing portion has an inner peripheral surface facing the inner peripheral surface of a hole formed therein. The rotating shaft has a first shaft longitudinal groove portion formed on an outer peripheral surface of the second shaft portion and connected to the other end of the eccentric longitudinal groove portion, a vertical oil feed hole formed along the rotating shaft, and a horizontal oil feed hole connecting the vertical oil feed hole and the eccentric longitudinal groove portion. Effect of the Invention

[0007] The rotary compressor of the present disclosure can appropriately supply lubricating oil to the clearance between the drive shaft and the bearing. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a vertical sectional view showing a rotary compressor of the embodiment. [Diagram 2] FIG. 2 is an exploded top perspective view showing a compression section of the rotary compressor of the embodiment. [Diagram 3] FIG. 3 is an exploded top perspective view showing the drive shaft of the rotary compressor of the embodiment. [Figure 4] FIG. 4 is a side view showing a part of the drive shaft of the rotary compressor of the embodiment. [Diagram 5] FIG. 5 is a cross-sectional view taken along line GG' in FIG. 4, showing the drive shaft of the rotary compressor of the embodiment. [Figure 6]FIG. 6 is a graph showing the relationship between several ratios and several efficiencies. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] A rotary compressor according to an embodiment disclosed in the present application will be described below with reference to the drawings. Note that the following description does not limit the technology of the present disclosure. In addition, in the following description, the same components are given the same reference numerals, and duplicated descriptions are omitted. EXAMPLES

[0010] Fig. 1 is a vertical cross-sectional view showing a rotary compressor of the embodiment, and Fig. 2 is an upper exploded perspective view showing a compression section of the rotary compressor of the embodiment. As shown in Fig. 1, the rotary compressor 1 includes a compression section 12 arranged at a lower part in a sealed vertically-mounted cylindrical compressor housing 10, a motor 11 arranged above the compression section 12 and driving the compression section 12 via a drive shaft 15, and a vertically-mounted cylindrical accumulator 25 fixed to a side part of the compressor housing 10.

[0011] The accumulator 25 is connected to the upper suction chamber 131T (see Figure 2) of the upper cylinder 121T via the upper suction pipe 105 and the accumulator upper curved pipe 31T, and is connected to the lower suction chamber 131S (see Figure 2) of the lower cylinder 121S via the lower suction pipe 104 and the accumulator lower curved pipe 31S.

[0012] The motor 11 has a stator 111 on the outside and a rotor 112 on the inside, with the stator 111 fixed to the inner surface of the compressor housing 10 by shrink fitting or welding, and the rotor 112 fixed by shrink fitting to the drive shaft 15 arranged along a straight line parallel to the axial direction.

[0013] Lubricating oil 18 is sealed inside compressor housing 10 in an amount sufficient to almost immerse compression section 12 in order to lubricate the components constituting compression section 12 and to seal upper compression chamber 133T (see FIG. 2) and lower compression chamber 133S (see FIG. 2). Examples of components lubricated by lubricating oil 18 include upper piston 125T, lower piston 125S, upper cylinder 121T, lower cylinder 121S, upper end plate 160T, lower end plate 160S, and intermediate partition plate 140. Mounting legs 310 that support the entire rotary compressor 1 are fixed to the underside of compressor housing 10.

[0014] 2, the compression section 12 is configured by stacking, from the top, an upper end plate cover 170T having a dome-shaped bulge, an upper end plate 160T, an upper cylinder 121T, an intermediate partition plate 140, a lower cylinder 121S, a lower end plate 160S, and a flat lower end plate cover 170S. The entire compression section 12 is fixed by a plurality of through bolts 174, 175 and auxiliary bolts 176 arranged approximately concentrically from above and below.

[0015] The annular upper cylinder 121T is provided with an upper suction hole 135T that fits with the upper suction pipe 105. The annular lower cylinder 121S is provided with a lower suction hole 135S that fits with the lower suction pipe 104. An upper piston 125T is disposed in an upper cylinder chamber 130T of the upper cylinder 121T. The outer peripheral surface of the upper piston 125T abuts against an inner peripheral surface 129T of the upper cylinder 121T. A lower piston 125S is disposed in a lower cylinder chamber 130S of the lower cylinder 121S. The outer peripheral surface of the lower piston 125S abuts against an inner peripheral surface 129S of the lower cylinder 121S.

[0016] The upper cylinder 121T is provided with an upper vane groove 128T extending radially outward from the center of the upper cylinder chamber 130T, and an upper vane 127T is disposed in the upper vane groove 128T. The lower cylinder 121S is provided with a lower vane groove 128S extending radially outward from the center of the lower cylinder chamber 130S, and a lower vane 127S is disposed in the lower vane groove 128S.

[0017] Upper cylinder 121T has upper spring hole 124T at a position overlapping with upper vane groove 128T from the outer surface, with a depth that does not penetrate into upper cylinder chamber 130T, and upper spring 126T is disposed in upper spring hole 124T. Lower cylinder 121S has lower spring hole 124S at a position overlapping with lower vane groove 128S from the outer surface, with a depth that does not penetrate into lower cylinder chamber 130S, and lower spring 126S is disposed in lower spring hole 124S.

[0018] The upper cylinder chamber 130T is formed inside the upper cylinder 121T by the upper end plate 160T being in close contact with the upper end, which is an end on one side of the upper cylinder 121T, and the intermediate partition plate 140 being in close contact with the lower end, which is the end on the other side of the upper cylinder 121T. That is, the upper end of the upper cylinder chamber 130T is closed by the upper end plate 160T, and the lower end is closed by the intermediate partition plate 140. The lower cylinder chamber 130S is formed inside the lower cylinder 121S by the intermediate partition plate 140 being in close contact with the upper end, which is an end on one side of the lower cylinder 121S, and the lower end, which is the end on the other side of the lower cylinder 121S, being closed by the lower end plate 160S. That is, the upper end of the lower cylinder chamber 130S is closed by the intermediate partition plate 140, and the lower end is closed by the lower end plate 160S.

[0019] The upper cylinder chamber 130T is divided into an upper suction chamber 131T communicating with the upper suction hole 135T and an upper compression chamber 133T communicating with an upper discharge hole 190T provided in the upper end plate 160T when the upper vane 127T is pressed by the upper spring 126T and abuts against the outer circumferential surface of the upper piston 125T. The lower cylinder chamber 130S is divided into a lower suction chamber 131S communicating with the lower suction hole 135S and a lower compression chamber 133S communicating with a lower discharge hole 190S provided in the lower end plate 160S when the lower vane 127S is pressed by the lower spring 126S and abuts against the outer circumferential surface of the lower piston 125S.

[0020] The upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T, and an annular upper valve seat (not shown) that surrounds the upper discharge hole 190T is formed on the outlet side of the upper discharge hole 190T. The upper end plate 160T is formed with an upper discharge valve accommodating recess 164T that extends in a groove shape from the position of the upper discharge hole 190T toward the outer periphery of the upper end plate 160T.

[0021] The upper discharge valve accommodating recess 164T accommodates the upper discharge valve 200T, which is a reed valve type upper discharge valve whose rear end is fixed in the upper discharge valve accommodating recess 164T by an upper rivet 202T and whose front part opens and closes the upper discharge hole 190T, and the entire upper discharge valve retainer 201T whose rear end is overlapped with the upper discharge valve 200T and fixed in the upper discharge valve accommodating recess 164T by an upper rivet 202T and whose front part is curved (warped) upward to open the upper discharge valve 200T, thereby regulating the opening degree of the upper discharge valve 200T.

[0022] The lower end plate 160S is provided with a lower discharge hole 190S which penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S, and an annular lower valve seat is formed on the outlet side of the lower discharge hole 190S surrounding the lower discharge hole 190S. The lower end plate 160S is formed with a lower discharge valve accommodating recess which extends in a groove shape from the position of the lower discharge hole 190S toward the outer periphery of the lower end plate 160S.

[0023] The lower discharge valve accommodating recess accommodates the lower discharge valve 200S, which is a reed valve type lower discharge valve whose rear end is fixed within the lower discharge valve accommodating recess by a lower rivet 202S and whose front part opens and closes the lower discharge hole 190S, and the lower discharge valve holder 201S, whose rear end is overlapped with the lower discharge valve 200S and fixed within the lower discharge valve accommodating recess by the lower rivet 202S and whose front part is curved (warped) downward to open the lower discharge valve 200S, thereby regulating the opening degree of the lower discharge valve 200S.

[0024] An upper end plate cover chamber 180T is formed between the upper end plate 160T and the upper end plate cover 170T having a dome-shaped bulge, which are fixed to each other. A lower end plate cover chamber 180S is formed between the lower end plate 160S and the flat lower end plate cover 170S, which are fixed to each other. A refrigerant passage hole 136 is provided which passes through the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper end plate 160T, and the upper cylinder 121T and communicates between the lower end plate cover chamber 180S and the upper end plate cover chamber 180T.

[0025] 3 is an upper exploded perspective view showing the drive shaft of the rotary compressor of the embodiment. The drive shaft 15 is formed in a roughly rod-like shape and includes a countershaft portion 151 (third shaft portion), a main shaft portion 153 (first shaft portion), a lower eccentric shaft portion 152S, an upper eccentric shaft portion 152T, and an intermediate shaft portion 154 (second shaft portion). The countershaft portion 151 is rotatably supported by a sub-bearing portion 161S. That is, the countershaft portion 151 is fitted into a hole formed in the sub-bearing portion 161S. The main shaft portion 153 is fixed to the rotor 112 and rotatably supported by a main bearing portion 161T. That is, the main shaft portion 153 is fitted into a hole formed in the main bearing portion 161T.

[0026] The lower eccentric shaft portion 152S is disposed between the countershaft portion 151 and the mainshaft portion 153, adjacent to the countershaft portion 151, and integrally formed with the countershaft portion 151. The lower eccentric shaft portion 152S is fitted into a hole formed in the lower piston 125S, i.e., the outer circumferential surface of the lower eccentric shaft portion 152S faces the inner circumferential surface of the hole formed in the lower piston 125S. The upper eccentric shaft portion 152T is disposed between the lower eccentric shaft portion 152S and the mainshaft portion 153, adjacent to the mainshaft portion 153, and integrally formed with the mainshaft portion 153. The upper eccentric shaft portion 152T is fitted into a hole formed in the upper piston 125T, i.e., the outer circumferential surface of the upper eccentric shaft portion 152T faces the inner circumferential surface of the hole formed in the upper piston 125T. The lower eccentric shaft portion 152S and the upper eccentric shaft portion 152T are provided with a phase difference of approximately 180 degrees from each other.

[0027] The intermediate shaft portion 154 is disposed between the lower eccentric shaft portion 152S and the upper eccentric shaft portion 152T, adjacent to the lower eccentric shaft portion 152S and integrally formed with the lower eccentric shaft portion 152S, and adjacent to the upper eccentric shaft portion 152T and integrally formed with the upper eccentric shaft portion 152T. The intermediate shaft portion 154 is surrounded by the intermediate partition plate 140, and the outer peripheral surface of the intermediate shaft portion 154 faces the inner peripheral surface of the hole formed in the intermediate partition plate 140. The drive shaft 15 is provided with an oil supply vane 158. The drive shaft 15 is formed with an oil supply vertical hole 155 penetrating from the lower end to the upper end. The oil supply vane 158 is press-fitted into the oil supply vertical hole 155 and fixed to the drive shaft 15.

[0028] FIG. 4 is a side view showing a part of the drive shaft 15 of the rotary compressor of the embodiment. The drive shaft 15 is further formed with an upper eccentric shaft portion vertical groove 41. The upper eccentric shaft portion vertical groove 41 is formed so as to be along a straight line parallel to the axial direction. The upper eccentric shaft portion vertical groove 41 is formed with a vertical groove upper end portion 42, a vertical groove lower end portion 43, and an eccentric vertical groove portion 44. The vertical groove upper end portion 42 is formed on the outer circumferential surface of the main shaft portion 153 of the drive shaft 15, and the upper end of the upper eccentric shaft portion vertical groove 41 is formed in the vertical groove upper end portion 42. A part of the vertical groove upper end portion 42 faces the inner circumferential surface of a hole formed in the main bearing portion 161T, that is, it is formed on the outer circumferential surface portion of the outer circumferential surface of the main shaft portion 153 of the drive shaft 15 that faces the inner circumferential surface of the hole formed in the main bearing portion 161T.

[0029] The vertical groove lower end portion 43 is formed on the outer peripheral surface of the intermediate shaft portion 154 of the drive shaft 15, and the lower end of the upper eccentric shaft portion vertical groove 41 is formed in the vertical groove lower end portion 43. A part of the vertical groove lower end portion 43 faces the inner peripheral surface of the hole formed in the intermediate partition plate 140, that is, it is formed on the outer peripheral surface portion of the outer peripheral surface of the intermediate shaft portion 154 of the drive shaft 15 that faces the inner peripheral surface of the intermediate partition plate 140. The eccentric vertical groove portion 44 is formed between the vertical groove upper end portion 42 and the vertical groove lower end portion 43. The upper end of the eccentric vertical groove portion 44 is connected to the vertical groove upper end portion 42, and the lower end of the eccentric vertical groove portion 44 is connected to the vertical groove lower end portion 43. The eccentric vertical groove portion 44 is formed on the outer peripheral surface of the upper eccentric shaft portion 152T of the drive shaft 15, that is, it faces the inner peripheral surface of the upper piston 125T. The eccentric groove portion 44 is further formed so that the area of ​​a cross section intersecting a plane perpendicular to the axial direction does not vary with respect to axial position.

[0030] The drive shaft 15 is further formed with an upper eccentric shaft partial horizontal oil-feed hole 45. FIG. 5 is a cross-sectional view taken along line G-G' in FIG. 4, showing the drive shaft 15 of the rotary compressor of the embodiment. The upper eccentric shaft partial horizontal oil-feed hole 45 is formed inside the upper eccentric shaft portion 152T of the drive shaft 15, and is formed along a straight line 46. The straight line 46 is perpendicular to the axial direction and perpendicular to a rotation axis 47 about which the drive shaft 15 rotates. One end of the upper eccentric shaft partial horizontal oil-feed hole 45 is connected to the oil-feed vertical hole 155, and the other end of the upper eccentric shaft partial horizontal oil-feed hole 45 is connected to the eccentric vertical groove portion 44 of the upper eccentric shaft portion vertical groove 41. The cross-sectional area B of the eccentric longitudinal groove portion 44 indicates the area of ​​a cross section where the eccentric longitudinal groove portion 44 intersects with a plane perpendicular to the axial direction. The cross-sectional area A of the upper eccentric shaft partial horizontal oil-feed hole 45 is equal to the area of ​​a cross section where the upper eccentric shaft partial horizontal oil-feed hole 45 intersects with a plane perpendicular to the straight line 46. The eccentric longitudinal groove portion 44 and the upper eccentric shaft partial horizontal oil-feed hole 45 are formed so that the ratio B / A obtained by dividing the cross-sectional area B by the cross-sectional area A satisfies the following formula. 0.4≦B / A≦1

[0031] When the rotary compressor 1 compresses the refrigerant, the drive shaft 15 rotates in a rotation direction 51 around the rotation shaft 47. At this time, an angle θ seen in the rotation direction 51 from a starting line 53 that starts from the rotation shaft 47 and intersects with a maximum eccentric position point 52 of the upper eccentric shaft to a moving radius that starts from the rotation shaft 47 and intersects with the upper eccentric shaft portion vertical groove 41 is greater than 180 degrees and smaller than 360 degrees. The maximum eccentric position point 52 of the upper eccentric shaft indicates the point farthest from the rotation shaft 47 on the outer circumferential surface of the upper eccentric shaft portion 152T. That is, the length of an opposite direction path tracing the outer peripheral surface of the upper eccentric shaft portion 152T in the opposite direction of the rotational direction 51 from the upper eccentric shaft maximum eccentric position point 52 to the upper eccentric shaft portion vertical groove 41 is shorter than the length of a rotational direction path tracing the outer peripheral surface of the upper eccentric shaft portion 152T in the rotational direction 51 from the upper eccentric shaft maximum eccentric position point 52 to the upper eccentric shaft portion vertical groove 41. In other words, the upper eccentric shaft portion vertical groove 41 is formed so that the angle θ is greater than -180 degrees and less than 0 degrees.

[0032] The drive shaft 15 further has a lower eccentric shaft portion longitudinal groove and a lower eccentric shaft portion horizontal oil supply hole, which are not shown. The lower eccentric shaft portion longitudinal groove is formed in the same manner as the upper eccentric shaft portion longitudinal groove 41. That is, the lower eccentric shaft portion longitudinal groove is formed along a straight line parallel to the axial direction, that is, along a straight line parallel to the rotation shaft 47, like the upper eccentric shaft portion longitudinal groove 41. The upper end of the lower eccentric shaft portion longitudinal groove is formed on the outer peripheral surface of the intermediate shaft portion 154 of the drive shaft 15. The lower end of the lower eccentric shaft portion longitudinal groove is formed on the outer peripheral surface of the countershaft portion 151 of the drive shaft 15, and faces the inner peripheral surface of the hole formed in the counterbearing portion 161S. The eccentric longitudinal groove portion connecting the upper end and the lower end of the lower eccentric shaft portion longitudinal groove is formed on the outer peripheral surface of the lower eccentric shaft portion 152S of the drive shaft 15.

[0033] The angle θ' of rotation in the rotation direction 51 around the rotation axis 47 from the starting line intersecting the maximum eccentric position of the lower eccentric shaft with the rotation axis 47 as the starting point to the moving radius intersecting the lower eccentric shaft portion vertical groove with the rotation axis 47 as the starting point is greater than 180 degrees and smaller than 360 degrees, in other words, greater than -180 degrees and smaller than 0 degrees. The maximum eccentric position of the lower eccentric shaft indicates the point on the outer circumferential surface of the lower eccentric shaft portion 152S that is farthest from the rotation axis 47. That is, the lower eccentric shaft portion vertical groove is formed so that the opposite direction path is shorter than the rotation direction path. Here, the opposite direction path indicates the path that traces the outer circumferential surface of the lower eccentric shaft portion 152S from the maximum eccentric position of the lower eccentric shaft to the lower eccentric shaft portion vertical groove in the opposite direction of the rotation direction 51. The rotational direction path indicates a path that follows the outer circumferential surface of the lower eccentric shaft portion 152S from the maximum eccentric position point of the lower eccentric shaft to the lower eccentric shaft portion vertical groove in the rotational direction 51. In other words, the lower eccentric shaft portion vertical groove is formed so that the angle θ' is greater than -180 degrees and less than 0 degrees.

[0034] The lower eccentric shaft portion horizontal oil-feed hole is formed inside the lower eccentric shaft portion 152S of the drive shaft 15, similar to the upper eccentric shaft portion horizontal oil-feed hole 45. The straight line along which the lower eccentric shaft portion horizontal oil-feed hole extends is perpendicular to the axial direction and perpendicular to the rotation shaft 47. One end of the lower eccentric shaft portion horizontal oil-feed hole is connected to the vertical oil-feed hole 155, and the other end of the lower eccentric shaft portion horizontal oil-feed hole is connected to the eccentric vertical groove portion of the lower eccentric shaft portion vertical groove. The cross-sectional area B' of the eccentric longitudinal groove portion of the lower eccentric shaft portion longitudinal groove indicates the area of ​​a cross section where the intermediate longitudinal groove portion of the lower eccentric shaft portion longitudinal groove intersects with a plane perpendicular to the axial direction. The cross-sectional area A' of the lower eccentric shaft portion horizontal oil-feed hole is equal to the area of ​​a cross section where the lower eccentric shaft portion horizontal oil-feed hole intersects with a plane perpendicular to the straight line along which the lower eccentric shaft portion horizontal oil-feed hole extends. The intermediate longitudinal groove portion of the lower eccentric shaft portion longitudinal groove and the lower eccentric shaft portion horizontal oil-feed hole are formed so that the ratio B' / A', obtained by dividing the cross-sectional area B' by the cross-sectional area A', satisfies the following formula. 0.4≦B' / A'≦1

[0035] [Operation of the rotary compressor 1 of the embodiment] The flow of the refrigerant caused by the rotation of the drive shaft 15 will be described below. In the upper cylinder chamber 130T, the upper piston 125T fitted to the upper eccentric shaft portion 152T of the drive shaft 15 revolves along the inner peripheral surface 129T of the upper cylinder 121T due to the rotation of the drive shaft 15, so that the upper suction chamber 131T expands in volume while drawing in the refrigerant from the upper suction pipe 105, and the upper compression chamber 133T compresses the refrigerant while reducing its volume. When the pressure of the compressed refrigerant becomes higher than the pressure of the upper end plate cover chamber 180T outside the upper discharge valve 200T, the upper discharge valve 200T opens and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T. The refrigerant discharged to the upper end plate cover chamber 180T is discharged into the compressor housing 10 from the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.

[0036] In the lower cylinder chamber 130S, the lower piston 125S fitted to the lower eccentric shaft portion 152S of the drive shaft 15 revolves along the inner peripheral surface 129S of the lower cylinder 121S by the rotation of the drive shaft 15, so that the lower suction chamber 131S expands its volume while drawing in the refrigerant from the lower suction pipe 104, and the lower compression chamber 133S compresses the refrigerant while reducing its volume. When the pressure of the compressed refrigerant becomes higher than the pressure of the lower end plate cover chamber 180S outside the lower discharge valve 200S, the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. The refrigerant discharged to the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 and the upper end plate cover chamber 180T and is discharged into the inside of the compressor housing 10 from the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.

[0037] The refrigerant discharged into the inside of the compressor casing 10 is guided above the motor 11 through a notch (not shown) that connects the top and bottom of the stator 111 and is provided on the outer periphery of the stator 111, or a gap (not shown) in the winding portion of the stator 111, or a gap 115 (see Figure 1) between the stator 111 and the rotor 112, and is discharged from the discharge pipe 107 at the top of the compressor casing 10.

[0038] The flow of the lubricating oil 18 will be described below. The lubricating oil 18 stored in the compressor housing 10 is sucked up into the oil supply vertical hole 155 by the oil supply vane 158 when the drive shaft 15 rotates. The lubricating oil 18 inside the upper eccentric shaft portion oil supply horizontal hole 45 is given a centrifugal force when the drive shaft 15 rotates, and flows toward the upper eccentric shaft portion vertical groove 41 and is supplied to the upper eccentric shaft portion vertical groove 41. The lubricating oil 18 inside the oil supply vertical hole 155 is sucked into the upper eccentric shaft portion oil supply horizontal hole 45 by the lubricating oil 18 inside the upper eccentric shaft portion oil supply horizontal hole 45 flowing toward the upper eccentric shaft portion vertical groove 41. The lubricating oil 18 inside the lower eccentric shaft portion oil supply horizontal hole is given a centrifugal force when the drive shaft 15 rotates, and flows toward the lower eccentric shaft portion vertical groove and is supplied to the lower eccentric shaft portion vertical groove. The lubricating oil 18 inside the vertical oil feed hole 155 flows toward the lower eccentric shaft partial horizontal oil feed hole, and is thereby sucked into the lower eccentric shaft partial horizontal oil feed hole. The lubricating oil 18 stored in the compressor housing 10 is sucked from the vertical oil feed hole 155 into the upper eccentric shaft partial horizontal oil feed hole 45 and the lower eccentric shaft partial horizontal oil feed hole, and is further sucked up into the vertical oil feed hole 155.

[0039] That is, the lubricating oil 18 stored in the compressor housing 10 is supplied to the upper eccentric shaft portion vertical groove 41 and the lower eccentric shaft portion vertical groove through the oil supply vertical hole 155, the upper eccentric shaft portion horizontal oil supply hole 45, and the lower eccentric shaft portion horizontal oil supply hole, respectively, as the drive shaft 15 rotates. The lubricating oil 18 supplied to the upper eccentric shaft portion vertical groove 41 is supplied to the eccentric vertical groove portion 44 of the upper eccentric shaft portion vertical groove 41, and is supplied to the outer circumferential surface of the upper eccentric shaft portion 152T of the drive shaft 15 through the eccentric vertical groove portion 44. The lubricating oil 18 supplied to the outer circumferential surface of the upper eccentric shaft portion 152T reduces the frictional force acting between the upper eccentric shaft portion 152T and the upper piston 125T, thereby reducing the wear of the upper eccentric shaft portion 152T and the upper piston 125T.

[0040] The lubricating oil 18 supplied to the upper eccentric shaft portion vertical groove 41 is further supplied to the vertical groove upper end portion 42 and the vertical groove lower end portion 43 via the eccentric vertical groove portion 44. The lubricating oil 18 supplied to the vertical groove upper end portion 42 is supplied to the outer circumferential surface of the main shaft portion 153 and is supplied to the clearance between the main shaft portion 153 and the main bearing portion 161T. The rotary compressor 1 can reduce the frictional force acting between the main shaft portion 153 and the main bearing portion 161T by supplying the lubricating oil 18 to the clearance between the main shaft portion 153 and the main bearing portion 161T, and can reduce the wear of the main shaft portion 153 and the main bearing portion 161T. The lubricating oil 18 supplied to the vertical groove lower end portion 43 is supplied to the outer circumferential surface of the intermediate shaft portion 154 and is supplied to the clearance between the intermediate shaft portion 154 and the intermediate partition plate 140.

[0041] The size of the clearance between the upper eccentric shaft portion 152T and the upper piston 125T varies as the upper piston 125T revolves. For example, the position where the clearance between the upper eccentric shaft portion 152T and the upper piston 125T has a large width and a small width varies as the upper piston 125T revolves. The upper eccentric shaft portion longitudinal groove 41 is connected to the large width area of ​​the clearance between the upper eccentric shaft portion 152T and the upper piston 125T by forming the upper eccentric shaft portion longitudinal groove 41 so that the angle θ is greater than -180 degrees and less than 0 degrees. The lubricating oil 18 supplied to the upper eccentric shaft portion longitudinal groove 41 is supplied in large amount to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T by connecting the upper eccentric shaft portion longitudinal groove 41 to the relatively large width area of ​​the clearance between the upper eccentric shaft portion 152T and the upper piston 125T. By supplying a large amount of lubricating oil 18 to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T, the rotary compressor 1 can further reduce the frictional force acting between the upper eccentric shaft portion 152T and the upper piston 125T, and can further reduce wear of the upper eccentric shaft portion 152T and the upper piston 125T.

[0042] The lubricating oil 18 supplied to the lower eccentric shaft portion longitudinal groove is supplied to the eccentric longitudinal groove portion of the lower eccentric shaft portion longitudinal groove, and is supplied to the outer circumferential surface of the lower eccentric shaft portion 152S of the drive shaft 15 through the eccentric longitudinal groove portion. By supplying the lubricating oil 18 to the outer circumferential surface of the lower eccentric shaft portion 152S, the rotary compressor 1 can reduce the frictional force acting between the lower eccentric shaft portion 152S and the lower piston 125S, and can reduce wear of the lower eccentric shaft portion 152S and the lower piston 125S.

[0043] The lubricating oil 18 supplied to the lower eccentric shaft portion longitudinal groove is further supplied to the upper end and the lower end of the lower eccentric shaft portion longitudinal groove through the eccentric longitudinal groove portion of the lower eccentric shaft portion longitudinal groove. The lubricating oil 18 supplied to the upper end of the lower eccentric shaft portion longitudinal groove is supplied to the outer circumferential surface of the intermediate shaft portion 154 and is supplied to the clearance between the intermediate shaft portion 154 and the intermediate partition plate 140. The lubricating oil 18 supplied to the lower end of the lower eccentric shaft portion longitudinal groove is supplied to the outer circumferential surface of the countershaft portion 151 and is supplied to the clearance between the countershaft portion 151 and the sub-bearing portion 161S. The lubricating oil 18 supplied to the clearance between the countershaft portion 151 and the sub-bearing portion 161S reduces the frictional force acting between the countershaft portion 151 and the sub-bearing portion 161S, and reduces the wear of the countershaft portion 151 and the sub-bearing portion 161S.

[0044] The size of the clearance between the lower eccentric shaft portion 152S and the lower piston 125S varies as the lower piston 125S revolves. For example, the position where the large part and the small part of the clearance between the lower eccentric shaft portion 152S and the lower piston 125S are generated varies as the lower piston 125S revolves. The lower eccentric shaft portion longitudinal groove is connected to the large width area of ​​the clearance by forming the lower eccentric shaft portion longitudinal groove so that the angle θ' is greater than -180 degrees and less than 0 degrees. The lubricating oil 18 supplied to the lower eccentric shaft portion longitudinal groove is supplied in large amount to the clearance between the lower eccentric shaft portion 152S and the lower piston 125S by connecting the lower eccentric shaft portion longitudinal groove to a predetermined area of ​​the relatively large width area of ​​the clearance between the lower eccentric shaft portion 152S and the lower piston 125S. By supplying a large amount of lubricating oil 18 to the clearance between the lower eccentric shaft portion 152S and the lower piston 125S, the rotary compressor 1 can further reduce the frictional force acting between the lower eccentric shaft portion 152S and the lower piston 125S, and can further reduce wear of the lower eccentric shaft portion 152S and the lower piston 125S.

[0045] In order to confirm the effect of the rotary compressor 1, a plurality of rotary compressor prototypes have been manufactured and evaluation tests have been performed on each of the plurality of rotary compressor prototypes. Table 1 shows a plurality of manufacturing conditions and a plurality of efficiencies corresponding to the plurality of rotary compressor prototypes. [Table 1]

[0046] The multiple rotary compressor prototypes include a rotary compressor with prototype number 1, a rotary compressor with prototype number 2, a rotary compressor with prototype number 3, a rotary compressor with prototype number 4, and a rotary compressor with prototype number 5. Each of the multiple manufacturing conditions indicates a cross-sectional area A and a cross-sectional area B. The multiple rotary compressor prototypes are manufactured so that the ratios B / A of the cross-sectional area A and the cross-sectional area B are different from one another, and are manufactured similarly to one another except that the ratios B / A are different from one another.

[0047] The cross-sectional area A of the rotary compressor prototype No. 1 is 7.07 mm 2 The cross-sectional area B of the rotary compressor prototype No. 1 is 3.64 mm 2 The cross-sectional area A of the prototype rotary compressor No. 2 is 7.07 mm 2 The cross-sectional area B of the prototype rotary compressor No. 2 is 3.75 mm 2 The cross-sectional area A of the prototype rotary compressor No. 3 is 7.07 mm 2 The cross-sectional area B of the prototype rotary compressor No. 3 is 5.30 mm 2 The cross-sectional area A of the prototype rotary compressor No. 4 is 7.07 mm 2 The cross-sectional area B of the prototype rotary compressor No. 4 is 5.50 mm 2 The cross-sectional area A of the prototype rotary compressor No. 5 is 7.07 mm 2 The cross-sectional area B of the prototype rotary compressor No. 5 is 6.30 mm 2 This shows that.

[0048] FIG. 6 is a graph showing the relationship between multiple ratios B / A and multiple efficiencies. The multiple ratios B / A correspond to multiple rotary compressor prototypes. The ratio B / A corresponding to a certain rotary compressor prototype among the multiple ratios B / A indicates a value obtained by dividing the cross-sectional area B of the rotary compressor prototype by the cross-sectional area A of the rotary compressor prototype. The multiple efficiencies correspond to multiple rotary compressor prototypes and are obtained by mounting each of the multiple rotary compressor prototypes on the same refrigeration cycle device. The efficiency corresponding to a certain rotary compressor prototype among the multiple efficiencies indicates a value obtained by dividing the capacity (e.g., COP) of the refrigeration cycle device in which the rotary compressor prototype is provided by the amount of power consumed by the rotary compressor prototype.

[0049] The graph in Fig. 6 shows that when the ratio B / A is 0.75 or less, the smaller the ratio B / A, the lower the efficiency, and that the smaller the cross-sectional area B of the eccentric vertical groove portion 44 is relative to the cross-sectional area A of the upper eccentric shaft portion horizontal oil-feed hole 45, the lower the efficiency of the rotary compressor 1. In other words, the graph in Fig. 6 shows that when the ratio B / A is 0.75 or less, the smaller the ratio B / A, the greater the frictional force acting against the rotation of the drive shaft 15, and that the amount of lubricating oil 18 supplied to the clearance between the main shaft portion 153 and the main bearing portion 161T is reduced.

[0050] 6 further shows that when the ratio B / A is greater than 0.75, the greater the ratio B / A, the lower the efficiency, and the smaller the cross-sectional area B of the eccentric vertical groove portion 44 is relative to the cross-sectional area A of the upper eccentric shaft portion horizontal oil-feed hole 45, the lower the efficiency of the rotary compressor 1. That is, the graph in FIG. 6 shows that when the ratio B / A is greater than 0.75, the greater the ratio B / A, the greater the frictional force acting against the rotation of the drive shaft 15, and the amount of lubricating oil 18 supplied to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T is reduced by the amount of the increase in the amount of lubricating oil 18 supplied to the clearance between the main shaft portion 153 and the main bearing portion 161T.

[0051] The graph in FIG. 6 further shows that the efficiency of the rotary compressor 1 becomes greater than a predetermined value E when the ratio B / A satisfies the following formula: 0.4≦B / A≦1 The graph in Fig. 6 further indicates that when the ratio B / A does not satisfy the above formula, the efficiency of the rotary compressor 1 may be smaller than the value E. In other words, the graph in Fig. 6 indicates that the efficiency of the rotary compressor 1 in which the ratio B / A is within a predetermined range is better than the efficiency of other rotary compressors in which the ratio B / A is outside that range.

[0052] [Effects of the rotary compressor 1 according to the embodiment] The rotary compressor 1 of the embodiment includes a compressor housing 10, a drive shaft 15 disposed inside the compressor housing 10, a motor 11 that rotates the drive shaft 15 around a rotary shaft 47, and a compression section 12 that compresses a refrigerant by the rotation of the drive shaft 15. The drive shaft 15 includes a main shaft portion 153, an intermediate shaft portion 154, and an upper eccentric shaft portion 152T disposed between the main shaft portion 153 and the intermediate shaft portion 154. The compression section 12 includes an upper cylinder 121T and an upper piston 125T. The upper piston 125T has a hole that fits into the upper eccentric shaft portion 152T, and revolves inside an upper cylinder chamber 130T formed inside the upper cylinder 121T by the rotation of the drive shaft 15. The drive shaft 15 is formed with an eccentric vertical groove portion 44, a vertical groove upper end portion 42, a vertical groove lower end portion 43, an oil supply vertical hole 155, and an upper eccentric shaft portion horizontal oil supply hole 45. The eccentric vertical groove portion 44 is formed on the outer peripheral surface of the eccentric portion of the upper eccentric shaft portion 152T that faces the inner peripheral surface of the hole formed in the upper piston 125T, and is connected to the upper eccentric shaft portion horizontal oil supply hole 45. The vertical groove upper end portion 42 is formed on the outer peripheral surface of the main shaft portion 153, and is connected to one end of the eccentric vertical groove portion 44. The vertical groove lower end portion 43 is formed on the outer peripheral surface of the intermediate shaft portion 154, and is connected to the other end of the eccentric vertical groove portion 44. The oil supply vertical hole 155 is formed along the rotation shaft 47. The upper eccentric shaft portion horizontal oil supply hole 45 connects the oil supply vertical hole 155 and the eccentric vertical groove portion 44.

[0053] In the rotary compressor 1 of the embodiment, the upper end of the upper eccentric shaft portion vertical groove 41 is formed on the outer circumferential surface of the main shaft portion 153, so that the lubricating oil 18 can be appropriately supplied to the clearance between the main shaft portion 153 and the main bearing portion 161T. Therefore, the rotary compressor 1 can reduce the frictional force acting between the drive shaft 15 and the main bearing portion 161T, and the efficiency of the rotary compressor 1 can be improved.

[0054] In addition, in the rotary compressor 1 of the embodiment, the ratio B / A obtained by dividing the area (cross-sectional area B) of a cross section where the eccentric vertical groove portion 44 intersects with a plane perpendicular to the rotating shaft 47 by the area (cross-sectional area A) of a cross section where the upper eccentric shaft partial oil-feed horizontal hole 45 intersects with a plane perpendicular to the straight line along which the upper eccentric shaft partial oil-feed horizontal hole 45 extends satisfies the following equation. 0.4≦B / A≦1 The rotary compressor 1 of the embodiment is manufactured so that the ratio B / A falls within a specific range, and thus it is possible to supply an appropriate amount of lubricating oil 18 to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T and to the clearance between the main shaft portion 153 and the main bearing portion 161T. By supplying an appropriate amount of lubricating oil 18 to a plurality of clearances, the rotary compressor 1 of the embodiment can appropriately reduce the frictional force acting on the drive shaft 15 and improve the efficiency of compressing the refrigerant.

[0055] In addition, in the rotary compressor 1 of the embodiment, the angle θ of rotation in the rotation direction 51 around the rotary shaft 47 from the starting line 53 starting from the rotary shaft 47 and intersecting with the maximum eccentric position point 52 of the upper eccentric shaft to the moving radius starting from the rotary shaft 47 and intersecting with the vertical groove 41 of the upper eccentric shaft portion is greater than -180 degrees and smaller than 0 degrees. The rotary compressor 1 of the embodiment is manufactured so that the angle θ is an appropriate value, so that a large amount of lubricating oil 18 can be supplied to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T. In the rotary compressor 1 of the embodiment, the frictional force between the upper eccentric shaft portion 152T and the upper piston 125T can be reduced by supplying a large amount of lubricating oil 18 to the clearance between the upper eccentric shaft portion 152T and the upper piston 125T, and the efficiency of compressing the refrigerant can be improved.

[0056] The drive shaft 15 of the rotary compressor 1 of the embodiment further includes a countershaft portion 151 and a lower eccentric shaft portion 152S disposed between the intermediate shaft portion 154 and the countershaft portion 151. The compression section 12 further includes a lower cylinder 121S and a lower piston 125S. The lower piston 125S has a hole that fits into the lower eccentric shaft portion 152S, and revolves inside a lower cylinder chamber 130S formed inside the lower cylinder 121S as the drive shaft 15 rotates. The drive shaft 15 further includes an eccentric vertical groove portion of the lower eccentric portion vertical groove, a vertical groove upper end portion of the lower eccentric portion vertical groove, a vertical groove lower end portion of the lower eccentric portion vertical groove, and a lower eccentric portion horizontal oil supply hole. The eccentric vertical groove portion of the lower eccentric portion vertical groove is formed on the outer peripheral surface of the lower eccentric shaft portion 152S that faces the inner peripheral surface of the hole formed in the lower piston 125S. An upper end portion of the lower eccentric portion longitudinal groove is formed on the outer circumferential surface of the intermediate shaft portion 154 and is connected to one end of the eccentric portion of the lower eccentric portion longitudinal groove. A lower end portion of the lower eccentric portion longitudinal groove is formed on the outer circumferential surface of the counter shaft portion 151 and is connected to the other end of the eccentric portion of the lower eccentric portion longitudinal groove. The lower eccentric shaft portion oil feed vertical hole connects the oil feed vertical hole 155 and the eccentric portion of the lower eccentric portion longitudinal groove.

[0057] In the rotary compressor 1 of the embodiment, the lower end portion of the lower eccentric portion vertical groove is formed on the outer circumferential surface of the countershaft portion 151, so that the lubricating oil 18 can be appropriately supplied to the clearance between the countershaft portion 151 and the sub-bearing portion 161S. Therefore, the rotary compressor 1 can reduce the frictional force acting between the drive shaft 15 and the sub-bearing portion 161S, and can improve the efficiency of compressing the refrigerant. In the rotary compressor 1 of the embodiment, the lower eccentric portion vertical groove is formed in the same manner as the upper eccentric shaft portion vertical groove 41, so that the efficiency of compressing the refrigerant can be further improved.

[0058] In the rotary compressor 1 of the embodiment, the ratio B' / A' obtained by dividing the cross-sectional area B' of the lower eccentric portion vertical groove by the cross-sectional area A' of the lower eccentric shaft portion horizontal oil-feed hole satisfies the following formula. 0.4≦B' / A'≦1 The rotary compressor 1 of the embodiment is manufactured so that the ratio B' / A' falls within a specific range, whereby an appropriate amount of lubricating oil 18 can be supplied to the clearance between the lower eccentric shaft portion 152S and the lower piston 125S and to the clearance between the counter shaft portion 151 and the counter bearing portion 161S. The rotary compressor 1 of the embodiment can appropriately reduce the frictional force acting on the drive shaft 15 by supplying an appropriate amount of lubricating oil 18 to a plurality of clearances, and can improve the efficiency of compressing the refrigerant.

[0059] In addition, in the rotary compressor 1 of the embodiment, the angle θ' of rotation in the rotation direction 51 around the rotary shaft 47 from the starting line intersecting the maximum eccentric position point of the lower eccentric shaft with the rotary shaft 47 as the starting point to the moving radius intersecting the vertical groove of the lower eccentric portion with the rotary shaft 47 as the starting point is larger than -180 degrees and smaller than 0 degrees. The rotary compressor 1 of the embodiment is manufactured so that the angle θ' is an appropriate value, so that a large amount of lubricating oil 18 can be supplied to the clearance between the lower eccentric shaft portion 152S and the lower piston 125S. In the rotary compressor 1 of the embodiment, the frictional force between the lower eccentric shaft portion 152S and the lower piston 125S can be appropriately reduced by supplying a large amount of lubricating oil 18 to the clearance between the lower eccentric shaft portion 152S and the lower piston 125S, and the efficiency of compressing the refrigerant can be improved.

[0060] Incidentally, in the rotary compressor 1 of the embodiment described above, a part of the vertical groove upper end portion 42 faces the inner peripheral surface of the main bearing portion 161T, but the vertical groove upper end portion 42 may not face the inner peripheral surface of the main bearing portion 161T. Also, in the rotary compressor 1 of the embodiment described above, the lower end of the vertical groove of the lower eccentric shaft portion faces the inner peripheral surface of the sub-bearing portion 161S, but the lower end of the vertical groove of the lower eccentric shaft portion may not face the inner peripheral surface of the sub-bearing portion 161S. Even in this case, the rotary compressor 1 can appropriately supply the lubricating oil 18 to the clearance between the main shaft portion 153 and the main bearing portion 161T and between the sub-shaft portion 151 and the sub-bearing portion 161S. Therefore, the rotary compressor 1 can reduce the frictional force acting between the main shaft portion 153 and the main bearing portion 161T and between the sub-shaft portion 151 and the sub-bearing portion 161S, and can improve the efficiency of compressing the refrigerant.

[0061] Incidentally, the rotary compressor 1 of the above-described embodiment is formed as a two-cylinder rotary compressor, but may be formed as a single-cylinder rotary compressor. For example, the compression section 12 is omitted from the lower cylinder 121S, the lower piston 125S, the lower vane 127S, and the intermediate partition plate 140. The drive shaft 15 is omitted from the lower eccentric shaft portion 152S and the intermediate shaft portion 154, the upper eccentric shaft portion 152T is adjacent to the countershaft portion 151, and the vertical groove lower end portion 43 of the upper eccentric shaft portion vertical groove 41 is formed on the outer circumferential surface of the countershaft portion 151. Such a rotary compressor can also reduce the frictional force acting on the drive shaft 15, and improve the efficiency of compressing the refrigerant.

[0062] Although the embodiments have been described above, the embodiments are not limited to the above. The above-described components include those that can be easily imagined by a person skilled in the art, those that are substantially the same, and those that are within the so-called equivalent range. Furthermore, the above-described components can be appropriately combined. Furthermore, at least one of various omissions, substitutions, and modifications of the components can be made without departing from the gist of the embodiments. [Explanation of symbols]

[0063] 1: Rotary compressor 10: Compressor housing 11: Motor 12: Compression section 15: Drive shaft 18: Lubricating oil 121T: Upper cylinder (cylinder) 121S: Lower cylinder (other cylinder) 125T: Upper piston (piston) 125S: Lower piston (other piston) 151: Secondary shaft part (3rd shaft part) 152T: Upper eccentric shaft part (eccentric shaft part) 152S: Lower eccentric shaft part (other eccentric shaft part) 153: Main shaft part (1st shaft part) 154: Intermediate shaft part (second shaft part) 155: Oil supply vertical hole 161T: Main bearing part 161S: Secondary bearing part 41: Upper eccentric shaft vertical groove 42: Upper end of vertical groove (1st axis vertical groove) 43: Bottom end of vertical groove (2nd axis vertical groove part) 44: Eccentric vertical groove part 45: Upper eccentric shaft partial oil supply hole (oil supply hole) 46: Straight line 47: Rotation axis 51:Rotation direction 52: Upper eccentric shaft maximum eccentric position point (maximum eccentric position point) 53: Starting line

Claims

1. A compressor housing; A drive shaft disposed inside the compressor housing; A motor that rotates the drive shaft about a rotation axis; a compression unit that compresses a refrigerant by rotation of the drive shaft, The drive shaft is a first shaft portion rotatably supported by a bearing portion; A second shaft portion; an eccentric shaft portion disposed between the first shaft portion and the second shaft portion, The compression section includes: A cylinder; a piston that revolves within a cylinder chamber formed inside the cylinder by the rotation of the drive shaft, the piston having a hole that fits into the eccentric shaft portion, The drive shaft has an eccentric longitudinal groove portion formed on an outer peripheral surface of the eccentric shaft portion facing an inner peripheral surface of a hole formed in the piston; a first shaft longitudinal groove portion formed on an outer peripheral surface of the first shaft portion, connected to one end of the eccentric longitudinal groove portion, and facing an inner peripheral surface of a hole formed in the bearing portion; a second shaft longitudinal groove portion formed on an outer peripheral surface of the second shaft portion and connected to the other end of the eccentric longitudinal groove portion; a vertical oil supply hole formed along the rotation shaft; An oil-feed horizontal hole is formed connecting the oil-feed vertical hole and the eccentric vertical groove portion. Rotary compressor.

2. The ratio B / A obtained by dividing the area of ​​a cross section where the eccentric longitudinal groove portion intersects with a plane perpendicular to the rotation shaft by the area of ​​a cross section where the horizontal oil feed hole intersects with a plane perpendicular to the straight line along which the horizontal oil feed hole intersects is expressed by the following formula: 0.4≦B / A≦1 Fulfill The rotary compressor according to claim 1 .

3. The angle of rotation from a starting line intersecting the maximum eccentric position point farthest from the rotation axis on the outer circumferential surface of the eccentric shaft portion and starting at the rotation axis to a moving radius intersecting the eccentric longitudinal groove portion and starting at the rotation axis in the rotation direction of the drive shaft around the rotation axis is greater than -180 degrees and less than 0 degrees. The rotary compressor according to claim 1 or 2.

4. The drive shaft is a third shaft portion rotatably supported by another bearing portion; and another eccentric shaft portion disposed between the second shaft portion and the third shaft portion, The compression section includes: Other cylinders, a piston that revolves within a cylinder chamber that is formed within the cylinder by rotation of the drive shaft, the piston having a hole that fits into the eccentric shaft portion, The drive shaft has another eccentric longitudinal groove portion formed on an outer peripheral surface of the other eccentric shaft portion facing an inner peripheral surface of a hole formed in the other piston; a third shaft longitudinal groove portion formed on an outer peripheral surface of the second shaft portion and connected to one end of the other eccentric longitudinal groove portion; a fourth shaft longitudinal groove portion formed on an outer peripheral surface of the third shaft portion, connected to the other end of the other eccentric longitudinal groove portion, and facing an inner peripheral surface of a hole formed in the other bearing portion; Another horizontal oil-feed hole is further formed to connect the vertical oil-feed hole and the other eccentric vertical groove portion. The rotary compressor according to any one of claims 1 to 3.

5. The ratio B' / A' obtained by dividing the area of ​​a cross section where the other eccentric longitudinal groove portion intersects with a plane perpendicular to the rotation shaft by the area of ​​a cross section where the other horizontal oil-feed hole intersects with a plane perpendicular to the straight line along which the other horizontal oil-feed hole intersects is expressed by the following formula: 0.4≦B′ / A′≦1 Fulfill The rotary compressor according to claim 4.

6. The angle of rotation from a starting line intersecting the other maximum eccentric position point farthest from the rotation axis on the outer circumferential surface of the other eccentric shaft portion and starting at the rotation axis to a moving radius intersecting the other eccentric longitudinal groove portion and starting at the rotation axis in the rotation direction of the drive shaft around the rotation axis is greater than -180 degrees and less than 0 degrees. The rotary compressor according to claim 4 or 5.

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