JP2012107587A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make the diameter of a compressing chamber relatively larger than the inner diameter of a casing.SOLUTION: The compressor includes the casing 2 and a cylinder 50 arranged in the inside of the first cylindrical part 3a which is part of the casing 2 in the radial direction and having the compression chamber 51, the center axis B1 of the compression chamber 51 does not coincide with the center axis A1 of the first cylindrical part 3a. Consequently, the distance between the peripheral wall face of the compression chamber and the inner peripheral surface of the casing can be made larger in a part in a peripheral direction than in the other part.

Description

  The present invention relates to a compressor having a cylinder in which a compression chamber is formed.

  Conventionally, a compressor having a cylinder, a piston disposed in the cylinder, a shaft on which the piston is mounted, a motor that rotationally drives the shaft, and a cylindrical casing that accommodates these is known as a compressor. The piston has a roller mounted on the eccentric portion of the shaft and a blade that protrudes radially outward from the outer peripheral surface of the roller, and the cylinder is provided with the roller. It has a compression chamber and a concave blade accommodating portion formed radially outward from the peripheral wall surface of the compression chamber. In this compressor, the central axis of the compression chamber and the rotation axis of the shaft are provided coaxially. Further, since the outer peripheral surface of the motor is fixed to the inner peripheral surface of the casing and the shaft is disposed at the center of the motor, the central axis of the compression chamber and the central axis of the casing are provided coaxially. .

JP 2009-281305 A

  In the conventional compressor, since the central axis of the compression chamber and the central axis of the casing are provided coaxially, the distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is the same over the entire circumference. . Therefore, when the diameter of the casing is reduced without changing the diameter of the compression chamber to reduce the size of the compressor, or the diameter of the compression chamber is increased without changing the diameter of the casing to increase the capacity of the compression chamber. The distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is shortened. At this time, since the blade accommodating portion is formed radially outward from the peripheral wall surface of the compression chamber, the length of the outer portion of the blade accommodating portion is the shortest, and the strength of this portion is significantly reduced. .

  Moreover, as compressors other than the compressor mentioned above, the cylinder which has a compression chamber and the vane accommodating part formed toward the radial direction from the surrounding wall surface, the roller arrange | positioned in a compression chamber, and arrangement | positioning at a vane accommodating part A compressor having a vane whose tip is pressed against the outer peripheral surface of the roller is known, but the same problem occurs in this compressor.

  Then, an object of this invention is to provide the compressor which can make the diameter of a compression chamber relatively large with respect to the internal diameter of a casing.

  In order to solve the above-described problem, a compressor according to a first aspect of the present invention includes a casing, and a cylinder that is provided radially inside a first cylindrical portion that is a part of the casing and has a compression chamber. The center axis of the compression chamber and the center axis of the first cylindrical portion do not coincide with each other.

  In this compressor, since the central axis of the compression chamber and the central axis of the first cylindrical portion which is a part of the casing do not coincide with each other, the distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is It can be larger in one part of the direction than the other part. Therefore, by appropriately providing a portion having a large distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing, the central axis of the compression chamber and the central axis of the cylindrical portion of the casing as in a conventional compressor are provided. Compared to the case of being provided on the same axis, the diameter of the compression chamber can be made relatively larger than the inner diameter of the casing.

  A compressor according to a second invention is the compressor according to the first invention, wherein the cylinder has a recess formed radially outward from a peripheral wall surface of the compression chamber. A central axis is located between the central axis of the compression chamber and the recess.

  In this compressor, a portion having a large distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is provided in a portion corresponding to the concave portion, thereby ensuring the length of the outer portion of the concave portion in the cylinder. The diameter of the compression chamber can be relatively increased with respect to the inner diameter. Therefore, when the diameter of the compression chamber is relatively increased with respect to the inner diameter of the casing, it is possible to suppress the strength of the portion of the cylinder on the outer side in the radial direction from decreasing.

  A compressor according to a third invention is the compressor according to the first or second invention, wherein the casing includes a cylindrical casing body and two lid portions that close both ends of the casing body, The diameter of the main body is constant over the cylinder axis direction.

  In this compressor, since the casing body is cylindrical with a constant diameter, it is easy to manufacture the casing.

  A compressor according to a fourth invention is the compressor according to the third invention, wherein the motor includes a rotor through which the shaft is inserted, and a stator disposed radially outside the rotor. Has a plurality of concave core cut portions formed on the outer peripheral surface thereof, and is formed in a region opposite to the central axis of the compression chamber with respect to the central axis of the casing when viewed from the axial direction. Further, at least one of the core cut portions is larger than the core cut portion formed in a region on the central axis side of the compression chamber with respect to the central axis of the casing.

  In this compressor, the space between the core cut portion formed on the outer peripheral surface of the stator and the inner peripheral surface of the casing is used as an oil return passage for returning the lubricating oil to the lower portion of the casing. At least one of the core cut portions formed in the portion where the distance between the peripheral wall surface of the chamber and the inner peripheral surface of the casing is large can be made larger than the core cut portion formed on the opposite side. Therefore, the oil return passage can be provided efficiently in terms of space.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, since the center axis of the compression chamber and the center axis of the first cylindrical portion which is a part of the casing do not coincide with each other, the distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is It can be made larger in the circumferential direction than in other parts. Therefore, by appropriately providing a portion having a large distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing, the central axis of the compression chamber and the central axis of the cylindrical portion of the casing as in a conventional compressor are provided. Compared to the case of being provided on the same axis, the diameter of the compression chamber can be made relatively larger than the inner diameter of the casing.

  In the second aspect of the invention, by providing a portion where the distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is large in the portion where the recess is formed, the length of the outer portion of the recess in the cylinder is secured. The diameter of the compression chamber can be relatively increased with respect to the inner diameter of the casing. Therefore, when the diameter of the compression chamber is relatively increased with respect to the inner diameter of the casing, it is possible to suppress the strength of the portion of the cylinder on the outer side in the radial direction from decreasing.

  In 3rd invention, since a casing main body is a cylindrical shape with a fixed diameter, it is easy to manufacture a casing.

  In the fourth invention, the space between the core cut portion formed on the outer peripheral surface of the stator and the inner peripheral surface of the casing is used as an oil return passage for returning the lubricating oil to the lower portion of the casing. At least one of the core cut portions formed in the portion where the distance between the peripheral wall surface of the compression chamber and the inner peripheral surface of the casing is large can be made larger than the core cut portion formed on the opposite side. Therefore, the oil return passage can be provided efficiently in terms of space.

It is sectional drawing of the compressor which concerns on embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is a top view of the insulator with which the compressor shown in FIG. 1 is provided. It is the IV-IV sectional view taken on the line of FIG. (A) is the same figure as FIG. 4, (b) is sectional drawing of the compressor of a comparative example, (c) is sectional drawing of the conventional compressor. (A) is the same figure as FIG. 4, (b) is sectional drawing of the compressor of a comparative example, (c) is sectional drawing of the conventional compressor. It is sectional drawing of the compressor which concerns on other embodiment of this invention, Comprising: It is a figure corresponded in FIG. It is sectional drawing of the compressor which concerns on other embodiment of this invention, Comprising: It is a figure corresponded in FIG. It is sectional drawing of the compressor which concerns on other embodiment of this invention, Comprising: It is a figure corresponded in FIG. It is sectional drawing of the compressor which concerns on other embodiment of this invention, Comprising: It is a figure corresponded in FIG. (A) is a top view of the cylinder with which the compressor which concerns on other embodiment of this invention is provided, (b) is a top view of the cylinder with which the conventional compressor is provided.

  Hereinafter, embodiments of the present invention will be described.

<Overall configuration of compressor 1>
As shown in FIG. 1, the compressor 1 of the present embodiment includes a casing 2, a compression mechanism 40 and a drive mechanism 10 disposed in the casing 2. The compressor 1 is used by being incorporated in a refrigeration cycle such as an air conditioner, for example, and compresses a refrigerant (CO2 in this embodiment) introduced from a suction pipe (not shown) and discharges it from a discharge pipe 6. In the following description of the compressor 1, the vertical direction in FIG. 1 is simply referred to as the vertical direction. FIG. 1 is a cross-sectional view taken along the line I-I in FIGS.

<Configuration of casing 2>
The casing 2 includes a cylindrical casing body 3 that extends in the vertical direction, and lids 4 and 5 that block the upper and lower openings of the casing body 3. The casing body 3 is provided with a suction pipe (not shown) for introducing the refrigerant into the compressor 1, and the upper lid 4 has a discharge pipe 6 for discharging the compressed refrigerant, A terminal terminal 7 for supplying a current to a coil 15 of a stator 14 (to be described later) of the drive mechanism 10 is provided. In FIG. 1, wiring for connecting the coil 15 and the terminal terminal 7 is omitted. Further, in the lower part of the casing 2, lubricating oil L for smoothing the operation of the sliding portion of the compression mechanism 40 is stored.

The casing body 3 is formed in a cylindrical shape, and its diameter is constant over the cylinder axis direction. As will be described later, a cylinder 50 and a core 20 are arranged inside the casing body 3, and a portion on the radially outer side of the cylinder 50 in the casing body 3 is a first cylindrical portion 3 a, and the casing body 3 A radially outer portion of the core 20 is referred to as a second cylindrical portion 3b. Then, as shown in FIG. 1, the central axis A2 of the central axis A1 and the second cylindrical portion 3b of the first cylindrical portion 3a is positioned on the axis C _A is the first reference axis.

<Configuration of Drive Mechanism 10>
The drive mechanism 10 includes a shaft 11 and a motor 12 that rotationally drives the shaft 11. The motor 12 includes a substantially cylindrical rotor 13 in which magnets are embedded, and a substantially cylindrical stator 14 disposed on the radially outer side of the rotor 13 via an air gap. The upper portion of the shaft 11 is inserted inside the rotor 13. The central axis of the inner peripheral surface of the stator 14 B2 is provided on the axis C _B is the second reference axis, the central axis of the second cylindrical portion 3b of the casing main body 3 A2 (the axis C _A) Does not match.

  The stator 14 is wound around the substantially cylindrical core 20 fixed to the inner peripheral surface of the casing body 3, two insulators 30, 30 disposed at both upper and lower ends of the core 20, and the core 20 and the insulator 30. And a coil 15.

  As shown in FIG. 2, the core 20 includes an annular portion 21 and nine teeth portions 22 that protrude radially inward from the inner peripheral surface of the annular portion 21. In FIG. 2, the shaft 11 and the rotor 13 are omitted. The annular portion 21 has a substantially cylindrical shape, and the outer peripheral surface thereof is fixed to the inner peripheral surface of the second cylindrical portion 3b of the casing body 3 by spot welding or the like. The nine teeth portions 22 are provided on the inner peripheral surface of the annular portion 21 at equal intervals in the circumferential direction. The protruding lengths from the inner peripheral surface of the annular portion 21 of the nine teeth portions 22 are all the same. An insulating film (not shown) for insulating the core 20 and the coil 15 is provided on the inner peripheral surface of the annular portion 21 and the side surface of the tooth portion 22.

  Further, nine concave core cut portions 21 a to 21 i are formed on the outer peripheral surface of the annular portion 21 side by side in the circumferential direction. The space above and below the motor 12 communicates with the space surrounded by the core cut portions 21a to 21i and the inner peripheral surface of the casing body 3 (hereinafter referred to as the oil return passage 23). The oil return passage 23 is used as a passage through which the lubricating oil L and the refrigerant are passed.

Further, in a plan view, a straight line connecting the deepest portion and the axis C _A of the core cut portions 21a to 21i, the intersection between the inner circumferential surface of the casing body 3 and P. The size of the core-cut portions 21a~21i, the more the distance between the corresponding point P and the axis C _B is long, is formed to be larger. The size of the core cut portion is the size of the opening area along the horizontal direction of the oil return passage 23. The core cutting unit 21a~21i is formed symmetrically with respect to a plane E1 which includes the axis _{C A} and axis _{C B.}

  As shown in FIG. 1, the two insulators 30 and 30 arranged above and below the core 20 have the same configuration except for the installation direction. The insulator 30 is made of an insulating resin material having high heat resistance and is provided to insulate the core 20 and the coil 15 from each other. As shown in FIG. 3, the insulator 30 includes an annular portion 31 and nine projecting portions 32 that project radially inward from the inner peripheral surface of the annular portion 31. The inner diameter of the annular portion 31 is substantially the same as the annular portion 21 of the core 20, and the outer diameter of the annular portion 31 is smaller than the annular portion 21 of the core 20. The nine protruding portions 32 are provided at equal intervals in the circumferential direction, and are respectively disposed so as to face the teeth portion 22 of the core 20. The protruding portion 32 has substantially the same shape as the tooth portion 22 of the core 20 as viewed from above, and has a semicircular plate portion 32a at the protruding tip. As shown in FIG. 3, nine cutout portions 31 a are formed on the outer peripheral surface of the annular portion 31 so as not to block the core cut portions 21 a to 21 i of the annular portion 21.

  As shown in FIGS. 1 and 2, the coil 15 is wound around a tooth portion 22 and two projecting portions 32 disposed above and below the tooth portion 22. The coil 15 is wound around each tooth portion 22, and the winding method of the coil 15 is so-called concentrated winding. When a current is supplied to the coil 15, an electromagnetic force is generated, and the rotor 13 is rotated by the electromagnetic force. Note that the winding method of the coil 15 is not limited to concentrated winding, and may be so-called distributed winding.

As shown in FIG. 1, the shaft 11 is fixed to the rotor 13 and rotates integrally with the rotor 13. As shown in FIGS. 1 and 4, the shaft 11 has an eccentric portion 11 a at a position in the compression chamber 51 described later. The eccentric part 11a has a substantially cylindrical shape, and its central axis is eccentric with respect to the rotation axis (axis C _B ) of the shaft 11. A roller 61 (described later) of the compression mechanism 40 is attached to the outer peripheral surface of the eccentric portion 11a.

  As shown in FIG. 1, an oil supply passage 11 b extending in the vertical direction is formed inside the lower half of the shaft 11. A spiral blade-shaped pump member (not shown) for sucking the lubricating oil L into the oil supply passage 11b as the shaft 11 rotates is inserted into the lower end portion of the oil supply passage 11b. Further, the shaft 11 is formed with a plurality of discharge holes 11 c for discharging the lubricating oil L in the oil supply passage 11 b to the outside of the shaft 11. In FIG. 4, the oil supply passage 11b of the shaft 11 is omitted.

<Configuration of compression mechanism 40>
As shown in FIG. 1, the compression mechanism 40 is disposed on the cylinder 50, the piston 60 disposed inside the cylinder 50, the front head 41 disposed on the upper side of the cylinder 50, and the upper side of the front head 41. A muffler 42 and a rear head 43 disposed below the cylinder 50 are provided.

  As shown in FIG. 4, the cylinder 50 is a substantially annular member, and the outer peripheral surface thereof is fixed to the inner peripheral surface of the first cylindrical portion 3 a of the casing body 3 by spot welding or the like. In the cylinder 50, a compression chamber 51, a blade accommodating portion (recessed portion) 52, a suction hole 53, and a plurality of oil return holes 54 (see FIG. 1) are formed. In FIG. 4, the plurality of oil return holes 54 are omitted. The compression chamber 51 is a circular hole. The upper and lower openings of the compression chamber 51 are closed by the front head 41 and the rear head 43, respectively. The blade accommodating portion 52 is formed in a concave shape from the peripheral wall surface of the compression chamber 51 toward the radially outer side. The suction hole 53 is provided for introducing the refrigerant into the compression chamber 51, and the tip of a suction pipe (not shown) is fitted therein. The oil return hole 54 is formed on the outer side in the radial direction of the front head 41 as viewed from above and below. Although not shown, the plurality of oil return holes 54 are formed side by side in the circumferential direction.

In the compressor 1 of this embodiment, the center axis B1 of the compression chamber 51 is provided on the axis C _B, it does not coincide with the center axis A1 of the first cylindrical portion 3a of the cylinder 50. Further, as shown in FIG. 4, the blade accommodating portion 52 is formed at a position opposite to the central axis B <b> 1 of the compression chamber 51 with respect to the central axis A <b> 1 of the first cylindrical portion 3 a of the casing body 3. . That is, the central axis A 1 of the first cylindrical portion 3 a of the casing body 3 is located between the central axis B 1 of the compression chamber 51 and the blade accommodating portion 52.

  Therefore, the distance between the compression chamber 51 and the first cylindrical portion 3a of the casing body 3 is not the same over the entire circumference, but is the largest in the portion where the blade accommodating portion 52 is formed. Let this maximum distance be D1. The inner diameter of the casing body 3 is R1, the diameter r1 of the compression chamber 51, and the length of the radially outer portion of the blade housing portion 52 in the cylinder 50 is L1.

First, the case where the diameter of the casing is reduced without changing the diameter of the compression chamber in order to reduce the size of the compressor will be described with reference to FIG.
FIG. 5C is a cross section of a conventional compressor 801. In the compressor 801, the central axis of the compression chamber 851 and the central axis of the casing body 803 are provided coaxially. Further, the inner diameter R8 of the casing body 803 is larger than the inner diameter R1 of FIG. 5A which is the present embodiment, and the diameter of the compression chamber 851 and the length of the radially outer portion of the blade accommodating portion 852 in the cylinder 850 are the same. This is the same as r1 and L1 in FIG.
FIG. 5B shows a comparative example, and the compression when the inner diameter of the casing body 803 of the compressor 801 shown in FIG. 5C is reduced to the same size (R1) as in this embodiment. A cross section of the machine 701 is shown. The diameter of the compression chamber 751 of the compressor 701 remains the same as r1 in FIG.
When the inner diameter of the casing main body is reduced while maintaining the state where the central axis of the compression chamber 751 and the central axis of the casing main body 703 are coaxially provided as in this comparative example, the blade accommodating portion 752 in the cylinder 750 is reduced. Since the length L7 of the radially outer portion is shorter than that of the conventional compressor 801, sufficient strength cannot be ensured.
On the other hand, in the present embodiment, the inner diameter of the casing body is reduced by preventing the central axis of the compression chamber 51 and the central axis of the casing body 3 (3a) from being provided coaxially. However, the inner diameter of the casing body can be made smaller than that of the conventional compressor 801 while the length L1 of the radially outer portion of the blade accommodating portion 52 in the cylinder 50 is ensured to be equal to that of the conventional compressor 801.

Next, a case where the diameter of the compression chamber is increased without changing the diameter of the casing in order to increase the capacity of the compression chamber will be described with reference to FIG.
FIG. 6C is a cross section of a conventional compressor 901. In the compressor 901, the central axis of the compression chamber 951 and the central axis of the casing body 903 are provided coaxially. Further, the diameter r9 of the compression chamber 951 is smaller than the diameter r1 of FIG. 5A, which is the present embodiment, and the inner diameter of the casing body 903 and the length of the radially outer portion of the blade housing portion 952 in the cylinder 950 are This is the same as R1 and L1 in FIG.
FIG. 6B shows a comparative example, and the compressor when the diameter of the compression chamber 951 of the compressor 901 shown in FIG. 6C is increased to the same size (r1) as in this embodiment. A cross section 701 is shown. The inner diameter of the casing main body 703 of the compressor 701 remains the same as R1 in FIG.
When the diameter of the compression chamber is increased while maintaining the state where the central axis of the compression chamber 751 and the central axis of the casing main body 703 are provided coaxially as in this comparative example, the blade accommodating portion 752 in the cylinder 750 is maintained. Since the length L7 of the radially outer portion is shorter than that of the conventional compressor 901, sufficient strength cannot be ensured.
On the other hand, in the present embodiment, the diameter of the compression chamber is increased as in the comparative example by preventing the central axis of the compression chamber 51 and the central axis of the casing body 3 (3a) from being provided coaxially. However, the diameter of the compression chamber can be made larger than that of the conventional compressor 901 while the length L1 of the radially outer portion of the blade accommodating portion 52 in the cylinder 50 is ensured to be equal to that of the conventional compressor 901.
Thus, the compressor 1 of the present embodiment has a diameter of the compression chamber 51 with respect to the inner diameter of the casing body 3 as compared with the case where the center axis of the compression chamber and the center axis of the casing body 3 are provided coaxially. The ratio can be increased. That is, the diameter of the compression chamber 51 can be relatively increased with respect to the inner diameter of the casing body 3.

  As shown in FIG. 4, the piston 60 includes an annular roller 61 and a blade 62 extending radially outward from the outer peripheral surface of the roller 61. The roller 61 is mounted in the compression chamber 51 so as to be rotatable relative to the outer peripheral surface of the eccentric portion 11a. The blade 62 is movably disposed between a pair of bushes 63 disposed in the blade accommodating portion 52. The pair of bushes 63 is formed in a shape in which a substantially cylindrical member is divided into half. The pair of bushes 63 can swing in the blade housing portion 52 with the blade 62 disposed therebetween. Therefore, the blade 62 can advance and retreat in the blade accommodating portion 52 and can swing around the pair of bushes 63.

  As shown in FIG. 1, the front head 41 is fixed to the upper end surface of the cylinder 50 and closes the upper opening of the compression chamber 51. The shaft 11 is rotatably inserted into the front head 41. Further, the front head 41 is formed with a discharge hole 41a (see FIG. 4) for discharging the refrigerant compressed in the compression chamber 51. 4 is a cross-sectional view taken along line IV-IV in FIG. 1, and the discharge hole 41a of the front head 41 does not originally appear, but is shown for convenience of explanation. The front head 41 is attached with a valve mechanism (not shown) that opens and closes the outlet of the discharge hole 41c according to the pressure in the compression chamber 51.

  The muffler 42 is provided in order to reduce noise associated with refrigerant discharge. The muffler 42 is disposed above the front head 41 and forms a muffler space M between the front head 41 and the muffler 42. The muffler 42 is formed with a muffler discharge port 42a for discharging the refrigerant in the muffler space M.

  The rear head 43 is fixed to the lower end surface of the cylinder 50 and closes the lower opening of the compression chamber 51. The shaft 11 is rotatably inserted into the rear head 43.

<Operation of Compressor 1>
Next, the operation of the compressor 1 will be described.
When the shaft 11 is rotated by driving the motor 12 while supplying the refrigerant from the suction hole 53 into the compression chamber 51, the roller 61 attached to the eccentric portion 11 a is in contact with the peripheral wall surface of the compression chamber 51 in the circumferential direction. Moving. As a result, the volume of the space formed by the side surface of the piston 60 and the peripheral wall surface of the compression chamber 51 changes, so that the refrigerant is compressed in the compression chamber 51.

  When the pressure in the compression chamber 51 becomes equal to or higher than a predetermined pressure, a valve mechanism (not shown) provided in the front head 41 opens, and the refrigerant in the compression chamber 51 enters the muffler space M through the discharge hole 41c. Discharged. The refrigerant discharged into the muffler space M is discharged from the muffler discharge port 42a to the outside of the compression mechanism 40, and then passes through an air gap between the stator 14 and the rotor 13 to be finally discharged. It is discharged out of the casing 2 from the pipe 6.

  At this time, part of the lubricating oil L discharged into the compression chamber 51 from the discharge hole 11c of the shaft 11 is discharged out of the compression mechanism 40 together with the refrigerant. A part of the lubricating oil L discharged out of the compression mechanism 40 moves to the space above the motor 12 together with the refrigerant, and then the oil return passage 23 (the core cut portions 21a to 21i and the inner peripheral surface of the casing body 3). And the oil return hole 54 of the front head 41, and returned to the lower part of the casing 2. In addition, the other part of the lubricating oil L discharged outside the compression mechanism 40 passes through the oil return hole 54 of the front head 41 and moves to the lower part of the casing 2 without moving to the space above the motor 12. Returned.

<Characteristics of compressor 1>
In the compressor 1 of the present embodiment described above, since the central axis B1 of the compression chamber 51 and the central axis A1 of the first cylindrical portion 3a of the casing body 3 do not coincide with each other, the compression chamber 51 in a part in the circumferential direction. The distance between the peripheral wall surface and the inner peripheral surface of the casing body 3 can be made larger than that of other portions.
In the present embodiment, since the center axis A1 of the first cylindrical portion 3a of the casing body 3 is located between the center axis B1 of the compression chamber 51 and the blade accommodating portion 52, the compression chamber 51 and the casing body 3 are arranged. , The distance D1 of the portion where the blade accommodating portion 52 is formed can be made the longest.
Therefore, compared with a conventional compressor (see FIGS. 5 (c) and 6 (c)) in which the central axis of the compression chamber and the central axis of the cylindrical portion of the casing are provided coaxially, the blade is accommodated. The diameter of the compression chamber 51 can be relatively increased with respect to the inner diameter of the casing body 3 (first cylindrical portion 3a) while ensuring the distance D1 of the portion where the portion 52 is formed equally.
Therefore, the casing main body 3 (first cylindrical portion 3a) is secured while ensuring the length L1 of the radially outer portion of the blade accommodating portion 52 in the cylinder 50 to be equal to that of the conventional compressor and ensuring the strength of this portion. The diameter of the compression chamber 51 can be made relatively large with respect to the inner diameter.

Further, in the present embodiment, the size of the core-cut portions 21a~21i, the more the distance between the corresponding point P and the axis C _B is long, is formed to be larger. Therefore, the oil return passage 23 formed by the core cut portion and the inner peripheral surface of the casing body 3 can be provided efficiently in terms of space.
Further, the total opening area along the horizontal direction of the nine oil return passages 23 is the same as that of the present embodiment in the diameter of the casing body and the diameter of the compression chamber, and the central axis of the compression chamber and the casing body 3 are the same. It is possible to secure the same level as the case where the center axis matches. That is, the amount of oil passing through the nine oil return passages 23 can be maintained at the same level as in the above case.

  As mentioned above, although embodiment of this invention was described, it should be thought that the specific structure of this invention is not limited to the said embodiment. The scope of the present invention is shown not only by the description of the above-described embodiment but also by the scope of claims for patent, and further includes meanings equivalent to the scope of claims for patent and all modifications within the scope. Note that the modifications described below can be implemented in appropriate combination.

  The distance between the central axis A1 of the first cylindrical portion 3a of the casing body 3 and the central axis B1 of the compression chamber 51 is not limited to that shown in FIG. However, when the central axis A1 of the first cylindrical portion 3a of the casing body 3 is located between the central axis B1 of the compression chamber 51 and the blade accommodating portion 52, the axis A1 may be located in the compression chamber 51. preferable.

In the above embodiment, the size of the core-cut portions 21a~21i the size of a distance between the corresponding point P and the axis C _B is long, have been formed to be larger, nine core cut portions However, the present invention is not limited to this configuration.
For example, as the core 120 shown in FIG. 7, perpendicular to the plane E1 containing the axis _{C A} and axis _{C B,} and a plane passing through the axis _{C A,} when the plane F1, axis _{C B} to this plane F1 At least one of the core cut portions 121a~121d formed on the opposite side of the region (Fig. 7, the core cut portions 121b, 121c) is formed in a region of the axis _{C B} side with respect to the plane F1 What is necessary is just to be larger than the core cut parts 21e-21i which are. That is, when viewed from the vertical direction (axial direction), at least one of the core cut part formed on the opposite side of the region between the axis C _B with respect to the central axis A2 of the casing main body 3, the central axis A2 of the casing main body 3 it is larger than the core cut portions formed in the region of the axis C _B side against. According to this configuration, at least one of the core cut portions formed in the portion where the distance between the peripheral wall surface of the compression chamber 51 and the inner peripheral surface of the casing body 3 is larger than the core cut portion formed on the opposite side. Can be big. Therefore, the oil return passage 123 can be provided efficiently in terms of space.

  Further, the core cut portions 21a to 21i may all have the same size.

  In the above embodiment, the outer peripheral surface of the cylinder 50 is fixed to the inner peripheral surface of the casing body 3, but the outer peripheral surface of the front head 41 or the rear head is fixed to the inner peripheral surface of the casing body 3 instead of the cylinder 50. May be. In this case, for example, as shown in FIG. 8, the cylinder 250 has a shape in which a part of the outer peripheral surface protrudes radially outward, and the blade accommodating portion 52 and the suction hole 53 are formed in the protruding portion 251a. .

  The compression mechanism 40 of the above embodiment has a configuration in which a piston 60 composed of a roller 61 and a blade 62 is arranged inside a cylinder 50. For example, as shown in FIG. And the vane 361 may be arranged. The cylinder 350 includes a compression chamber 351, a vane housing portion (recess portion) 352 formed in a concave shape from the peripheral wall surface of the compression chamber 351 toward the radially outer side, a suction hole 353, and a plurality of oil return holes (not shown). ) Is formed. The central axis A1 of the first cylindrical portion 3a of the casing body 3 is located between the central axis B301 of the compression chamber 351 and the vane accommodating portion 352. The roller 360 is mounted on the outer peripheral surface of the eccentric portion 11a. The vane 361 is urged by an urging spring 362 provided in the vane accommodating portion 352, and the tip is pressed against the outer peripheral surface of the roller 360. When the shaft 11 is rotated, the roller 360 moves in the circumferential direction while being in contact with the peripheral wall surface of the compression chamber 351, and the space formed by the outer peripheral surface of the roller 360, the side surface of the vane 361, and the peripheral wall surface of the compression chamber 351. Since the volume changes, the refrigerant is compressed in the compression chamber 351.

In the above embodiment, the casing body 3 has a cylindrical shape with a constant diameter. For example, like the casing body 403 of the casing 402 shown in FIG. The diameter of the portion 403d may be different. The portion 403 c includes a first cylindrical portion 403 a on the radially outer side of the cylinder 50, and the portion 403 d includes a second cylindrical portion 403 b on the radially outer side of the core 420. However, in terms of ease of manufacture of the casing, it is preferable that the casing body 3 has a cylindrical shape with a constant diameter, as in the above embodiment. The central axis A401 of the first cylindrical portion 3a does not coincide with the central axis B401 of the compression chamber 51. Specifically, the axis A401 is located between the axis B401 and the blade accommodating portion. Axis A401 is provided on the axis _{C A,} the center axis B401 of the compression chamber 51 is provided on the axis _{C B} which coincides with the axis of rotation of the shaft 11.

In this modified embodiment, as shown in FIG. 10, the center axis A402 of the second cylindrical portion 403b may be provided on the axis C _B. According to this structure, the conventional motor whose outer peripheral surface and inner peripheral surface are coaxial can be used as it is.

  In the above embodiment, the refrigerant compressed in the compression chamber 51 is discharged from the compression mechanism 40 through the discharge hole 41 c formed in the front head 41 and the muffler space M, and then discharged from the discharge pipe 6. However, for example, as shown in FIG. 11A, the refrigerant compressed in the compression chamber 551 is provided in the casing body (not shown) via the discharge passage 554 formed in the cylinder 550. It may be configured to be discharged from a discharge pipe (not shown). The discharge channel 554 is configured by connecting a discharge hole 554c, a discharge chamber 554b, and a discharge hole 554a in this order from the compression chamber 551 side. The discharge chamber 554b penetrates the cylinder 550 in the vertical direction. The upper and lower openings of the discharge chamber 554b are closed by a front head (not shown) and a rear head (not shown). The discharge chamber 554b is provided with a valve mechanism 555 that opens and closes the outlet of the discharge hole 554a in accordance with the pressure in the compression chamber 551. An end of a discharge pipe (not shown) is fitted into the discharge hole 554a. Therefore, the length of the discharge hole 554a needs to be long enough to fit the discharge pipe.

In the case of this modification, as shown in FIG. 11A, the central axis A501 of the first cylindrical portion of the casing body (not shown) is coaxial with the central axis of the outer peripheral surface of the cylinder 550. The central axis B501 may be located between the blade housing portion 552 and the discharge flow channel 554. According to this configuration, as shown in FIG. 11 (b), the outer side in the radial direction of the blade accommodating portion 552 in the cylinder 550 compared to the case where the central axis of the compression chamber 1051 and the central axis of the outer peripheral surface of the cylinder 1050 are coaxial. The length L5 of the part can be increased. Further, the length of the discharge channel 554 can be made longer than the discharge channel 1054 of the cylinder 1050 shown in FIG. Therefore, the size of the discharge chamber 554b (opening area along the horizontal direction) can be made larger than that of the discharge chamber 1054b shown in FIG.
In FIG. 11A, the central axis A501 of the first cylindrical portion of the casing body is located on the left side in the drawing with respect to the straight line G5 connecting the central axis B501 of the compression chamber 551 and the center of the blade accommodating portion 552. However, it may be on the straight line G5.

  Although the compressor 1 of the said embodiment is a 1 cylinder type, you may apply this invention to a 2 cylinder type compressor.

  If the present invention is used, the diameter of the compression chamber can be relatively increased with respect to the inner diameter of the casing.

DESCRIPTION OF SYMBOLS 1 Compressor 2, 402 Casing 3, 403 Casing main body 3a, 403a 1st cylindrical part 3b, 403b 2nd cylindrical part 4, 5 Lid part 11 Shaft 12 Motor 13 Rotor 14 Stator 20, 120, 420 Core 21a ˜21i, 121a˜121i, core cut part 50, 250, 350, 550 cylinder 51, 351, 551 compression chamber 52, 552 Blade housing part (concave part)
352 Vane receiving part (concave part)
A1, A401, A501 Central axis A2, A402 of the first cylindrical part B1, B301, B401, B501 of the second cylindrical part The central axis of the compression chamber

Claims (4)

A casing,
A cylinder provided in the radial direction of the first cylindrical portion that is a part of the casing, and having a compression chamber;
The compressor characterized in that the central axis of the compression chamber does not coincide with the central axis of the first cylindrical portion. The cylinder has a recess formed radially outward from a peripheral wall surface of the compression chamber;
2. The compressor according to claim 1, wherein a central axis of the first cylindrical portion is located between a central axis of the compression chamber and the concave portion. The casing has a cylindrical casing body and two lid portions that close both ends of the casing body,
The compressor according to claim 1 or 2, wherein a diameter of the casing body is constant over a cylinder axis direction. The motor includes a rotor through which the shaft is inserted, and a stator disposed on the radially outer side of the rotor,
The stator has a plurality of concave core cut portions formed on the outer peripheral surface thereof,
When viewed from the axial direction, at least one of the core cut portions formed in a region opposite to the central axis of the compression chamber with respect to the central axis of the casing is at least one of the compression chambers with respect to the central axis of the casing. The compressor according to claim 3, wherein the compressor is larger than the core cut portion formed in a region on the central axis side.

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