ROTARY COMPRESSOR
A rotary compressor includes: a sealed vertical compressor housing in which a refrigerant discharging unit is provided at an upper part, a refrigerant intake unit is provided at a lower part, and lubricant oil is retained; a compressing unit that is disposed in the compressor housing, includes an upper end plate and a lower end plate that block an annular cylinder and end portions of the cylinder, and discharges a refrigerant sucked from the intake unit through the discharging unit by compressing the refrigerant in the cylinder; and a motor that is disposed in the compressor housing, includes a cylindrical stator and a rotor that is fixed to a rotation axis to rotate in the stator, and drives the compressing unit via the rotation axis.
This application is based upon and claims the benefit of priority of the prior Japanese Patent Application No. 2015-067242, filed on Mar. 27, 2015, the entire contents of which are incorporated herein by reference.
FIELDThe present invention relates to a rotary compressor used in an air conditioner or a refrigerating machine.
BACKGROUNDIn the rotary compressor, if compressive strain is generated in a stator of a motor disposed in a compressor housing, magnetization characteristics of the stator are degraded to cause an increase in iron loss, and thus the efficiency of the motor is lowered.
For example, Japanese Laid-open Patent Publication No. 2010-255623 (Patent Document 1) discloses a compressor that includes a sealed vessel, a motor including at least a stator and a rotor and disposed in the sealed vessel, and a compression mechanism including at least an axis driven by the rotor. In the compressor, the outer diameter of the compression mechanism is greater than the outer diameter of the stator, and the compressor further includes a ring-shaped fixation member which is inserted between the sealed vessel and the outer diameter of the stator to be fixed to the outer circumference of the stator through an interference fit, and is welded to the sealed vessel at three locations.
In addition, Patent Document 1 discloses a compressor that includes a sealed vessel, a motor including at least a stator and a rotor and disposed in the sealed vessel, and a compression mechanism including at least an axis driven by the rotor. In the compressor, the outer diameter of the compression mechanism is greater than the outer diameter of the stator, and the compressor further includes a throttle part which is obtained by subjecting a part of the sealed vessel to drawing processing and of which the drawn part is in contact with the stator, the throttle part being fixed to the stator by laser welding.
Furthermore, Japanese Laid-open Patent Publication No. 2008-248889 (Patent Document 2) discloses a compressor that includes an annular stator, a rotor disposed in an internal space of the stator to be rotatable, and a sealed vessel including a cylindrical portion that accommodates the stator and the rotor, in which the stator and the cylindrical portion are fixed to each other at three or more locations in a circumferential direction by spot welding, in a state where a clearance of 0.01 mm to 0.30 mm is secured between an outer circumferential surface of the stator and an inner circumferential surface of the cylindrical portion. The compression mechanism of the compressor is screwed to a mounting plate, and the mounting plate is spot-welded to the cylindrical portion of the sealed vessel.
However, in the compressor disclosed in Patent Document 1 that includes a ring-shaped fixation member which is inserted between the sealed vessel and the outer diameter of the stator to be fixed to the outer circumference of the stator through an interference fit, and is welded to the sealed vessel at three locations, the ring-shaped fixation member is fixed to the outer circumference of the stator through an interference fit. Therefore, there is a problem in that compressive strain is generated in the stator, and thus, the efficiency of the motor is lowered. In addition, there is also a problem in that the costs for the use of the fixation member are increased.
In addition, in the compressor disclosed in Patent Document 1 which includes a throttle part which is obtained by subjecting a part of the sealed vessel to drawing processing and of which the drawn part is in contact with the stator, and in which the throttle part is fixed to the stator by laser welding, a part of the sealed vessel is subjected to drawing processing. Therefore, there is a problem in that the costs for the drawing processing are increased.
Furthermore, in the compressor disclosed in Patent Document 2, the stator and the cylindrical portion are fixed to each other at three or more locations in a circumferential direction by spot welding, in a state where a radial clearance of 0.01 mm to 0.30 mm is secured between the stator and the cylindrical portion, the compression mechanism is screwed to a mounting plate, and the mounting plate is spot-welded to the cylindrical portion of the sealed vessel. Therefore, in a case where a radial clearance of 0.30 mm is provided between a stator and a cylindrical portion, there is a problem in that since the radial clearance is too large, it is necessary to perform centering of the stator with respect to the cylindrical portion, and thus assembly work is increased. In addition, since the compression mechanism is fixed to the cylindrical portion via the mounting plate, there is a problem in that costs for the use of the mounting plate are increased.
SUMMARYAccording to an aspect of the embodiments, a rotary compressor includes: a sealed vertical compressor housing in which a refrigerant discharging unit is provided at an upper part, a refrigerant intake unit is provided at a lower part, and lubricant oil is retained; a compressing unit that is disposed in the compressor housing, includes an upper end plate and a lower end plate that block an annular cylinder and end portions of the cylinder, and discharges a refrigerant sucked from the intake unit through the discharging unit by compressing the refrigerant in the cylinder; and a motor that is disposed in the compressor housing, includes a cylindrical stator and a rotor that is fixed to a rotation axis to rotate in the stator, and drives the compressing unit via the rotation axis. In a case where an inner diameter of a body unit of the compressor housing is φDm, an outer diameter of the upper end plate of the compressing unit is φDb, and an outer diameter of the stator of the motor is φDs, φDm, φDb, and φDs are set such that two expressions of −0.05 mm≦φDm−φDb≦0.05 mm and 0.1 mm≦φDm−φDs≦0.2 mm are satisfied, and an outer circumferential portion of the upper end plate and an outer circumferential portion of the stator are respectively spot-welded to the body unit of the compressor housing at a plurality of sites separated in a circumferential direction.
The object and advantages of the invention will be realized and attained by means of the elements and combinations particularly pointed out in the claims.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory and are not restrictive of the invention.
Hereinafter, an embodiment (example) of the invention will be described in detail with reference to the drawings.
As illustrated in
A stator 111 of the motor 11 is formed in a cylindrical shape and is fixed to an inner circumferential surface of a body unit 10A of the compressor housing 10 by spot welding. A dimensional relationship and an assembly method of the body unit 10A of the compressor housing 10 and the stator 111 which are characteristic configurations of the rotary compressor 1 of the invention will be described below. A rotor 112 is disposed in the cylindrical stator 111 and is fixed to the rotation axis 15 by shrink-fitting which mechanically connects the motor 11 and the compressing unit 12.
The compressing unit 12 includes a first compressing unit 12S and a second compressing unit 12T. As illustrated in
As illustrated in
In the first cylinder 121S, the first vane groove 128S is formed along the entire height of the cylinder in a radial direction away from the first cylinder inner wall 123S. A flat first vane 127S is slidably fitted in the first vane groove 128S. In the second cylinder 121T, the second vane groove 128T is formed along the entire height of the cylinder in the radial direction away from the second cylinder inner wall 123T. A flat second vane 127T is slidably fitted in the second vane groove 128T.
As illustrated in
At the time of activating the rotary compressor 1, the first vane 127S protrudes away from the first vane groove 128S into the first cylinder chamber 130S due to the repulsive force of the first vane spring 126S. A tip end of the first vane 1275 is in contact with an outer circumferential surface of the first annular piston 125S, and by the first vane 127S, the first cylinder chamber 1305 is divided into a first inlet chamber 131S and a first compression chamber 133S. Similarly, the second vane 127T protrudes away from the second vane groove 128T into the second cylinder chamber 130T due to the repulsive force of the second vane spring 126T. A tip end of the second vane 127T is in contact with an outer circumferential surface of the second annular piston 125T, and the second cylinder chamber 130T is divided by the second vane 127T into a second inlet chamber 131T and a second compression chamber 133T.
In addition, in the first cylinder 121S, a first pressure guiding-in path 129S is formed which communicates with the outer side of the first vane groove 128S in the radial direction and the inside of the compressor housing 10 via an opening portion R (refer to
The first inlet hole 135S, that causes the first inlet chamber 131S and an external unit to communicate with each other, is provided in the first side-flared portion 122S of the first cylinder 121S in order to suck the refrigerant from the external unit into the first inlet chamber 131S. The second inlet hole 135T, that causes the second inlet chamber 131T and the external unit to communicate with each other, is provided in the second side-flared portion 122T of the second cylinder 121T in order to suck the refrigerant from the external unit into the second inlet chamber 131T. The cross sectional shapes of the first inlet hole 135S and the second inlet hole 135T are circles.
As illustrated in
A lower end plate 160S is disposed on the lower end portion of the first cylinder 121S and blocks the first cylinder chamber 130S of the first cylinder 121S. In addition, an upper end plate 160T is disposed on the upper end portion of the second cylinder 121T and blocks the second cylinder chamber 130T of the second cylinder 121T. The lower end plate 160S blocks the lower end portion of the first cylinder 121S and the upper end plate 160T blocks the upper end portion of the second cylinder 121T.
A sub-bearing unit 161S is formed on the lower end plate 160S, and a sub-axis unit 151 of the rotation axis 15 is rotatably supported by the sub-bearing unit 161S. A main-bearing unit 161T is formed on the upper end plate 160T, and a main-axis unit 153 of the rotation axis 15 is rotatably supported by the main-bearing unit 161T.
The rotation axis 15 includes a first eccentric portion 152S and a second eccentric portion 152T which are eccentric to each other by deviating the phases thereof by 180°. The first eccentric portion 152S is rotatably fitted in the first annular piston 125S of the first compressing unit 12S. The second eccentric portion 152T is rotatably fitted in the second annular piston 125T of the second compressing unit 12T.
If the rotation axis 15 is rotated, the first annular piston 125S revolves along the first cylinder inner wall 123S in the first cylinder 121S in a clockwise direction in
As illustrated in
The lower muffler chamber 180S is one chamber formed in an annular shape, and is a part of a communication path which causes the discharging side of the first compressing unit 12S to communicate with the inside of an upper muffler chamber 180T through a refrigerant path 136 (refer to
As illustrated in
The cover for lower end plate 170S, the lower end plate 160S, the first cylinder 121S, and the intermediate partition plate 140 are inserted from the lower side and are fastened to the second cylinder 121T by using a plurality of penetrating bolts 175 that are screwed into female screws provided on the second cylinder 121T. The cover for upper end plate 170T and the upper end plate 160T are inserted from the upper side and are fastened to the second cylinder 121T by using a penetrating bolt 174 that is screwed into the female screw provided on the second cylinder 121T. The cover for lower end plate 170S, the lower endplate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, the upper end plate 160T, and the cover for upper end plate 170T, which are integrally fastened by using the plurality of penetrating bolts 174 and 175 and the like, configure the compressing unit 12. In the compressing unit 12, the outer circumferential portion of the upper end plate 160T is fixed to the body unit 10A of the compressor housing 10 by spot welding, and thus the compressing unit 12 is fixed to the compressor housing 10. The dimensional relationship of the upper end plate 160T and the body unit 10A will be described below.
The low pressure refrigerant of a refrigerant circuit is guided to the first compressing unit 12S through an accumulator (not illustrated) and the first inlet hole 135S (refer to
A discharge pipe 107 as a discharging unit that is connected to the refrigerant circuit and discharges the high pressure refrigerant to a condenser side of the refrigerant circuit is connected to the top of the compressor housing 10. That is, the first outlet 190S and the second outlet 190T are connected to the condenser of the refrigerant circuit.
In the compressor housing 10, the lubricant oil is enclosed approximately up to the height of the second cylinder 121T. In addition, the lubricant oil is sucked through a lubricating pipe 16, which is attached to the lower end portion of the rotation axis 15, by a pump impeller (not illustrated) inserted into a lower portion of the rotation axis 15, and circulates in the compressing unit 12, thereby performing lubrication between sliding components (the first annular piston 125S and the second annular piston 125T) and performing sealing of a minute gap of the compressing unit 12.
Next, the characteristic configuration of the rotary compressor 1 of the example will be described with reference to
As illustrated in
As illustrated in
Next, a method of fixing the motor 11 and the compressing unit 12 that are connected to each other via the rotation axis 15, in the body unit 10A of the compressor housing 10 will be described. As illustrated in
The compressing unit 12 in which the rotor 112 is fixed to the rotation axis 15 is lowered by placing the rotor 112 downward so that the end portion of the rotation axis 15 comes into contact with an upper convex portion 202 of the gap gage 200. If the compressing unit 12 is further lowered, the rotor 112 is guided to the shim 201 of the gap gage 200 and is inserted into the stator 111 so that the gap gage 200 is pushed downward. As illustrated in
Next, as illustrated in
Next, a method of fixing the upper end plate 160T of the compressing unit 12 and the stator 111 of the motor 11 to the body unit 10A of the compressor housing 10 will be described with reference to
The motor 11 which is centered by the compressing unit 12 and the gap gage 200 is positioned in the body unit 10A to be fixed by firstly welding the body unit 10A and the upper end plate 160T. The stator 111 is directly welded to the body unit 10A in a state of being centered and in a state of not receiving compressive force in the radial direction from the body unit 10A. Therefore, the compressive strain is not generated in the stator 111, and thus the magnetization characteristics of the stator are not degraded so that iron loss is not increased. As a result, the efficiency of the motor 11 is high and it is possible to suppress an increase in costs.
In addition, the stator 111 is fixed to the body unit 10A by spot welding at the position of the stator 111 on the compressing unit 12 side and the position of the stator 111 symmetrical to the position on the compressing unit 12 side. Therefore, even if the rotary compressor 1 receives impact such as falling, the stator 111 is not damaged due to the dislocation of the caulking, which is between the welding position on the compressing unit 12 side and the position symmetrical to the welding position on the compressing unit 12 side, of the stator 111 that is formed by caulking the stacked steel sheets. Furthermore, as illustrated in
After the compressing unit 12 and the motor 11 are welded to be fixed to the body unit 10A, if a bottom 100 and a top 10B are welded to the body unit 10A by full circle welding as illustrated in
Hereinbefore, the example has been described, but the example is not limited by the contents described above. In addition, the components described above include those that can be easily conceived by those skilled in the art, those that are substantially identical thereto, and those in a scope of so-called equivalents. In addition, the components described above can be appropriately combined. Furthermore, at least one of various omission, replacement, and modification of the components can be performed without departing from the gist of the example.
According to an aspect of the embodiments, in a case where the inner diameter of the body unit of the compressor housing is φDm, the outer diameter of the upper end plate of the compressing unit is φDb, and the outer diameter of the stator of the motor is φDs, φDm, φDb, and φDs are set such that two expressions of −0.05 mm≦φDm−φDb≦0.05 mm and 0.1 mm ≦φDm−φDs≦0.2 mm are satisfied, and the outer circumferential portion of the upper end plate and the outer circumferential portion of the stator are respectively spot-welded to the body unit of the compressor housing at a plurality of sites separated in the circumferential direction. Therefore, the compressive strain is not generated in the stator of the motor disposed in the compressor housing, and thus the magnetization characteristics of the stator are not degraded. As a result, the efficiency of the motor is high and it is possible to suppress an increase in costs.
All examples and conditional language recited herein are intended for pedagogical purposes of aiding the reader in understanding the invention and the concepts contributed by the inventors to further the art, and are not to be construed as limitations to such specifically recited examples and conditions, nor does the organization of such examples in the specification relate to a showing of the superiority and inferiority of the invention. Although the embodiments of the present invention have been described in detail, it should be understood that the various changes, substitutions, and alterations could be made hereto without departing from the spirit and scope of the invention.
Claims
1. A rotary compressor comprising:
- a sealed vertical compressor housing in which a refrigerant discharging unit is provided at an upper part, a refrigerant intake unit is provided at a lower part, and lubricant oil is retained;
- a compressing unit that is disposed in the compressor housing, includes an upper end plate and a lower end plate that block an annular cylinder and end portions of the cylinder, and discharges a refrigerant sucked from the intake unit through the discharging unit by compressing the refrigerant in the cylinder; and
- a motor that is disposed in the compressor housing, includes a cylindrical stator and a rotor that is fixed to a rotation axis to rotate in the stator, and drives the compressing unit via the rotation axis,
- wherein, in a case where an inner diameter of a body unit of the compressor housing is φDm, an outer diameter of the upper end plate of the compressing unit is φDb, and an outer diameter of the stator of the motor is φDs, φDm, φDb, and φDs are set such that two expressions of −0.05 mm≦φDm−φDb≦0.05 mm and 0.1 mm≦φDm−φDs≦0.2 mm are satisfied, and an outer circumferential portion of the upper end plate and an outer circumferential portion of the stator are respectively spot-welded to the body unit of the compressor housing at a plurality of sites separated in a circumferential direction.
2. The rotary compressor according to claim 1, wherein the spot welding between the stator of the motor and the body unit of the compressor housing is performed after the spot welding between the upper end plate of the compressing unit and the body unit.
3. The rotary compressor according to claim 2, wherein the spot welding between the stator of the motor and the body unit of the compressor housing is performed in a state where centering between the stator and the rotor of the motor is performed.
Type: Application
Filed: Mar 24, 2016
Publication Date: Sep 29, 2016
Inventors: Yuji KOMAI (Kanagawa), Naoya MOROZUMI (Kanagawa)
Application Number: 15/080,328