CN114729641A - Rotary compressor and refrigeration cycle device - Google Patents
Rotary compressor and refrigeration cycle device Download PDFInfo
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- CN114729641A CN114729641A CN201980102293.5A CN201980102293A CN114729641A CN 114729641 A CN114729641 A CN 114729641A CN 201980102293 A CN201980102293 A CN 201980102293A CN 114729641 A CN114729641 A CN 114729641A
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- spring guide
- fitting
- vane
- rotary compressor
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- 238000005057 refrigeration Methods 0.000 title claims description 13
- 230000002093 peripheral effect Effects 0.000 claims abstract description 33
- 238000003780 insertion Methods 0.000 claims description 26
- 230000037431 insertion Effects 0.000 claims description 26
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 230000002265 prevention Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 description 28
- 238000007906 compression Methods 0.000 description 28
- 239000003507 refrigerant Substances 0.000 description 24
- 230000004048 modification Effects 0.000 description 14
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- 238000000034 method Methods 0.000 description 9
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- 238000010586 diagram Methods 0.000 description 2
- 230000005489 elastic deformation Effects 0.000 description 2
- 230000004907 flux Effects 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 239000010721 machine oil Substances 0.000 description 2
- 229920001289 polyvinyl ether Polymers 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
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- 238000007599 discharging Methods 0.000 description 1
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- 229920001971 elastomer Polymers 0.000 description 1
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- 238000004146 energy storage Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 229920005862 polyol Polymers 0.000 description 1
- -1 polyol ester Chemical class 0.000 description 1
- 230000003449 preventive effect Effects 0.000 description 1
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- 229920005989 resin Polymers 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The rotary compressor comprises: the rotary vane pump comprises a closed container, an annular cylinder accommodated in the closed container, a rotary piston eccentrically rotating along the inner circumferential surface of the cylinder, vanes reciprocating in vane grooves arranged in the cylinder in the radial direction, and vane springs for applying force to the vanes to enable the front ends of the vanes to abut against the rotary piston. The rotary compressor further includes a spring guide having a cylindrical portion in which the blade spring is fixed, and a fitting convex portion protruding outward from an outer peripheral surface of one end side of the cylindrical portion. The cylinder is formed with a cylindrical fitting recess that is open on the outer peripheral surface side of the cylinder and has a bottom portion that communicates with the vane grooves. The fitting recess has a retaining piece for retaining the fitting projection of the spring guide. The rotary compressor has the following structure: the spring guide is rotated in a state where one end of the spring guide on the side where the fitting projection is formed is inserted into and fitted into the fitting recess of the cylinder through the opening formed in the closed container, and the fitting projection is locked to the anti-slip piece, thereby fixing the spring guide to the cylinder.
Description
Technical Field
The present invention relates to a rotary compressor and a refrigeration cycle device used in an air conditioner, a refrigerator, a freezer, or the like.
Background
The rotary compressor comprises: the rotary piston is eccentrically rotated in the cylinder, and the vane is slidably disposed in a vane groove provided in the cylinder. The vane is urged by a vane spring so that the tip of the vane is always in contact with the rotary piston, and the space inside the cylinder is divided into a low-pressure space and a high-pressure space. Then, the rotary piston eccentrically moves in the cylinder, whereby the volume of the low-pressure space is reduced to become a high-pressure space, and the refrigerant sucked into the cylinder is compressed.
In such a hermetic compressor, the vane spring that biases the vane is housed in a vane spring insertion hole formed in the cylinder and held in the cylinder. In the structure in which the leaf spring is held in the cylinder in this way, the length of the leaf spring is limited by the distance between the end surface on the rear end side of the leaf and the inner circumferential surface of the sealed container, and cannot be longer than this distance. Therefore, when the vane moves to the rearmost top dead center position of the reciprocating motion, the entire length of the vane spring reaches the close contact length at which the vane spring contracts to the maximum, and the stress generated in the vane spring increases, which may cause fatigue failure of the vane spring.
Therefore, there are techniques as follows: a space for housing the leaf spring is secured outside the sealed container, and the restriction on the length of the leaf spring is eliminated, thereby preventing fatigue failure due to excessive stress applied to the leaf spring (see, for example, patent document 1). Patent document 1 has a structure in which a cylindrical spring guide accommodating a leaf spring is joined to a cylinder from the outside of a closed container. The spring guide has the following structure: two slits are provided at the end of the cylinder body on the side of joining, two connecting pieces capable of elastic displacement in the radial direction are formed, and a separation preventing piece projecting outward is provided at the tip of each of the two connecting pieces. The two connecting pieces of the spring guide are elastically deformed radially inward and inserted into a spring insertion hole provided in the cylinder, and the retaining piece is engaged with a peripheral edge of the spring insertion hole after passing through the spring insertion hole, thereby fixing the spring guide to the spring insertion hole.
Patent document 1: japanese Kokoku publication Sho-51-030005
In the rotary compressor of patent document 1, the fixing is performed by elastic deformation of the two connecting pieces of the spring guide, and when each retaining piece passes through the spring insertion hole, the retaining piece is pressed in a direction of expanding the width of the vane groove, and therefore, there is a possibility that the width of the vane groove is increased. If the width of the groove of the blade is increased, the operation of the blade may become unstable.
The spring guide applies a force in a direction of being pulled out from the cylinder block by a pressure and a vibration at the time of operation of the compressor, a collision at the time of separation of the vane from the rotary piston at the time of abnormal refrigerant compression in the compression element, or the like, and a biasing force at the time of expansion and contraction of the vane spring at the time of reciprocation of the vane. Therefore, the spring guide is required to have a structure that does not come off the cylinder.
Disclosure of Invention
The present invention has been made in view of the above circumstances, and an object thereof is to provide a rotary compressor and a refrigeration cycle apparatus capable of suppressing deformation of a vane groove and suppressing disengagement of a spring guide from a cylinder block.
The rotary compressor of the present invention comprises: a closed container; an annular cylinder housed in the closed container; a rotary piston that eccentrically rotates along an inner circumferential surface of the cylinder; a vane reciprocating in a vane groove provided in the cylinder in a radial direction; a vane spring that urges the vane so that a tip end of the vane abuts against the rotary piston; and a spring guide having: the rotary compressor comprises a cylindrical part fixed with a blade spring inside and a fitting convex part protruding outwards from the outer peripheral surface of one end side of the cylindrical part, wherein a cylindrical fitting concave part which is opened at the outer peripheral surface side of the cylinder and is communicated with a blade groove at the bottom surface is formed on the cylinder, and the fitting concave part is provided with a slip-off preventing sheet for preventing the slip-off of the fitting convex part of the spring guide, and the rotary compressor comprises the following structures: in a state where the one end portion of the spring guide on the formation side of the fitting convex portion is inserted into and fitted into the fitting concave portion of the cylinder through the opening portion formed in the closed casing, the spring guide is rotated to lock the fitting convex portion to the coming-off preventing piece, and the spring guide is fixed to the cylinder.
According to the present invention, since the spring guide is fixed to the cylinder by fitting the fitting convex portion of the spring guide to the fitting concave portion of the cylinder, the pressing force in the direction of expanding the vane groove does not act. Therefore, deformation of the vane groove can be suppressed. Further, since the fitting convex portion is configured to be locked to the anti-slip piece provided in the fitting concave portion, even if a force is applied to the spring guide in a direction of being pulled out from the cylinder during operation, the spring guide can be prevented from slipping out from the cylinder.
Drawings
Fig. 1 is a sectional view showing a schematic configuration of a rotary compressor according to embodiment 1.
Fig. 2 is an enlarged cross-sectional view of a compression structure in the rotary compressor according to embodiment 1.
Fig. 3 is a perspective view of a spring guide in the rotary compressor according to embodiment 1.
Fig. 4 is an enlarged view showing a joint structure between a spring guide and a cylinder block in the rotary compressor according to embodiment 1.
Fig. 5 is a schematic perspective view of a cylinder block of the rotary compressor according to embodiment 1.
Fig. 6 is a view showing a cylinder block of the rotary compressor according to embodiment 1.
Fig. 7 is a view showing an end surface portion of the cylinder block of the rotary compressor according to embodiment 1, the end surface portion being divided by the vane grooves and the fitting recesses.
Fig. 8 is a view showing a spring guide of the rotary compressor according to embodiment 1.
Fig. 9 is a view showing modification 1 of the stopper of the rotary compressor according to embodiment 1.
Fig. 10 is a perspective view of the cylinder block of fig. 9.
Fig. 11 is a view showing a modification 2 of the stopper of the rotary compressor according to embodiment 1.
Fig. 12 is a diagram showing a refrigerant circuit of the refrigeration cycle apparatus according to embodiment 2.
Detailed Description
In the present embodiment, a rotary compressor used in an air conditioner, a refrigerator, a freezer, or the like will be described as an example.
(embodiment mode 1)
Fig. 1 is a sectional view showing a schematic configuration of a rotary compressor according to embodiment 1. Fig. 2 is an enlarged cross-sectional view of a compression mechanism in the rotary compressor according to embodiment 1. Fig. 3 is a perspective view of a spring guide in the rotary compressor according to embodiment 1. Fig. 4 is an enlarged view showing a joint structure between a spring guide and a cylinder block in the rotary compressor according to embodiment 1. In this specification, when the cylinder block is referred to as "radial direction", "circumferential direction", and "axial direction", unless otherwise specified, the cylinder block is referred to as "radial direction", "circumferential direction", and "axial direction", respectively.
The rotary compressor 1 includes, in the interior of the hermetic container 5: electric element 25, compression element 10 for compressing the refrigerant, and rotation shaft 17 for transmitting the driving force of electric element 25 to compression element 10.
As shown in fig. 1, the closed casing 5 is a substantially cylindrical closed casing. The thickness of the closed casing 5 is set to such a degree that the closed casing 5 is not deformed by the internal pressure of the refrigerant compressed by the compression element 10. Further, by making the thickness of the closed casing 5 thick, it is possible to make it difficult for the influence of the deformation of the closed casing 5 due to heating to be applied to the compression element 10 when the rotary compressor 1 is mounted to an apparatus such as an air conditioner or a refrigerator by arc spot welding, for example.
An accumulator 28 for attenuating refrigerant sound is provided outside the sealed container 5, adjacent to the sealed container 5. The accumulator 28 is connected to each of two compression mechanisms constituting the compression element 10, which will be described later, via an accumulator tube 29. A discharge pipe 16 for discharging the refrigerant compressed by the compression element 10 is connected to an upper portion of the closed casing 5. A refrigerating machine oil for lubricating the compression element 10 is stored in the bottom of the closed casing 5. As the refrigerating machine oil, POE (polyol ester), PVE (polyvinyl ether), AB (alkylbenzene), or the like is used as a synthetic oil.
The electric element 25 includes: a cylindrical stator 26 fixed to the inner peripheral surface of the closed casing 5, and a cylindrical rotor 27 rotatably disposed inside the stator 26. The stator 26 is formed to have an outer diameter larger than the inner diameter of the sealed container 5, and is fixed to the inner circumferential surface of the sealed container 5 by shrink fitting. The rotor 27 has magnetic poles formed by permanent magnets. The rotor 27 is rotated by the action of magnetic flux generated by magnetic poles on the rotor 27 and magnetic flux generated by the stator 26.
The electromotive element 25 and the compression element 10 are coupled to each other via the rotary shaft 17, the rotation of the electromotive element 25 is transmitted to the compression element 10, and the compression element 10 compresses the refrigerant by the transmitted rotational force. The refrigerant compressed by the compression element 10 passes through a discharge port 21 (see fig. 2) provided in the compression element 10 and is discharged into the closed casing 5. Therefore, the closed casing 5 is filled with the compressed high-temperature and high-pressure refrigerant gas.
The compression element 10 includes: two compression mechanisms disposed in the axial direction of the rotary shaft 17, an upper bearing 18, a lower bearing 19, and the intermediate plate 12. That is, the compression element 10 is a multi-cylinder type including two compression mechanisms. The rotary compressor 1 is not limited to a multi-cylinder type having a plurality of compression mechanisms, and may be a single-cylinder type having one compression mechanism.
Since the compression mechanisms are configured similarly, only one will be described for convenience. As shown in fig. 2, the compression mechanism includes: cylinder 11, rotary piston 13, vane 14, vane spring 15, and spring guide 30 having vane spring 15 fixed therein.
The cylinder 11 is formed of an annular flat plate. Both ends in the axial direction of the cylinder chamber 11a inside the cylinder block 11 are open, and are closed by the intermediate plate 12 and one of the upper bearing 18 and the lower bearing 19. As shown in fig. 2 and 4, the cylinder 11 is formed with a suction port 20 penetrating in the radial direction and a discharge port 21 formed in the inner circumferential surface 11b of the cylinder 11. An accumulator tube 29 of the accumulator 28 is connected to the intake opening 20.
As shown in fig. 2, the rotary piston 13 is housed in the cylinder chamber 11a of the cylinder 11 in a state of being rotatably fitted to the eccentric portion 17a of the rotary shaft 17. The rotary piston 13 eccentrically rotates along the inner peripheral surface 11b of the cylinder 11.
The cylinder block 11 is formed with vane grooves 22 that communicate with the cylinder chamber 11a and extend in the radial direction. The vane 14 is disposed in the vane groove 22 to be movable forward and backward in the radial direction. A leaf spring 15 is disposed on the back surface 14b side of the leaf 14. A receiving recess for receiving an end of the leaf spring 15 is formed in the back surface 14b of the leaf 14. Fig. 2 shows a cross section of the accommodation recess, and the end of the leaf spring 15 is fixed to the bottom surface of the accommodation recess.
The vane spring 15 biases the vane 14 so that the tip end 14a of the vane 14 abuts on the rotary piston 13. The vane 14 is pressed radially inward by the urging force of the vane spring 15, and the tip end portion 14a of the vane 14 is constantly in contact with the rotary piston 13. As described above, the tip end portion 14a of the vane 14 abuts against the rotary piston 13, whereby the inside of the cylinder chamber 11a is partitioned into a low-pressure space and a high-pressure space. The vane 14 reciprocates in the vane groove 22 with the tip end portion 14a kept in contact with the outer peripheral surface 13c of the rotary piston 13 as the rotary piston 13 rotates eccentrically in the cylinder chamber 11a.
The leaf spring 15 is a coil spring formed by spirally winding a wire material such as metal. The blade spring 15 has an expansion portion 15a which expands and contracts with the movement of the blade 14, and a non-expansion portion 15b which is provided at an end portion of the expansion portion 15a in the expansion and contraction direction and does not expand and contract. The non-stretchable portion 15b is not stretched by winding the wires to a diameter larger than that of the stretchable portion 15a and the wires are in close contact with each other.
The leaf spring 15 is fixed in the tubular spring guide 30 at the non-expansion portion 15b. The outer diameter of the non-stretchable portion 15b is formed larger than the inner diameter of the spring guide 30, and the diameter of the non-stretchable portion 15b is reduced by pressing the non-stretchable portion 15b into the spring guide 30, so that the leaf spring 15 is fixed in the spring guide 30 by a restoring force for restoring the diameter. The fixation of the leaf spring 15 to the spring guide 30 is not limited to this fixation method, and may be the following method.
The leaf spring 15 may be fixed to the spring guide 30 by providing a circumferential groove in the inner peripheral surface of the spring guide 30 and fitting the non-expansion portion 15b into the circumferential groove. Further, a spiral groove that matches the wire diameter of the leaf spring 15 may be provided on the inner circumferential surface of the spring guide 30, and the leaf spring 15 may be fixed to the spring guide 30 by fitting the non-stretchable portion 15b of the leaf spring 15 into the spiral groove. In addition, when the number of turns of the non-stretchable portion 15b of the leaf spring 15 is one, it is sufficient as follows. The inner peripheral surface of the spring guide 30 is provided with a single-turn groove corresponding to the wire diameter of the leaf spring 15, and the leaf spring 15 is fixed to the spring guide 30 by fitting the non-stretchable portion 15b of the leaf spring 15 into the single-turn groove.
The spring guide 30 is made of an iron material. The spring guide 30 is not limited to a high-strength material such as an iron material, and may be made of a low-strength material such as resin. One end 30a of the spring guide 30 is fitted into the cylinder 11, and the other end 30b protrudes outside the closed casing 5 through the opening 8 provided in the closed casing 5.
As shown in fig. 3, the spring guide 30 includes a cylindrical portion 31 and a fitting convex portion 32 that protrudes outward from an outer peripheral surface of one end side of the cylindrical portion 31. The leaf spring 15 is fixed inside the cylindrical portion 31. The fitting projections 32 are arc-shaped projections along the outer peripheral surface of the cylindrical portion 31, and two are formed symmetrically with respect to the central axis of the spring guide 30. The fitting convex portion 32 is used for fitting with a fitting concave portion 40, which will be described later, provided in the cylinder 11. In the spring guide 30, the one end portion 30a side is inserted into the closed casing 5 through the opening 8 provided in the closed casing 5, and the fitting convex portion 32 is inserted into and fitted into the fitting concave portion 40 provided in the cylinder 11. The structure of the spring guide 30 fitted into the cylinder 11 will be described in detail again.
A blade passing portion 31a is formed at one end of the cylindrical portion 31. The blade passing portion 31a is formed of a slit extending from one end of the cylindrical portion 31 in the axial direction of the cylindrical portion 31, and two blade passing portions are formed symmetrically with respect to the central axis of the cylindrical portion 31. As shown in fig. 4, the vane passage portion 31a is positioned on an extension line in the radial direction of the vane groove 22 in a state where the spring guide 30 is fixed to the cylinder 11, so that the vane 14 reciprocates in the vane passage portion 31a.
Here, the dimensions of the spring guide 30 will be explained. The diameter D1 of the cylindrical portion 31 is smaller than the axial length of the blade 14 (the length in the direction perpendicular to the paper surface of fig. 4). The width W1 in the radial direction of the blade passing portion 31a is larger than the width of the blade 14 in the same direction. Thus, after passing through the vane groove 22, the vane 14 enters the vane passage portion 31a without contacting the vane passage portion 31a and reciprocates.
The amount L1 of protrusion of the spring guide 30 from the outer peripheral surface 11c of the cylinder 11 is set to the following range. The projection amount L1 is set to exceed the first length and be equal to or less than the second length. The first length is obtained by adding "the distance between the back surface 14b of the vane 14 and the outer peripheral surface 11c of the cylinder 11 when the vane 14 is at the top dead center position after moving rearward" to "the contact length of the vane spring 15". The second length is obtained by adding "the entire length of the blade 14" to "the entire length of the blade spring 15 in the natural state". The contact length of the leaf spring 15 is a length of the leaf spring 15 in a state where the wires are in contact with each other while being contracted to the maximum.
The spring guide 30 to which the leaf spring 15 is fixed is disposed in the protruding portion 6, and the protruding portion 6 is provided so as to protrude outward of the closed casing 5. The protruding portion 6 is a cylindrical member having a circular, rectangular or oblong cross-sectional shape. As shown in fig. 2, the protrusion 6 is attached to the opening 8 formed in the sealed container 5 such that the center axis of the protrusion 6 is perpendicular to the center axis of the cylinder 11. The protruding portion 6 is fixed to the closed casing 5 by pressing the end of the protruding portion 6 into the opening 8 formed in the closed casing 5.
A lid 7 is attached to an end portion (hereinafter referred to as an outer circumferential end portion) of the protruding portion 6 opposite to the side fixed to the closed casing 5. The lid 7 is a lid that closes the outer circumferential end of the protrusion 6. The lid 7 is joined to the outer peripheral end of the protrusion 6 by welding, brazing, or the like, for example. The protruding portion 6 is sealed by closing the outer peripheral end of the protruding portion 6 with the lid 7, and the sealed container 5 is sealed.
In embodiment 1, the leaf spring 15 is fixed to the cylinder 11 after being fixed to the spring guide 30. The outer diameter of the cylindrical portion 31 of the spring guide 30 is smaller than the inner diameter of the opening 8 of the closed casing 5, so that the spring guide 30 is fixed to the cylinder 11 without contacting the closed casing 5. Here, if the end portion of the leaf spring 15 is fixed to the lid portion 7 without providing the spring guide 30, the leaf spring 15 cannot be provided with high accuracy. The outer contour of the rotary compressor 1 is composed of the closed casing 5, the protruding portion 6, and the lid portion 7, and the internal pressure caused by the refrigerant discharged from the compression element 10 acts on these outer contour components. The outer contour component changes in shape such as bulging outward under the influence of the internal pressure. Therefore, if the leaf spring 15 is fixed to the outer-ring component, the leaf spring 15 cannot be positioned at the target position, that is, at a position along the direction perpendicular to the center axis of the cylinder 11, due to the deformation of the outer-ring component caused by the internal pressure.
In contrast, in embodiment 1, the leaf spring 15 is fixed to the spring guide 30, which is a member different from the outer-profile component member, and the spring guide 30 is fixed to the cylinder 11. Therefore, the leaf spring 15 can be provided with high accuracy, and the leaf spring 15 can be operated stably.
(operation of rotary compressor)
Next, the operation of the rotary compressor according to embodiment 1 will be described. When electric power is supplied to the electromotive element 25, the rotation shaft 17 is rotated by the electromotive element 25. When the rotating shaft 17 rotates, the eccentric portion 17a performs an eccentric rotation motion in the cylinder chamber 11a. The eccentric rotation of the eccentric portion 17a causes the rotary piston 13 to rotate eccentrically in the cylinder chamber 11a, and the low-pressure gas refrigerant sucked into the cylinder chamber 11a from the accumulator tube 29 of the accumulator 28 is compressed. When the gas refrigerant compressed in the cylinder chamber 11a reaches a predetermined pressure, the gas refrigerant is discharged from the discharge hole 21 into the internal space of the closed casing 5. The high-pressure gaseous refrigerant discharged into the internal space of the closed casing 5 is discharged to the outside of the closed casing 5 through a discharge pipe 16 provided in the closed casing 5.
Here, the vane 14 reciprocates in the vane groove 22 in accordance with the rotation of the rotary piston 13. As shown in fig. 2, when the contact position of the outer peripheral surface 13c of the rotary piston 13 with the inner peripheral surface 11b of the cylinder 11 and the phase of the arrangement position of the vanes 14 coincide with each other (hereinafter, referred to as the rotary piston 13 being in the vane groove phase), the vanes 14 move rearward in a direction away from the cylinder 11 and are positioned at the top dead center position. When the contact position between the outer peripheral surface 13c of the rotary piston 13 and the inner peripheral surface 11b of the cylinder 11 is 180 ° out of phase with the arrangement position of the vane 14, the vane 14 moves forward in the direction toward the center of the cylinder 11, that is, is located at the bottom dead center position. Thus, the vane 14 reciprocates between the top dead center position and the bottom dead center position. When the rotary piston 13 is in the phase rotated by 90 ° from the position of fig. 2, the vane 14 is located at an intermediate position between the top dead center position and the bottom dead center position.
In this way, the reciprocating range of the vane 14 is between the top dead center position and the bottom dead center position, and the positions of the vane 14 with respect to the vane passage portion 31a of the spring guide 30 when the vane 14 is at the top dead center position, the bottom dead center position, and the intermediate position are as follows.
When the blade 14 is at the top dead center position shown in fig. 2, the back surface 14b of the blade 14 is located in the blade passing portion 31a of the spring guide 30. When the vane 14 is at the bottom dead center position, the back surface 14b of the vane 14 is not located in the vane passage portion 31a of the spring guide 30. In addition, when the blade 14 is at the intermediate position, the back surface 14b of the blade 14 is not positioned in the blade passing portion 31a of the spring guide 30. The reason for such a structure is based on the manufacturing conditions, and details thereof will be described later.
During operation of the rotary compressor 1, so-called liquid backflow may occur in which the liquid refrigerant flows into the closed casing 5. When the liquid flows back, the vane 14 is pressed radially outward because the internal pressure of the cylinder chamber 11a increases rapidly. In this case, the blade 14 moves radially outward from the top dead center position, and stops when the back surface 14b of the blade 14 comes into contact with the bottom surface 31ab of the blade passing portion 31a of the spring guide 30. That is, the bottom surface 31ab of the blade passing portion 31a functions as a stopper of the blade 14 when the liquid flows back. The radial positions of the bottom surface 31ab of the blade passing portion 31a are set as follows: the length of the leaf spring 15 does not become a close contact length in a state where the back surface 14b of the leaf 14 contacts the bottom surface 31ab of the leaf passage portion 31a. Therefore, when the internal pressure of the cylinder chamber 11a rapidly increases during liquid backflow or the like, excessive pressure does not act on the leaf spring 15.
The rotary compressor 1 according to embodiment 1 has a structure in which the protruding portion 6 is attached so as to protrude outward from the sealed container 5. Therefore, the outer contour of the rotary compressor 1 is configured to be radially enlarged with respect to the arrangement portion of the leaf spring 15 in a manner. Therefore, the distance between the back surface 14b of the vane 14 and the inner peripheral surface of the closed casing 5 is not limited, and the entire length of the vane spring 15 can be freely set. The length of the leaf spring 15 can be freely set by adjusting the length of the protruding portion 6. Therefore, the entire length of the leaf spring 15 can be extended to reduce the expansion/contraction ratio of the leaf spring 15. By reducing the expansion/contraction ratio of the leaf spring 15, the fatigue resistance against stress repeatedly acting on the leaf spring 15 can be sufficiently ensured as compared with the case of using a spring having a large expansion/contraction ratio. This can increase the biasing force with which the vane 14 is pressed against the rotary piston 13 while ensuring the fatigue resistance.
Here, if the urging force of the vane spring 15 cannot be increased and the force pressing the vane 14 against the rotary piston 13 is insufficient, the vane 14 cannot follow the movement of the rotary piston 13 when the vane 14 is at the bottom dead center position. That is, the leading end 14a of the vane 14 is separated from the rotary piston 13. In this case, noise and vibration are generated.
In contrast, in embodiment 1, since the entire length of the leaf spring 15 can be freely set as described above, the expansion and contraction rate of the leaf spring 15 can be reduced by extending the entire length of the leaf spring 15, and a sufficient fatigue resistance can be ensured. Therefore, sufficient fatigue resistance can be ensured, and the urging force necessary to constantly press the vane 14 against the rotary piston 13 can be obtained, and noise and vibration caused by the separation of the vane 14 from the rotary piston 13 can be suppressed.
In embodiment 1, the distance between the lid 7 and the spring guide 30 can be freely set by adjusting the length of the protruding portion 6, and the following effects can be obtained. When the distance between the cover 7 and the spring guide 30 is short, heat generated when the cover 7 is joined to the protruding portion 6 by welding, brazing, or the like is transmitted to the leaf spring 15 via the cover 7, and there is a possibility that the characteristics of the leaf spring 15 are deteriorated. In contrast, in embodiment 1, since the distance between the cover 7 and the spring guide 30 can be freely set, by securing the distance sufficiently, it is possible to prevent deterioration of the characteristics of the leaf spring 15 due to heat transmitted to the leaf spring 15 at the time of joining.
However, in the conventional spring guide of the rotary compressor, when the retaining piece provided in the spring guide passes through the spring insertion hole provided in the cylinder block, the retaining piece is pressed in the direction of increasing the width of the vane groove by the elastic force, and thus the spring guide may be deformed in the direction of increasing the width of the vane groove.
Therefore, in the rotary compressor 1 according to embodiment 1, the spring guide 30 is fixed to the cylinder block 11 by a fitting method described below, thereby suppressing deformation that expands the width of the vane groove 22. Hereinafter, a structure in which the spring guide 30 is fitted to the cylinder 11 will be described.
Fig. 5 is a schematic perspective view of a cylinder block of the rotary compressor according to embodiment 1. Fig. 6 is a view showing a cylinder block of the rotary compressor according to embodiment 1, wherein (a) is a front view, and (b) is a sectional view taken along line a-a of (a). Fig. 7 is a view showing an end surface portion of the cylinder block of the rotary compressor according to embodiment 1, the end surface portion being divided by the vane grooves and the fitting recesses. Fig. 8 is a view showing a spring guide of the rotary compressor according to embodiment 1, wherein (a) is a front view of an end portion on an insertion side of the spring guide, and (b) is a sectional view of the spring guide cut off on a plane including a center axis of the spring guide.
As shown in fig. 5, the cylinder 11 is provided with a cylindrical fitting recess 40 into which the spring guide 30 is fitted so as to open on the outer circumferential surface 11c side. The fitting recess 40 extends radially inward from the outer peripheral surface 11c of the cylinder block 11, and communicates with the vane groove 22 at the bottom surface 44 of the fitting recess 40. The fitting recess 40 has a blade extension groove 45 extending the blade groove 22 radially outward, and is divided into two parts, i.e., a dividing recess 40a and a dividing recess 40a, by the blade extension groove 45.
An arc-shaped retaining piece 41 protruding toward the inside of the fitting recess 40 is formed at the radially outer end of each of the divided recesses 40a of the fitting recess 40. Each of the falling-off preventive pieces 41 is formed symmetrically with respect to the central axis of the fitting recess 40. The portion of the radially outer end of the fitting recess 40 where the retaining piece 41 is not formed serves as a passage portion 42, and the passage portion 42 allows the fitting projection 32 of the spring guide 30 to pass therethrough when the spring guide 30 is fitted to the fitting recess 40.
A stopper portion 43 is provided radially inward (hereinafter, referred to as the insertion direction rear side) of the retaining piece 41 of each of the divided recesses 40a of the fitting recess 40, and the stopper portion 43 comes into contact with the fitting projection 32 of the spring guide 30 to stop the rotation of the spring guide 30. The stopper 43 prevents the spring guide 30 from rotating due to vibration or pressure generated during operation or an impact force generated when the blade 14 collides with the spring guide 30. The stop 43 also has the effect of positioning the spring guide 30. The stopper 43 is formed of a convex portion protruding from the inner peripheral surface of the divided concave portion 40a.
In the above configuration, when the spring guide 30 is fitted to the cylinder 11, the one end portion 30a of the spring guide 30 is inserted into the fitting recess 40 from the outside of the sealed container 5 through the opening 8. At this time, the fitting convex portion 32 of the spring guide 30 is inserted so as to pass through the passing portion 42 formed in the fitting concave portion 40. Then, the spring guide 30 is rotated counterclockwise with the one end portion 30a of the spring guide 30 in contact with the bottom surface 44 of the fitting recess 40. The fitting projection 32 is thereby locked to the retaining piece 41. That is, the fitting projection 32 enters the insertion direction rear side of the escape prevention piece 41 and is locked. Then, in this state, the spring guide 30 is rotated until the fitting convex portion 32 abuts against the stopper portion 43. As described above, the spring guide 30 is fitted to the cylinder 11.
Here, "the outer diameter Φ 1 of the cylindrical portion 31 of the spring guide 30 and the inner diameter Φ 2 of the circle passing through the arc-shaped inner circumferential surfaces of the retaining pieces 41" or "the outer diameter Φ 3 of the circle passing through the outer circumferential surface of the fitting convex portions 32 of the spring guide 30 and the inner diameter Φ 4 of the fitting concave portion 40 of the cylinder 11" are configured to be almost equal. Thereby, the spring guide 30 is lightly pressed into the cylinder 11, and the spring guide 30 is positioned.
In addition, in a state where the spring guide 30 is fitted to the cylinder 11, the fitting projection 32 is locked to the retaining piece 41. Therefore, when a force is applied in a direction in which the spring guide 30 is pulled out from the cylinder 11, the stopper piece 41 is caught, and the spring guide 30 can be prevented from coming out of the cylinder 11.
In order not to hinder the reciprocation of the vane 14, the spring guide 30 needs to be attached to the cylinder 11 so that the vane passage portion 31a and the vane groove 22 are in the same phase. That is, it is necessary to align the blade passing portion 31a so as to be located on the extension line of the blade groove 22. In embodiment 1, the positional relationship of each part is set as follows: the spring guide 30 is rotated until the fitting convex portion 32 abuts against the stopper portion 43, and the above-described positioning is performed. Accordingly, when the spring guide 30 is fitted, it is possible to prevent the fitting convex portion 32 of the spring guide 30 from entering the vane groove 22 and hindering the reciprocation of the vane 14 due to the excessive rotation of the spring guide 30.
The fitting and fixing structure described above is a joining method that does not use elastic force as in the conventional art, and therefore the amount of deformation of the vane groove 22 can be reduced as compared with the conventional art.
Here, the dimensions of the fixing structure of the spring guide 30 and the cylinder 11 will be described in further detail.
The depth L2 (see fig. 7) of the fitting recess 40 of the cylinder 11 is preferably short for the following reason. When the depth L2 of the fitting recess 40 is increased, the length of the vane groove 22 in the same direction, that is, the length of the portion in sliding contact with the vane 14 is shortened accordingly, and seizure is likely to occur when the vane 14 slides in the vane groove 22 at a high speed. Therefore, the depth L2 of the fitting recess 40 is preferably short, and is preferably about 1/4 of the radial width L3 (see fig. 5) of the cylinder 11.
The length L4 (see fig. 7) of the stopper 43 of the cylinder 11 in the radial direction may be equal to or shorter than the length L5 from the end surface 41a on the back side in the insertion direction of the stopper piece 41 to the bottom surface 44 of the fitting recess 40.
The stopper 43 has a maximum circumferential length (see fig. 6) obtained by subtracting the circumferential length L6 (see fig. 8) of the fitting convex portion 32 of the spring guide 30 from the circumferential length of the divided concave portion 40a. This is because, if the length of the stopper 43 in the circumferential direction is longer than this length, the fitting convex portion 32 is positioned in the blade extending groove 45 in a state where the spring guide 30 is fitted in the fitting concave portion 40, and the reciprocation of the blade 14 is inhibited. Based on the same idea, the circumferential length L6 (see fig. 8) of the fitting convex portion 32 of the spring guide 30 is at most a length obtained by subtracting the circumferential length of the stopper portion 43 from the circumferential length of the inner circumferential surface 40b of the divided concave portion 40a.
When the circumferential length L6 of the fitting convex portion 32 is set to the maximum length, the fitting length of the fitting convex portion 32 and the fitting concave portion 40 becomes long, and the rotation suppressing effect by friction between the fitting convex portion 32 and the fitting concave portion 40 and the rigidity of the fitting convex portion 32 can be improved. Conversely, if the circumferential length L6 of the fitting projection 32 is too short, the rotation suppressing effect and sufficient rigidity of the fitting projection 32 cannot be ensured. Therefore, the circumferential length L6 of the fitting convex portion 32 is preferably about 1/2 of the circumferential length of the inner circumferential surface of the divided concave portion 40a. Similarly to the above, the length of the retaining piece 41 in the circumferential direction is preferably about 1/2 of the length of the inner circumferential surface of the divided concave portion 40a in the circumferential direction.
The length L8 (see fig. 8) of the fitting projection 32 of the spring guide 30 in the insertion direction and the length L9 (see fig. 7) of the slip-off preventing piece 41 in the insertion direction are preferably about half the depth L2 of the fitting recess 40 of the cylinder 11 in order to ensure the respective rigidities.
The outer diameter Φ 3 of the circle passing through the outer peripheral surface of each fitting convex portion 32 of the spring guide 30 is equal to or less than the axial length L7 (see fig. 5) of the cylinder 11.
Next, the assembly sequence of the main parts of the rotary compressor 1 will be described. First, an integrated body in which the upper bearing 18, the two cylinders 11, the intermediate plate 12, the lower bearing 19, and the rotating shaft 17 including the two rotary pistons 13 are combined is fixed inside the closed casing 5 to which the protruding portion 6 is joined. Each cylinder 11 is fixed to the closed casing 5 at a position where the fitting recess 40 faces the opening 8 of the closed casing 5. Then, the vane 14 is inserted into the vane groove 22 of one of the two cylinders 11 fixed to the closed casing 5 from the opening end of the protruding portion 6. Next, the spring guide 30 is inserted from the opening end of the projection 6, and the one end 30a is fitted into the fitting recess 40 of the cylinder 11 as described above. Then, the leaf spring 15 is inserted and fixed to the spring guide 30. The vane 14, the spring guide 30, and the vane spring 15 are also fixed to the other cylinder 11 in the same manner. Then, the lid portion 7 is engaged with the protrusion portion 6.
In the above assembly procedure, the leaf spring 15 is fixed to the spring guide 30 after the spring guide 30 is attached to the cylinder 11, but the reverse procedure may be used. That is, after the leaf spring 15 is fixed to the spring guide 30, the spring guide 30 to which the leaf spring 15 is fixed may be attached to the cylinder 11.
Here, if the leaf spring 15 is configured such that one end of the leaf spring 15 is fixed to the back surface 14b of the leaf 14 and the other end is brought into contact with the lid 7 without providing the spring guide 30, and the leaf spring 15 is held in the protruding portion 6, it is necessary to join the lid 7 to the protruding portion 6 while pressing and holding the other end of the leaf spring 15. In contrast, in embodiment 1, since the leaf spring 15 is fixed to the spring guide 30 joined to the cylinder 11 at the time of joining the lid 7 to the protruding portion 6, it is not necessary to hold the leaf spring 15 by pressure. Therefore, the assembling property is good.
When the leaf spring 15 is fixed to the spring guide 30, the rotary shaft 17 is rotated to move the rotary piston 13 to the leaf groove phase, and the leaf 14 is moved to the bottom dead center position. Accordingly, for example, the leaf spring 15 can be provided in a state where the length of the leaf spring 15 is long, that is, in a state where the spring force acting on the leaf spring 15 is small, as compared to when the leaf 14 is located at the top dead center position, and the assembling property is good.
The rotary piston 13 in one cylinder 11 is provided 180 ° out of phase with the rotary piston 13 in the other cylinder 11. Therefore, when the rotary piston 13 in one cylinder 11 is positioned at the vane groove phase, the rotary piston 13 in the other cylinder 11 is positioned at a phase shifted by 180 ° from the vane groove phase. Therefore, when the leaf spring 15 is inserted into one of the cylinders 11, first, the rotary piston 13 is moved to a phase shifted by 180 ° from the phase of the leaf groove, and the leaf 14 is inserted into the leaf spring 15 at the bottom dead center position. When the vane spring 15 is inserted into the other cylinder 11, the rotary shaft 17 is rotated 180 °, the rotary piston 13 is similarly moved to a phase shifted by 180 ° from the vane groove phase, and the vane 14 is moved to the bottom dead center position.
When the spring guide 30 is fixed to the cylinder 11, the one end portion 30a of the spring guide 30 is rotated while being inserted into the fitting recess 40 as described above. Therefore, when the spring guide 30 is rotated, if the rear surface 14b of the blade 14 enters the blade passing portion 31a of the spring guide 30, the spring guide 30 cannot be rotated. Therefore, the spring guide 30 is rotated while the blade 14 is moved so that the back surface 14b of the blade 14 does not enter the blade passing portion 31a. Specifically, for example, the vane 14 is moved to the bottom dead center position or the intermediate position. The reason why the rear surface 14b of the vane 14 is not located in the vane passage portion 31a when the vane 14 is at the bottom dead center position or the intermediate position is to prevent the spring guide 30 from being rotated when the spring guide 30 is fixed by the screw fixing method.
In the above, the spring guide 30 is fixed to the cylinder 11 by fitting, but in order to further secure the fixation, an adhesive may be used for further fixation, or the cylinder 11 and the spring guide 30 may be welded. In either method, the deformation of the vane grooves 22 is not caused by applying an excessive stress load to the vane grooves 22 of the cylinder 11.
The rotary compressor 1 according to embodiment 1 is not limited to the above-described structure, and modifications may be made without departing from the scope of the present invention. For example, the stopper 43 may be a structure that can suppress the rotation of the spring guide 30 by contacting the fitting convex portion 32 of the spring guide 30, and may be as in the following modifications 1 to 3.
(modification 1)
Fig. 9 is a view showing modification 1 of the stopper of the rotary compressor according to embodiment 1, and is a front view showing a state in which a spring guide is fixed to a cylinder. In fig. 9, the spring guide 30 is hatched to make it easier to distinguish the spring guide 30 from the cylinder 11. Fig. 10 is a perspective view of the cylinder block of fig. 9.
The stopper 43A of modification 1 is formed of a rod-shaped pin 50. The pin 50 is inserted into a pin insertion hole 51 formed in the cylinder 11, and the tip end portion 50a contacts the side surface of the fitting projection 32. In this way, the pin 50 contacts the side surface of the fitting projection 32, thereby suppressing the rotation of the spring guide 30. In this example, the left-turn rotation of the spring guide 30 can be suppressed.
The stopper 43 shown in fig. 9 and 10 may be combined with the structure of modification 1. That is, in addition to the configuration shown in fig. 9 and 10, the convex portion constituting the stopper portion 43 may be further provided in the divided concave portion 40a on the opposite side to the side where the pin 50 is inserted, among the divided concave portions 40a of the fitting concave portion 40.
(modification 2)
Fig. 11 is a view showing a modification 2 of the stopper of the rotary compressor according to embodiment 1. Fig. 11 shows an end surface portion of the cylinder block 11 divided by the vane grooves 22 and the fitting recess 40.
The stopper 43B of modification 2 is formed of a sheet-like elastic body 60. The elastic body 60 is used by being inserted into a gap formed in front and rear of the insertion direction of the fitting convex portion 32 in a state where the fitting convex portion 32 of the spring guide 30 is fitted to the fitting concave portion 40 of the cylinder 11. The elastic body 60 may be bonded to the surface of the release preventing piece 41 on the back side in the insertion direction or the bottom surface 44 of the fitting recess 40. Fig. 11 shows an example in which an elastic body 60 is bonded to the surface of the separation preventing piece 41 on the back side in the insertion direction.
The elastic body 60 is disposed in a gap between the front surface of the fitting projection 32 of the spring guide 30 in the insertion direction and the bottom surface 44 of the fitting recess 40 of the cylinder 11, or in a gap between the rear surface of the fitting projection 32 of the spring guide 30 in the insertion direction and the retaining piece 41 of the cylinder 11. The elastic body 60 has a thickness larger than the gap.
When the elastic body 60 is inserted so as to fill the gap formed on the front side in the insertion direction of the fitting convex portion 32, the fitting convex portion 32 is pressed by the retaining piece 41, and the rotation of the spring guide 30 can be suppressed. When the elastic body 60 is inserted so as to fill the gap formed on the rear side in the insertion direction of the fitting convex portion 32, the fitting convex portion 32 is pressed by the bottom surface 44 of the fitting concave portion 40, and the rotation of the spring guide 30 can be suppressed.
(modification 3)
The stopper may be configured by appropriately combining the stopper shown in fig. 5 and the like with the stoppers shown in modification 1 and modification 2.
As described above, the rotary compressor 1 according to embodiment 1 includes: a closed container 5; an annular cylinder 11 housed in the closed casing 5; a rotary piston 13 that eccentrically rotates along the inner circumferential surface of the cylinder 11; and a vane 14 that reciprocates in a vane groove 22 provided in the cylinder block 11 in the radial direction. The rotary compressor 1 further includes a vane spring 15, and the vane spring 15 biases the vane 14 so that the tip end portion 14a of the vane 14 abuts on the rotary piston 13. The rotary compressor 1 further includes a spring guide 30, and the spring guide 30 includes: a cylindrical portion 31 in which the leaf spring 15 is fixed, and a fitting convex portion 32 that protrudes outward from the outer peripheral surface of one end side of the cylindrical portion 31. A cylindrical fitting recess 40 is formed in the cylinder 11, the fitting recess 40 is open on the outer peripheral surface 11c side of the cylinder 11 and communicates with the vane grooves 22 on the bottom surface 44, the fitting recess 40 has a retaining piece 41 for retaining the fitting projection of the spring guide 30, and the rotary compressor has the following configuration: in a state where the one end portion of the spring guide 30 on the formation side of the fitting convex portion 32 is inserted into and fitted in the fitting concave portion 40 of the cylinder 11 through the opening portion 8 formed in the closed casing 5, the spring guide 30 is rotated, the fitting convex portion 32 is locked to the release preventing piece, and the spring guide 30 is fixed to the cylinder 11 so that the spring guide 30 does not come out of the fitting concave portion 40.
Since the spring guide 30 is fixed to the cylinder 11 by fitting the fitting convex portion 32 of the spring guide 30 to the fitting concave portion 40 of the cylinder 11, a pressing force in a direction to expand the vane groove 22 does not act unlike a conventional fixing structure using elastic deformation. Therefore, deformation of the vane groove 22 can be suppressed, and the vane 14 can be stably operated. Further, since the fitting convex portion 32 is locked to the retaining piece 41 provided in the fitting concave portion 40, even if a force is applied in a direction in which the spring guide 30 is pulled out from the cylinder 11 during operation, the spring guide 30 can be prevented from coming out from the cylinder 11.
The anti-slip piece 41 has a shape protruding inward from the radially outer end in the fitting recess 40 of the spring guide 30.
In this way, the retaining piece 41 can be formed in a shape protruding inward from the radially outer end in the fitting recess 40 of the spring guide 30.
The two fitting protrusions 32 of the spring guide 30 are formed symmetrically with respect to the central axis of the spring guide 30, and have two anti-slip pieces 41 corresponding to the two fitting protrusions 32.
By providing the two fitting protrusions 32 and the two anti-slip pieces 41 in this way, the spring guide 30 can be more reliably prevented from slipping out of the cylinder 11.
The rotary compressor 1 according to embodiment 1 includes the stopper 43, and the stopper 43 contacts the fitting projection 32 of the spring guide 30 to stop the rotation of the spring guide 30.
This can prevent the spring guide 30 from rotating during operation.
The stopper 43 may be a protrusion protruding from the inner circumferential surface 40b of the fitting recess 40, or may be a pin 50 inserted into a pin insertion hole 51 formed in the cylinder 11 and having a tip end 50a contacting the fitting protrusion 32. The stopper 43 may be formed of a sheet-shaped elastic body 60, and the elastic body 60 may be inserted to fill a gap formed in the front and rear directions in the insertion direction of the fitting convex portion 32 in a state where the fitting convex portion 32 of the spring guide 30 is fitted to the fitting concave portion 40 of the cylinder 11, and may have a wall thickness larger than the gap.
The inner diameter of the opening 8 of the closed casing 5 is larger than the outer diameter of the cylindrical portion 31 of the spring guide 30, and the spring guide 30 is fixed to the cylinder 11 so as not to contact the closed casing 5.
Since the spring guide 30 is fixed to the cylinder 11 so as not to contact the hermetic container 5 in this way, the leaf spring 15 can be accurately provided for the following reason. The outer contour of the rotary compressor 1 is composed of the closed casing 5, the protruding portion 6, and the lid portion 7, and the internal pressure caused by the refrigerant discharged from the compression element 10 acts on these outer contour components. The outer contour component changes in shape such as bulging outward under the influence of internal pressure. Therefore, if the leaf spring 15 is fixed to the outer-contour component, the position of the leaf spring 15 is affected by the deformation of the outer-contour component due to the internal pressure. In contrast, in embodiment 1, the spring guide 30 is fixed to the cylinder 11 so as not to contact the sealed container 5, and therefore the leaf spring 15 can be provided without being affected by deformation of the outer-profile component. That is, the leaf spring 15 can be provided with reference to the position of the cylinder 11, and the leaf spring 15 can be provided with high accuracy.
(embodiment mode 2)
Embodiment 2 relates to a refrigeration cycle apparatus including the rotary compressor 1 according to embodiment 1.
Fig. 12 is a diagram showing a refrigerant circuit of the refrigeration cycle apparatus according to embodiment 2.
The refrigeration cycle apparatus 70 includes the rotary compressor 1 according to embodiment 1, a condenser 71, a blow-off valve 72 as a pressure reducing device, and an evaporator 73. The gas refrigerant discharged from the rotary compressor 1 flows into the condenser 71, exchanges heat with air passing through the condenser 71 to become a high-pressure liquid refrigerant, and flows out. The high-pressure liquid refrigerant flowing out of the condenser 71 is decompressed by the expansion valve 72 to become a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 73. The low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 73 exchanges heat with the air passing through the evaporator 73, becomes a low-pressure gas refrigerant, and is again sucked into the rotary compressor 1.
The refrigeration cycle apparatus 70 configured as described above includes the rotary compressor 1 according to embodiment 1, and can obtain stable operation of the vane 14 and the vane spring 15. In addition, the spring guide 30 can be inhibited from coming out of the cylinder 11. This makes it possible to construct the refrigeration cycle device 70 with high reliability.
The refrigeration cycle apparatus 70 is suitable for use in an air conditioner, a refrigerator, a freezer, or the like.
Description of the reference numerals
A rotary compressor; sealing the container; a protrusion; a cover portion; an opening portion; a compression element; a cylinder body; a cylinder chamber; inner peripheral surface; outer peripheral surface; an intermediate plate; rotating the piston; an outer peripheral surface; a blade; a front end portion; a back side; a leaf spring; a telescoping portion; a non-telescoping section; an exhaust pipe; a rotating shaft; an eccentric portion; an upper bearing; a lower bearing; a suction inlet; a drain hole; a vane slot; an electrically powered element; a stator; a rotor; an energy storage; an accumulator tube; a spring guide; an end portion; another end; a cylindrical portion; a blade passing portion; 31ab.. bottom surface; a fitting projection; a mating recess; dividing the recess; inner peripheral surface; an anti-run sheet; an end face; a pass through portion; a stop portion; a stop portion; a stop portion; a bottom surface; 45.. blade extension slots; a pin; a front end portion; a pin insertion hole; an elastomer; a refrigeration cycle apparatus; 71.. a condenser; a blow-out valve; 73..
Claims (9)
1. A rotary compressor is characterized by comprising:
a closed container;
an annular cylinder housed in the closed container;
a rotary piston that eccentrically rotates along an inner circumferential surface of the cylinder;
a vane reciprocating in a vane groove provided in the cylinder in a radial direction;
a vane spring that urges the vane so that a tip end of the vane abuts against the rotary piston; and
a spring guide having: a cylindrical portion having the leaf spring fixed therein, and a fitting convex portion protruding outward from an outer peripheral surface of one end side of the cylindrical portion,
a cylindrical fitting recess that is open on an outer peripheral surface side of the cylinder and communicates with the vane groove on a bottom surface is formed in the cylinder, the fitting recess having a retaining piece that retains the fitting projection of the spring guide,
the rotary compressor has the following structure: in a state where one end portion of the spring guide on the formation side of the fitting convex portion is inserted and fitted into the fitting concave portion of the cylinder through an opening portion formed in the closed casing, the spring guide is rotated to lock the fitting convex portion to the release prevention piece, and the spring guide is fixed to the cylinder.
2. The rotary compressor of claim 1,
the disengagement prevention piece has a shape protruding inward from an end portion on the outer side in the radial direction at the fitting recess portion of the spring guide.
3. The rotary compressor of claim 1 or 2,
the two fitting projections of the spring guide are formed symmetrically with respect to the central axis of the spring guide, and the two anti-slip pieces are provided corresponding to the two fitting projections.
4. The rotary compressor of any one of claims 1 to 3,
and a stopper portion that comes into contact with the fitting projection of the spring guide to stop rotation of the spring guide.
5. The rotary compressor of claim 4,
the stopper is a convex portion protruding from an inner peripheral surface of the fitting concave portion.
6. The rotary compressor of claim 4,
the stopper is a pin inserted into a pin insertion hole formed in the cylinder, and a tip end portion of the pin is in contact with the fitting projection.
7. The rotary compressor of claim 4,
the stopper is formed of a sheet-shaped elastic body, and the elastic body is inserted so as to fill a gap formed in the front and rear in the insertion direction of the fitting convex portion in a state where the fitting convex portion of the spring guide is fitted to the fitting concave portion of the cylinder, and has a wall thickness larger than the gap.
8. The rotary compressor of any one of claims 1 to 7,
the inner diameter of the opening of the closed casing is configured to be larger than the outer diameter of the cylindrical portion of the spring guide, and the spring guide is fixed to the cylinder so as not to contact the closed casing.
9. A refrigeration cycle apparatus, characterized in that,
a rotary compressor according to any one of claims 1 to 8.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/045598 WO2021100166A1 (en) | 2019-11-21 | 2019-11-21 | Rotary compressor and refrigeration cycle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114729641A true CN114729641A (en) | 2022-07-08 |
Family
ID=75980465
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980102293.5A Pending CN114729641A (en) | 2019-11-21 | 2019-11-21 | Rotary compressor and refrigeration cycle device |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP7285953B2 (en) |
| CN (1) | CN114729641A (en) |
| CZ (1) | CZ2022177A3 (en) |
| WO (1) | WO2021100166A1 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5597189U (en) * | 1978-12-26 | 1980-07-05 | ||
| CN101240797A (en) * | 2008-03-07 | 2008-08-13 | 广东美芝制冷设备有限公司 | Rotation-type compressor sliding blade spring and uses thereof |
| JP2010007593A (en) * | 2008-06-27 | 2010-01-14 | Sanyo Electric Co Ltd | Two-stage rotary compressor |
| CN206328843U (en) * | 2016-12-23 | 2017-07-14 | 中山市奥珀金属制品有限公司 | A kind of odour-proof floor drain for being easy to remove outer Cancellation Missed |
| CN108603505A (en) * | 2016-02-15 | 2018-09-28 | 三菱电机株式会社 | Rotary compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5256484Y2 (en) * | 1973-07-06 | 1977-12-21 |
-
2019
- 2019-11-21 WO PCT/JP2019/045598 patent/WO2021100166A1/en active Application Filing
- 2019-11-21 JP JP2021558113A patent/JP7285953B2/en active Active
- 2019-11-21 CZ CZ2022177A patent/CZ2022177A3/en unknown
- 2019-11-21 CN CN201980102293.5A patent/CN114729641A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5597189U (en) * | 1978-12-26 | 1980-07-05 | ||
| CN101240797A (en) * | 2008-03-07 | 2008-08-13 | 广东美芝制冷设备有限公司 | Rotation-type compressor sliding blade spring and uses thereof |
| JP2010007593A (en) * | 2008-06-27 | 2010-01-14 | Sanyo Electric Co Ltd | Two-stage rotary compressor |
| CN108603505A (en) * | 2016-02-15 | 2018-09-28 | 三菱电机株式会社 | Rotary compressor |
| CN206328843U (en) * | 2016-12-23 | 2017-07-14 | 中山市奥珀金属制品有限公司 | A kind of odour-proof floor drain for being easy to remove outer Cancellation Missed |
Also Published As
| Publication number | Publication date |
|---|---|
| JP7285953B2 (en) | 2023-06-02 |
| CZ2022177A3 (en) | 2022-05-25 |
| JPWO2021100166A1 (en) | 2021-05-27 |
| WO2021100166A1 (en) | 2021-05-27 |
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