WO2017216875A1

WO2017216875A1 - Rotary compressor

Info

Publication number: WO2017216875A1
Application number: PCT/JP2016/067678
Authority: WO
Inventors: 友宏井柳
Original assignee: 三菱電機株式会社
Priority date: 2016-06-14
Filing date: 2016-06-14
Publication date: 2017-12-21
Also published as: JP6727300B2; CN109312748A; JPWO2017216875A1

Abstract

This rotary compressor is provided with: a sealed container; a compression element for compressing a coolant; and an electromotive element which serves as a drive source of the compression element. The compression element includes: a cylinder which is fixed to the sealed container; a crank shaft which is fixed to a rotor of the electromotive element; a rolling piston which compresses a coolant; an upper bearing which rotatably supports the crank shaft; a discharge muffler which is formed of a cylindrical body covering the upper bearing, and along an end edge of which a flange part extending outward is formed; and a pair of fastening members which are positioned so as to be opposed to each other with the crank shaft interposed therebetween and which fasten the flange part of the discharge muffler and the upper bearing so as to bring the flange part and the upper bearing into pressure contact with each other. Within ranges each obtained by 40°-rotation, in the left and right directions, around the rotational axial center of the crank shaft from a reference axis that passes the rotational axial center of the crank shaft and that is orthogonal to an axial line connecting the pair of fastening members with each other, pressure contact parts protruding toward the upper bearing are provided, on both sides across the axial line, on a lower surface of the flange part of the discharge muffler.

Description

Rotary compressor

The present invention relates to a rotary compressor provided with a discharge muffler.

Generally, in a rotary compressor, an upper bearing having a discharge hole for discharging a refrigerant compressed by the compressor is provided, and a discharge muffler is attached so as to cover the discharge hole. The discharge muffler has a muffler space formed therein, and reduces noise generated by pulsation of high-temperature and high-pressure refrigerant gas discharged from the discharge holes. The discharge muffler has a cylindrical shape having an opening on the side attached to the upper bearing, and a flange portion is formed along the edge. The discharge muffler is fastened and fixed to the upper bearing by a fastening member having a flange portion formed of a plurality of bolts or the like. For example, Patent Document 1 discloses a compressor having a configuration in which adhesion is ensured by fastening a discharge muffler to a fixed scroll member with as many bolts as possible.

By the way, in the rotary compressor, a cloth-like sound insulating material is attached to the outer surface of the sealed container. This sound insulating material has a characteristic that an attenuation effect is exhibited for a high frequency, for example, exceeding 4 kHz, but an attenuation effect is decreased for a low frequency of 4 kHz or less. Therefore, in the rotary compressor, the number of fastening members is increased so that the resonance frequency of the discharge muffler is not 4 kHz or less.

JP 2011-149299 A

As in the compressor disclosed in Patent Document 1, generally, a plurality of fastening members are provided, and there are provided at least four portions where the discharge muffler and the upper bearing are in pressure contact with each other. The resonance frequency of the discharge muffler at 4 kHz or less. It is set as the structure which does not have. However, if the number of fastening members is large, the number of parts increases and the number of work steps in the manufacturing process increases, which increases manufacturing costs. In addition, by strongly tightening the plurality of fastening members, the discharge muffler and the upper bearing may be distorted, which may affect the performance of the compressor. Therefore, in the rotary compressor, it is desired to reduce the number of fastening members. However, in the rotary compressor, if the number of fastening members is reduced, the pressure contact area between the discharge muffler and the upper bearing is reduced, and the resonance frequency of the discharge muffler is 4 kHz or less, so the damping effect by the sound insulating material is reduced. Noise is generated by the pulsation of the refrigerant gas discharged from the discharge hole.

The present invention has been made to solve the above-described problems, and has a configuration in which the number of fastening members for fastening the discharge muffler and the upper bearing is reduced, and has a resonance frequency of the discharge muffler at 4 kHz or less. Aim to provide no rotary compressor.

The rotary compressor according to the present invention includes a hermetic container, a compression element that is accommodated in the hermetic container and compresses the refrigerant, and a rotation that is accommodated in the hermetic container and disposed inside the stator and the stator. And an electric element that serves as a drive source for the compression element. The compression element passes through a cylinder chamber of the cylinder and the rotation of the electric element through the cylinder chamber of the cylinder. A crankshaft fixed to a child, a rolling piston that is fitted to an eccentric shaft portion of the crankshaft and eccentrically rotates in the cylinder chamber and compresses the refrigerant, and closes an upper end surface of the cylinder, and the crankshaft A discharge bearing muffler that is formed along an edge of an upper bearing that rotatably supports the upper bearing, and a cylindrical body that covers the upper bearing. And a pair of fastening members that fasten and press-fit the flange portion of the discharge muffler and the upper bearing, and the crankshaft is disposed on the lower surface of the flange portion of the discharge muffler. To the upper bearing within a range rotated by 40 ° to the left and right around the rotation axis of the crankshaft from a reference axis that passes through the rotation axis of the crankshaft and is orthogonal to the axis connecting the pair of fastening members. The press-contact portions protruding in this manner are provided on both sides of the axis.

According to the rotary compressor of the present invention, the center of the rotation axis of the crankshaft is centered on the flange portion of the discharge muffler from the reference axis passing through the rotation axis of the crankshaft and orthogonal to the axis connecting the pair of fastening members. In the range where the effect is obtained, each rotated by 40 ° to the left and right, press contact portions protruding toward the upper bearing are provided on both sides across the axis, respectively, together with the press contact portion by the fastening member, The discharge muffler and the upper bearing are pressed against each other at four locations. In other words, the rotary compressor according to the present embodiment can reduce the number of fastening members and increase the pressure contact location between the discharge muffler and the upper bearing, and therefore does not have a resonance frequency of the discharge muffler below 4 kHz. Noise due to pulsation of high-temperature and high-pressure refrigerant gas discharged from the discharge hole of the upper bearing can be suppressed.

It is sectional drawing which showed the internal structure of the rotary compressor which concerns on embodiment of this invention. It is the top view which showed the discharge muffler of the rotary compressor which concerns on embodiment of this invention. FIG. 3 is an enlarged sectional view taken along line AA indicated in FIG. 2. It is sectional drawing which showed the form from which the discharge muffler of the rotary compressor which concerns on embodiment of this invention differs. It is the graph which showed the resonant frequency of the discharge muffler by a hammering test. It is the graph which showed the resonant frequency of the discharge muffler by a hammering test. It is the graph which showed the resonant frequency of the discharge muffler by a hammering test. It is explanatory drawing which showed the test body A in a CAE analysis. It is the graph which showed the primary resonant frequency of the discharge muffler at the time of changing a press-contact location in the CAE analysis of the test body A. It is explanatory drawing which showed the test body B in a CAE analysis. It is the graph which showed the primary resonance frequency of the discharge muffler at the time of changing a press-contact location in the CAE analysis of the test body B. It is explanatory drawing which showed the test body C in a CAE analysis. 6 is a graph showing a primary resonance frequency of a discharge muffler when a pressure contact location is changed in a CAE analysis of a specimen C.

Embodiment.
DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a rotary compressor according to the present invention will be described with reference to the drawings. In addition, the following drawings including FIG. 1 are shown schematically, and the relationship between the sizes of the constituent members may be different from the actual one. In the following embodiment, a vertical rotary compressor will be described as an example. However, the present invention can be similarly applied to a horizontal rotary compressor.

FIG. 1 is a cross-sectional view showing the internal structure of a rotary compressor according to an embodiment of the present invention. FIG. 2 is a plan view showing a discharge muffler of the rotary compressor according to the embodiment of the present invention. FIG. 3 is an enlarged cross-sectional view taken along the line AA indicated in FIG. The rotary compressor 100 according to the present embodiment is used as one element of a refrigeration circuit that forms a refrigeration cycle in a refrigeration apparatus, an air conditioner, a heat pump hot water heater, a refrigerator, or the like. Based on FIG. 1, the structure and operation | movement of this rotary compressor 100 are demonstrated.

The rotary compressor 100 includes a sealed container 1, a compression element 4 and an electric element 3 housed in the sealed container 1. Refrigerating machine oil 40 that mainly lubricates the sliding portion of the compression element 4 is stored at the bottom of the sealed container 1. An accumulator 2 is provided on the side of the sealed container 1. The accumulator 2 includes a suction pipe 9 that sucks refrigerant gas into the compression element 4. A suction pipe 9 communicating with the accumulator 2 is connected to the lower part of the sealed container 1. Moreover, the discharge pipe 1a is connected to the upper part of the airtight container 1, and the compressed refrigerant gas is discharged | emitted. The accumulator 2 is provided to separate the refrigerant into liquid refrigerant and gas refrigerant so that the liquid refrigerant is not sucked into the compression element 4 as much as possible.

The compression element 4 has a mechanism for compressing, for example, CO ₂ refrigerant, and includes a cylinder 7, a rolling piston 11, a vane (not shown), a crankshaft 10, an upper bearing 5, a lower bearing 8, a discharge muffler 6, and the like. I have. Note that the refrigerant is not limited to the CO ₂ refrigerant.

The cylinder 7 in which the compression chamber is formed has a cylinder chamber 7a that is a substantially circular space in plan view, and the outer peripheral portion is fixed to the hermetic container 1 by a bolt or the like (not shown). The cylinder chamber 7a is open at both ends in the axial direction. The cylinder chamber 7 a is provided with a rolling piston 11 that rotates eccentrically by the crankshaft 10. The rolling piston 11 is slidably fitted to the eccentric shaft portion 10a of the crankshaft 10. A compression chamber (not shown) in which the space surrounded by the inner peripheral surface of the cylinder chamber 7a of the cylinder 7, the outer peripheral surface of the rolling piston 11 and the vane (not shown) changes its volume by the eccentric rotational movement of the rolling piston 11; Become.

Further, the cylinder 7 is provided with parallel vane grooves (not shown) extending in the radial direction and communicating with the cylinder chamber 7a in the axial direction. A back pressure chamber (not shown) which is a substantially circular space in plan view communicating with the vane groove is provided on the back surface (outside) of the vane groove.

The vane is housed in the vane groove of the cylinder 7 and is always pressed against the rolling piston 11 by a vane spring (not shown) provided in the back pressure chamber. In the rotary compressor 100, since the inside of the sealed container 1 is at a high pressure, when the operation is started, a force due to the differential pressure between the high pressure in the sealed container 1 and the pressure in the cylinder chamber 7a acts on the back surface (back pressure chamber side) of the vane. Therefore, the vane spring is mainly used for the purpose of pressing the vane against the rolling piston 11 when the rotary compressor 100 is started up (in a state where there is no difference between the pressure in the sealed container 1 and the cylinder chamber 7a). The shape of the vane is a flat shape (the thickness in the circumferential direction is smaller than the length in the radial direction and the axial direction).

The suction pipe 9 of the accumulator 2 is connected to the cylinder 7. A suction port (not shown) through which the refrigerant gas from the suction pipe 9 passes penetrates the cylinder chamber 7 a from the outer periphery of the cylinder 7.

The cylinder 7 is provided with a discharge port (not shown) in which the vicinity of the edge of a circle forming the cylinder chamber 7a which is a substantially circular space is cut out. The discharge port communicates with a discharge hole 5a including a discharge valve 5b that is a check valve.

The electric element 3 includes an electric motor rotor 30 and an electric motor stator 31. The electric motor rotor 30 is fixed to the crankshaft 10 by shrink fitting or the like. The electric motor stator 31 is fixed to the sealed container 1. Moreover, in order to supply electric power to the electric motor stator 31, a glass terminal installed at the upper part of the hermetic container 1 is connected to the electric motor stator 31 via a lead wire.

The crankshaft 10 is provided through the cylinder chamber 7a. An upper bearing 5 that rotatably supports the main shaft portion 10 b is provided on the upper surface of the cylinder 7. A lower bearing 8 that rotatably supports the auxiliary shaft portion 10c is provided on the lower surface of the cylinder 7. The upper bearing 5 has a substantially inverted T shape when viewed from the side, and closes the upper surface installed on the cylinder 7. The lower bearing 8 is substantially T-shaped in a side view and closes the lower surface installed on the cylinder 7. Further, the upper bearing 5 is provided with a discharge hole 5a at substantially the same position as the discharge port (not shown) of the cylinder 7 in plan view, and a discharge valve 5b is provided in the discharge hole 5a.

The discharge valve 5b receives the pressure in the cylinder chamber 7a and the pressure in the sealed container 1, and when the pressure in the cylinder chamber 7a is lower than the pressure in the sealed container 1, the discharge valve 5b is pressed against the discharge hole 5a. Occlude. On the other hand, when the pressure in the cylinder chamber 7a becomes higher than the pressure in the sealed container 1, the discharge valve 5b is pushed upward by the pressure in the cylinder chamber 7a, opens the discharge hole 5a, and the compressed refrigerant is Guide out of chamber 7a.

A discharge muffler 6 covering the upper surface is fixed to the upper surface of the upper bearing 5 by

fastening members

60 and 60. The discharge muffler 6 shown in FIG. 2 is in a state before being attached to the upper bearing 5. As shown in FIG. 2, the discharge muffler 6 is formed of a cylindrical body having an opening on the side attached to the upper bearing 5, and a flange portion 6b extending outward is formed along the edge. The discharge muffler 6 is fastened and fixed to the upper surface of the upper bearing 5 by a pair of

fastening members

60, 60 having flange portions 6b made of bolts or the like. The discharge muffler 6 has press contact portions a and c that are pressed by the

fastening members

60 and 60. As shown in FIG. 2, the pair of

fastening members

60, 60 are provided at positions facing each other with the crankshaft 10 in between.

The discharge muffler 6 has a center hole 6c that is inserted into the boss portion 5c of the upper bearing 5 at the approximate center in plan view. Further, the inside of the discharge muffler 6 is a muffler space 61 that communicates with the discharge hole 5a through the discharge valve 5b, and the discharge hole 6a is opened above the discharge muffler 6. The high-temperature and high-pressure refrigerant gas discharged from the discharge hole 5 a of the upper bearing 5 once enters the muffler space 61 and is then discharged into the sealed container 1 from the discharge hole 6 a of the discharge muffler 6.

As shown in FIG. 2, the flange portion 6 b of the discharge muffler 6 has a crankshaft extending from a reference axis X passing through the rotational axis P of the crankshaft 10 and perpendicular to the axis Y connecting the pair of

fastening members

60, 60. In the range S rotated 40 ° to the left and right about the 10 rotation axis P, press contact portions b and d projecting downward toward the upper bearing 5 are provided on both sides of the axis Y. . For example, the pressure contact portions b and d may be provided only on one side of the flange portion 6b with the reference axis X as a boundary (see FIG. 7A). Alternatively, the pressure contact parts b and d may be provided on both sides of the axis line Y within a range in which the pressure contact parts b and d are rotated by 40 ° to one side around the rotation axis P of the crankshaft 10 from the reference axis X. (See FIG. 8A). That is, since the rotary compressor 100 according to the present embodiment includes the pressure contact portions a and c of the discharge muffler 6 and the upper bearing 5 by the

fastening members

60 and 60, the discharge muffler 6 and the upper bearing 5 are It is press-contacted at four places.

As shown in FIG. 3, the pressure contact portions b and d are formed with a bent portion 6 d formed by bending the flange portion 6 b of the discharge muffler 6 into a V shape and bending the bent portion 6 d to the upper surface of the upper bearing 5. It is a configuration. The process of bending the flange portion 6b into a V-shape is easy and does not require technical skill, a lot of processing effort, and processing costs.

Desirably, the height L of the bent portion 6d protruding toward the upper bearing 5 is not less than 50 μm and not more than 300 μm from the lower surface of the flange portion 6b. If the height L of the bent portion 6d is too small, the flange portion 6b cannot be brought into pressure contact with the upper bearing 5 at the pressure contact portions b and d. On the other hand, if the height L of the bent portion 6d is excessively increased, the flange portion 6b cannot be brought into pressure contact with the upper bearing 5 at the pressure contact portions a and c. That is, the height L that allows the flange portion 6b and the upper bearing 5 to be securely brought into pressure contact with each other at four positions is set to 50 μm or more and 300 μm or less. However, the above height dimension L is an example, and is not limited to 50 μm or more and 300 μm or less.

Further, it is desirable that the discharge muffler 6 has a plate thickness of 1 mm or more and 2 mm or less. This is because the discharge muffler 6 is liable to bend when the plate thickness is too thin, and may be bent when the fastening member 60 is fastened. In addition, the thickness of the discharge muffler 6 is set to 2 mm or less in consideration of drawing processing when the discharge muffler 6 is manufactured. However, the above dimensions are merely examples, and the thickness of the discharge muffler 6 is not limited to 1 mm or more and 2 mm or less.

Incidentally, if the thickness of the discharge muffler 6 is increased, the discharge muffler 6 becomes difficult to be deformed when fastened by the

fastening members

60, 60, and cannot be flexibly pressed against the upper bearing 5, so that a slight gap is generated between the discharge muffler 6 and the upper bearing 5. Therefore, it has a resonance frequency below 4 kHz. However, due to an increase in refrigerant flow rate and an increase in refrigerant density, it is common to increase the plate thickness in order to ensure the reliability of the discharge muffler.

FIG. 4 is a cross-sectional view showing a different form of the discharge muffler of the rotary compressor according to the embodiment of the present invention. The pressure contact portions b and d shown in FIG. 4 have a configuration in which a protrusion 6 e is provided on the flange portion 6 b of the discharge muffler 6 and the protrusion 6 e is pressed against the upper surface of the upper bearing 5. The protruding portion 6e has, for example, a configuration in which the plate thickness of the flange portion 6b is partially increased, a dowel-shaped configuration, a configuration in which a rib is provided, or the like. As an example, the protrusion 6e has a size approximately equal to the shaft diameter of the fastening member 60. Moreover, the height dimension L which the protrusion part 6e protrudes toward the upper bearing 5 shall be 50 micrometers or more and 100 micrometers or less as an example similarly to the bending part 6d. In addition, the protrusion part 6e is not limited to the said structure, If it is the structure protruded toward the upper bearing 5, it can implement in a various aspect.

Here, the operation of the rotary compressor 100 will be described. In the rotary compressor 100, the refrigerant of the accumulator 2 is introduced into the compression chamber of the cylinder chamber 7a through the suction pipe 9 and the suction port, and then the electric element 3 is driven. When the electric element 3 is driven, the rolling piston 11 fitted to the eccentric shaft portion 10a of the crankshaft 10 rotates eccentrically, so that the refrigerant is compressed in the cylinder chamber 7a. The refrigerant compressed in the cylinder chamber 7 a is discharged into the muffler space 61 from the discharge hole 5 a of the upper bearing 5, and then discharged into the sealed container 1 from the discharge hole 6 a of the discharge muffler 6. The discharged refrigerant passes through the gaps of the electric element 3 (gap between the electric motor rotor 30 and the electric motor stator 31, grooves provided on the outer peripheral surface of the electric motor stator 31, etc.) and then from the discharge pipe 1a to the refrigeration circuit (FIG. (Not shown).

Next, the resonance frequency of the discharge muffler during the operation of the rotary compressor 100 will be described. 5A to 5C are graphs showing the resonance frequency of the discharge muffler by the hammering test. 5A to 5C, the horizontal axis represents frequency, and the vertical axis represents response level. First, FIG. 5A shows the generation of a resonance frequency in the case where the discharge muffler 6 and the upper bearing 5 are press-contacted at two locations of the press-contact portion a and the press-contact portion c shown in FIG. According to the test results shown in FIG. 5A, it was confirmed that at frequencies of 4 kHz or less, the frequencies were 1.19 kHz and 3.2 kHz and had a resonance frequency.

Next, in FIG. 5B, the discharge muffler 6 and the upper bearing 5 are press-contacted at two locations of the press-contact portion a and the press-contact portion c shown in FIG. 2, and further pressed at one location of the press-contact portion b or the press-contact portion d. The generation of the resonance frequency in the case of having a total of three press contact points is shown. According to the test result shown in FIG. 5B, it was confirmed that a frequency of 4 kHz or less has a resonance frequency when the frequency is 2.51 kHz.

Next, in FIG. 5C, the discharge muffler 6 and the upper bearing 5 are press-contacted at two locations of the press-contact portion a and the press-contact portion c shown in FIG. 2, and further pressed at two locations of the press-contact portion b and the press-contact portion d. The generation of the resonance frequency in the case of having a total of four pressure contact points is shown. According to the test results shown in FIG. 5C, it was confirmed that the discharge muffler 6 and the upper bearing 5 were pressed at four locations, so that there was no resonance frequency at a frequency of 4 kHz or less.

Next, with reference to FIGS. 6 to 8, the relationship between the press-contact point and the resonance frequency during the operation of the rotary compressor 100 will be described. First, FIG. 6A is an explanatory view showing a specimen A in CAE analysis. FIG. 6B is a graph showing the primary resonance frequency of the discharge muffler when the pressure contact location is changed in the CAE analysis of the test body A. In FIG. 6B, the horizontal axis represents the rotation angle θ from the reference axis X, and the vertical axis represents the resonance frequency. In the specimen A shown in FIG. 6A, one side of the flange portion 6b (on the left side in the illustrated example) at the position rotated from the reference axis X by the angle θ about the rotation axis P of the crankshaft 10 as a center. ) Only in the pressure contact portion b. The angle θ is changed in increments of 10 ° in the range of 0 ° to 90 °. According to the analysis result shown in FIG. 6B, it was confirmed that the resonance frequency was 3 kHz or less at all the rotation angles θ.

Next, FIG. 7A is an explanatory diagram showing the specimen B in the CAE analysis. FIG. 7B is a graph showing the primary resonance frequency of the discharge muffler when the pressure contact location is changed in the CAE analysis of the test body B. In FIG. 7B, the horizontal axis represents the rotation angle θ from the reference axis X, and the vertical axis represents the resonance frequency. In the test body B shown in FIG. 7A, the pressure contact portions b and d are provided on both sides of the flange portion 6b across the axis Y at a position rotated from the reference axis X about the rotation axis P of the crankshaft 10 by an angle θ. Each is provided. The pressure contact part b and the pressure contact part d are provided at positions symmetrical with respect to the axis Y. The angle θ is changed in increments of 10 ° in the range of 0 ° to 90 °. According to the analysis result shown in FIG. 7B, as shown in region R, when the rotation angle θ from the reference axis X is 40 ° or less, it was confirmed that there is no resonance frequency below 4 kHz.

Next, FIG. 8A is an explanatory view showing a specimen C in the CAE analysis. FIG. 8B is a graph showing the primary resonance frequency of the discharge muffler when the pressure contact location is changed in the CAE analysis of the specimen C. In FIG. 8B, the horizontal axis represents the rotation angle θ of the reference axis X, and the vertical axis represents the resonance frequency. In the test body C shown in FIG. 8A, the pressure contact portions b and d are provided on both sides of the flange portion 6b across the axis Y at a position rotated from the reference axis X about the rotation axis P of the crankshaft 10 by an angle θ. Each is provided. The pressure contact portion b and the pressure contact portion d are provided at positions that are symmetric with respect to the rotation axis P. The angle θ is changed in increments of 10 ° in the range of 0 ° to 90 °. According to the analysis result shown in FIG. 8B, as shown in the region R, when the rotation angle θ from the reference axis X is 40 ° or less, it was confirmed that there is no resonance frequency at 4 kHz or less.

Therefore, according to the rotary compressor 100 according to the present embodiment, the flange portion 6b of the discharge muffler 6 passes through the rotational axis P of the crankshaft 10 and is orthogonal to the axis Y connecting the pair of

fastening members

60 and 60. Pressure contact portions b and d projecting toward the upper bearing 5 within a range S in which a particular effect is obtained by rotating the reference shaft X around the rotation axis P of the crankshaft 10 by 40 ° to the left and right respectively. The discharge muffler 6 and the upper bearing 5 are pressed in four places together with the press contact portions a and c by the

fastening members

60 and 60, respectively. That is, since the rotary compressor 100 according to the present embodiment can reduce the number of fastening members 60 and increase the pressure contact locations of the discharge muffler 6 and the upper bearing 5, the resonance frequency of the discharge muffler 6 can be reduced to 4 kHz or less. The noise caused by the pulsation of the high-temperature and high-pressure refrigerant gas discharged from the discharge hole 5a of the upper bearing 5 can be suppressed.

Note that, as shown in FIG. 1, the oil surface of the refrigerating machine oil 40 is generally sealed so as to be an upper surface than the flange portion 6 b of the discharge muffler 6. That is, since the gap between the flange portion 6b and the upper bearing 5 is sealed by the refrigerating machine oil 40, the discharge muffler 6 is sufficiently sealed even if the flange portion 6b and the upper bearing 5 are not completely in close contact with each other. It is secured.

Further, the discharge muffler 6 shown in FIG. 2 is provided with a pair of reinforcing

ribs

62 and 62 facing each other across the center hole 6c in an arrangement orthogonal to the pair of

fastening members

60 and 60 to ensure rigidity. It is. Therefore, the discharge muffler 6 has high rigidity and is not easily deformed in a range in which the discharge muffler 6 is rotated by 5 ° to the left and right about the rotation axis P of the crankshaft 10 from the reference axis X. In other words, the discharge muffler 6 has a position where the press contact portions b and d are provided at a position rotated by 5 ° from the reference axis X to the left and right around the rotation axis P of the crankshaft 10 and a position rotated by 40 °. If it is within the range surrounded by, the force required for deformation can be reduced and assembly distortion is reduced.

Further, the press contact portions b and d are formed with a bent portion 6d formed by bending the flange portion 6b of the discharge muffler 6 into a V shape, and the bent portion 6d is pressed into contact with the upper bearing 5, so that the processing is easy. Technical skill and much processing effort and processing cost are not required. In addition, the pressure contact portions b and d can be configured such that a protrusion 6e is provided on the flange portion 6b of the discharge muffler 6 and the protrusion 6e is pressed against the upper bearing 5, so that the shape and size of the discharge muffler 6 can be increased. Depending on the thickness and thickness, the present invention can be carried out in various modes.

Further, the height dimension L projecting from the pressure contact portions b and d toward the upper bearing 5 is not less than 50 μm and not more than 300 μm from the lower surface of the flange portion 6 b, so that the flange portion 6 b and the upper bearing 5 are securely connected to each other as described above. Can be pressed in place.

Further, since the plate thickness of the flange portion 6b of the discharge muffler 6 is not less than 1 mm and not more than 2 mm, it has rigidity capable of preventing the bending that occurs when the

fastening members

60 and 60 are tightened, and is further drawn when the discharge muffler 6 is manufactured. Can be easily performed.

Although the present invention has been described above based on the embodiment, the present invention is not limited to the configuration of the embodiment described above. For example, the illustrated internal configuration of the rotary compressor 100 is an example, and is not limited to the above-described content, and can be similarly implemented even with a rotary compressor including other components. . In short, it should be noted that the scope of the present invention also includes the scope of various changes, applications, and uses made by those skilled in the art as needed.

1 sealed container, 1a discharge pipe, 2 accumulator, 3 electric element, 4 compression element, 5 upper bearing, 5a discharge hole, 5b discharge valve, 5c boss part, 6 discharge muffler, 6a discharge hole, 6b flange part, 6c center Hole, 6d Bend, 6e Projection, 7 Cylinder, 7a Cylinder Chamber, 8 Lower Bearing, 9 Suction Pipe, 10 Crankshaft, 10a Eccentric Shaft, 10b Main Shaft, 10c Subshaft, 11 Rolling Piston, 30 Motor Rotation Child, 31 Motor stator, 40 Refrigerating machine oil, 60 Fastening member, 61 Muffler space, 62 Reinforcing rib, 100 Rotary compressor, a, b, c, d pressure contact part, X reference axis, Y axis

Claims

A sealed container;
A compression element contained in the sealed container and compressing the refrigerant;
An electric element housed in the sealed container, having a stator and a rotor disposed inside the stator, and serving as a drive source for the compression element;
The compression element is
A cylinder fixed to the sealed container;
A crankshaft passing through a cylinder chamber of the cylinder and fixed to the rotor of the electric element;
A rolling piston that is fitted to an eccentric shaft portion of the crankshaft and eccentrically rotates in the cylinder chamber to compress the refrigerant;
An upper bearing for closing the upper end surface of the cylinder and rotatably supporting the crankshaft;
A discharge muffler comprising a cylindrical body covering the upper bearing, and a flange portion extending outward is formed along the edge,
A pair of fastening members that are provided at positions facing each other across the crankshaft, and that fasten and press-fit the flange portion of the discharge muffler and the upper bearing;
The lower surface of the flange portion of the discharge muffler is laterally centered about the rotation axis of the crankshaft from a reference axis that passes through the rotation axis of the crankshaft and is orthogonal to an axis that connects the pair of fastening members. A rotary compressor in which press contact portions protruding toward the upper bearing are provided on both sides of the axis within a range rotated by 40 °.
The rotary compressor according to claim 1, wherein the pressure contact portion is provided only on one side of the flange portion with the reference axis as a boundary.
2. The rotary according to claim 1, wherein the press contact portions are respectively provided on both sides of the axis line within a range rotated from the reference shaft by 40 ° to one side around the rotation axis of the crankshaft. Compressor.
The rotary compressor according to any one of claims 1 to 3, wherein a bent portion obtained by bending the flange portion of the discharge muffler into a V shape is formed as the pressure contact portion.
The rotary compressor according to any one of claims 1 to 3, wherein a protrusion is provided on the flange portion of the discharge muffler as the pressure contact portion.
The rotary compressor according to any one of claims 1 to 5, wherein a dimension of the pressure contact portion projecting toward the upper bearing is not less than 50 µm and not more than 300 µm from a lower surface of the flange portion.
The rotary compressor according to any one of claims 1 to 6, wherein a plate thickness of the flange portion of the discharge muffler is 1 mm or more and 2 mm or less.