JPWO2020161965A1 - Rotary compressor, manufacturing method of rotary compressor and refrigeration cycle equipment - Google Patents

Abstract

The rotary compressor of the embodiment includes a case, a rotating shaft, a compression mechanism unit, a balancer, and a balancer cover. A through hole is formed in the balancer cover at a position facing the rotation axis in the axial direction. The rotating shaft has a thrust sliding portion, a protruding portion, and a supply path. The thrust sliding portion abuts on the seal portion located around the through hole of the balancer cover in the axial direction of the rotation axis. The protruding portion is located on the inner peripheral side with respect to the thrust sliding portion, and projects below the lower end of the through hole through the through hole. The supply path opens at the lower end surface of the protrusion and guides the lubricating oil.

Description

Embodiments of the present invention relate to a rotary compressor, a method for manufacturing a rotary compressor, and a refrigeration cycle device.
The present application claims priority with respect to Japanese Patent Application No. 2019-02870 filed in Japan on February 7, 2019, the contents of which are incorporated herein by reference.

A rotary compressor is used in a refrigeration cycle device such as an air conditioner. In a rotary compressor, the refrigerant is compressed by eccentric rotation of the eccentric portion of the rotating shaft by the compression mechanism portion.

In this type of rotary compressor, the rotary shaft is formed with a supply path for supplying the lubricating oil stored in the case to the sliding portion between the rotary shaft and the bearing. However, if the refrigerant compressed by the compression mechanism enters the supply path, there is a possibility that the desired lubrication performance cannot be obtained.

JP-A-2018-165502

An object to be solved by the present invention is to provide a rotary compressor, a method for manufacturing the rotary compressor, and a refrigeration cycle device capable of obtaining desired lubrication performance.

The rotary compressor of the embodiment includes a case, a rotating shaft, a compression mechanism unit, a balancer, and a balancer cover. Lubricating oil is stored in the case. The axis of rotation is located within the case and has an eccentric portion. The compression mechanism includes a cylinder, a main bearing, and an auxiliary bearing. The cylinder accommodates an eccentric portion. The main bearing rotatably supports the rotating shaft above the cylinder. The auxiliary bearing rotatably supports the rotating shaft below the cylinder. A through hole is formed at a position facing the rotation axis of the balancer cover in the axial direction. The rotating shaft has a thrust sliding portion, a protruding portion, and a supply path. The thrust sliding portion of the rotating shaft abuts in the axial direction on the seal portion located around the through hole of the balancer cover. The protruding portion is located on the inner peripheral side of the thrust sliding portion, and projects below the through hole through the through hole. The supply path opens at the lower end surface of the protrusion to guide the lubricating oil.

FIG. 6 is a schematic configuration diagram of a refrigeration cycle apparatus including a cross-sectional view of a rotary compressor according to a first embodiment. FIG. 3 is a cross-sectional view of a compression mechanism portion corresponding to line II-II in FIG. Enlarged view of the main part of FIG. FIG. 3 is a partial cross-sectional view of the rotary compressor according to the second embodiment. A process diagram for explaining the assembly process.

Hereinafter, the rotary compressor of the embodiment, the manufacturing method of the rotary compressor, and the refrigeration cycle apparatus will be described with reference to the drawings.
(First Embodiment)
First, the refrigeration cycle device 1 will be briefly described. FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 1 including a cross-sectional view of the rotary compressor 2 according to the first embodiment.
As shown in FIG. 1, the refrigeration cycle device 1 of the present embodiment includes a rotary compressor 2, a condenser 3 which is a radiator connected to the rotary compressor 2, and an expansion connected to the condenser 3. A device 4 and an evaporator 5 as a heat absorber connected between the expansion device 4 and the rotary compressor 2 are provided.

The rotary compressor 2 is a so-called rotary compressor. The rotary compressor 2 compresses the low-pressure gas refrigerant taken into the inside to obtain a high-temperature and high-pressure gas refrigerant. The specific configuration of the rotary compressor 2 will be described later.
The condenser 3 dissipates heat from the high-temperature, high-pressure gas refrigerant sent from the rotary compressor 2 to form a high-pressure liquid refrigerant.

The expansion device 4 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser 3 to obtain a low-temperature / low-pressure liquid refrigerant.
The evaporator 5 vaporizes the low-temperature / low-pressure liquid refrigerant sent from the expansion device 4, and turns the low-temperature / low-pressure liquid refrigerant into a low-pressure gas refrigerant. Then, in the evaporator 5, when the low-pressure liquid refrigerant vaporizes, the heat of vaporization is taken from the surroundings, and the surroundings are cooled. The low-pressure gaseous refrigerant that has passed through the evaporator 5 is taken into the rotary compressor 2 described above.

As described above, in the refrigeration cycle apparatus 1 of the present embodiment, the refrigerant as the working fluid circulates while changing the phase between the gas refrigerant and the liquid refrigerant. In the refrigeration cycle apparatus 1 of the present embodiment, it is possible to use an HFC-based refrigerant such as R410A or R32, an HFO-based refrigerant such as R1234yf or R1234ze, or a natural refrigerant such as _{CO 2 as the refrigerant.}

Next, the rotary compressor 2 described above will be described.
The rotary compressor 2 of the present embodiment includes a compressor main body 11 and an accumulator 12.
The accumulator 12 is a so-called gas-liquid separator. The accumulator 12 is provided between the above-mentioned evaporator 5 and the compressor main body 11. The accumulator 12 is connected to the compressor body 11 through a suction pipe 21. The accumulator 12 supplies only the gaseous refrigerant out of the gaseous refrigerant vaporized by the evaporator 5 and the liquid refrigerant not vaporized by the evaporator 5 to the compressor main body 11.

The compressor main body 11 includes a rotating shaft 31, an electric motor unit 32, a compression mechanism unit 33, and a case 34 for accommodating the rotating shaft 31, the electric motor unit 32, and the compression mechanism unit 33. The compressor main body 11 of the present embodiment is arranged with the axial direction of the rotating shaft 31 as the vertical direction.
The case 34 is formed in a cylindrical shape, and both ends in the axial direction are closed. Lubricating oil J is housed in the case 34. A part of the compression mechanism portion 33 is immersed in the lubricating oil J.

The rotating shaft 31 is arranged coaxially with the axis O of the case 34. In the following description, the direction along the axis O is simply referred to as the axial direction, the direction orthogonal to the axial direction is referred to as the radial direction, and the direction around the axis O is referred to as the circumferential direction.

The electric motor unit 32 is arranged on the first side in the axial direction in the case 34. The compression mechanism unit 33 is arranged on the second side in the axial direction in the case 34. In the following description, the motor unit 32 side along the axial direction is the upper side, and the compression mechanism unit 33 side is the lower side.

The electric motor unit 32 is a so-called inner rotor type DC brushless motor. Specifically, the motor unit 32 includes a stator 35 and a rotor 36.
The stator 35 is fixed to the inner wall surface of the case 34 by shrink fitting or the like.
The rotor 36 is fixed to the upper part of the rotating shaft 31 with a radial interval inside the stator 35.

A counter bore 37 is formed on the inner peripheral portion of the lower surface of the rotor 36. The counter bore 37 is an annular recess formed over the entire circumference of the rotor 36 while being recessed upward from the lower surface of the rotor 36. A balancer 39 is provided on the outer peripheral portion of the lower surface of the rotor 36. The balancer 39 is formed in, for example, an arc shape in a plan view seen from the axial direction. The balancer 39 is provided on the lower surface of the rotor 36 at a part in the circumferential direction.

The compression mechanism 33 includes a cylindrical cylinder 41 through which the rotating shaft 31 penetrates, and a main bearing 42 and an auxiliary bearing 43 that separately close the openings at both ends of the cylinder 41 and rotatably support the rotating shaft 31. It has. The space formed by the cylinder 41, the main bearing 42, and the auxiliary bearing 43 constitutes the cylinder chamber 46.

An eccentric portion 51 that is eccentric in the radial direction with respect to the axis O is formed in a portion of the rotating shaft 31 described above that is located in the cylinder chamber 46. In the present embodiment, the eccentric direction of the eccentric portion 51 is set on the opposite side of the balancer 39 with the axis O in between.
A roller 53 is extrapolated to the eccentric portion 51. The roller 53 is configured to be eccentrically rotatable with respect to the axis O while the outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder 41 as the rotating shaft 31 rotates.

FIG. 2 is a cross-sectional view of the compression mechanism portion 33 corresponding to the line II-II of FIG.
As shown in FIG. 2, in the cylinder 41, a blade groove 54 recessed outward in the radial direction is formed in a part in the circumferential direction. The blade groove 54 is formed over the entire axial direction (vertical direction) of the cylinder 41. The blade groove 54 communicates with the inside of the case 34 at the outer end in the radial direction.

A blade 55 is provided in the blade groove 54. The blade 55 is configured to be slidable in the radial direction with respect to the cylinder 41. The blade 55 is urged inward in the radial direction by an urging member (not shown). The radial inner end surface of the blade 55 is in contact with the outer peripheral surface of the roller 53 in the cylinder chamber 46. As a result, the blade 55 moves back and forth into the cylinder chamber 46 as the roller 53 rotates eccentrically.

The cylinder chamber 46 is divided into a suction chamber 46a and a compression chamber 46b by a roller 53 and a blade 55. Then, in the compression mechanism unit 33, the compression operation is performed in the cylinder chamber 46 by the rotation operation of the roller 53 and the advance / retreat operation of the blade 55.

In the cylinder 41, the cylinder 41 is radially penetrated through a portion of the cylinder 41 located on the inner side of the blade groove 54 (on the left side of the blade groove 54 in FIG. 2) along the rotation direction of the roller 53 (see the arrow in FIG. 2). A suction hole 56 is formed. The suction pipe 21 (see FIG. 1) described above is connected to the suction hole 56 from the outer end in the radial direction. On the other hand, the radial inner end of the suction hole 56 is open in the cylinder chamber 46 (suction chamber 46a).

The main bearing 42 closes the upper end opening of the cylinder 41. The main bearing 42 rotatably supports a portion of the rotating shaft 31 located above the cylinder 41. Specifically, the main bearing 42 includes a tubular portion 61 through which the rotating shaft 31 is inserted, and a flange portion 62 projecting outward from the lower end portion of the tubular portion 61 in the radial direction.

The upper end of the tubular portion 61 is housed in the counter bore 37 described above. As a result, the rotary compressor 2 (compressor main body 11) is miniaturized in the axial direction.
A main bearing discharge hole 64 that penetrates the flange portion 62 in the axial direction is formed in a part of the flange portion 62 in the circumferential direction. The main bearing discharge hole 64 communicates with the cylinder chamber 46 (compression chamber 46b). A discharge valve mechanism 67 is provided on the flange portion 62. The discharge valve mechanism 67 opens the main bearing discharge hole 64 as the pressure inside the cylinder chamber 46 (compression chamber 46b) rises, and discharges the refrigerant to the outside of the cylinder chamber 46.

The main bearing 42 is provided with a muffler 65 that covers the main bearing 42 from above. A communication hole 66 that communicates with the inside and outside of the muffler 65 is formed at the central portion of the muffler 65 in the radial direction. The high-temperature and high-pressure gaseous refrigerant discharged through the discharge hole 64 described above is discharged into the case 34 through the communication hole 66.

The auxiliary bearing 43 closes the lower end opening of the cylinder 41. The auxiliary bearing 43 rotatably supports a portion of the rotating shaft 31 located below the cylinder 41. Specifically, the auxiliary bearing 43 includes a tubular portion 71 through which the rotating shaft 31 is inserted, and a flange portion 72 projecting outward from the upper end portion of the tubular portion 71 in the radial direction.

An auxiliary bearing discharge hole 73 that penetrates the flange portion 72 in the axial direction is formed in a part of the flange portion 72 in the circumferential direction. The auxiliary bearing discharge hole 73 communicates with the cylinder chamber 46 (compression chamber 46b). A discharge valve mechanism 75 is provided on the flange portion 72. The discharge valve mechanism 75 opens the auxiliary bearing discharge hole 73 as the pressure inside the cylinder chamber 46 (compression chamber 46b) rises, and discharges the refrigerant to the outside of the cylinder chamber 46.

The auxiliary bearing 43 is provided with a balancer cover 81 that covers the auxiliary bearing 43 from below. The balancer cover 81 is formed in a bottomed cylindrical shape that opens upward. At the bottom of the balancer cover 81, a seal portion 82 is formed at the central portion in the radial direction. The seal portion 82 is formed so as to bulge upward with respect to the outer peripheral portion of the bottom portion of the balancer cover 81. However, the seal portion 82 does not have to bulge from the bottom of the balancer cover 81. The upper surface of the seal portion 82 is formed as a flat surface orthogonal to the axis O. A through hole 84 that penetrates the seal portion 82 in the axial direction is formed in the central portion (the portion located on the axis O) of the seal portion 82.

The main bearing 42, the cylinder 41, and the auxiliary bearing 43 are formed with a communication hole 85 for communicating the inside of the muffler 65 and the inside of the balancer cover 81. The communication hole 85 penetrates the main bearing 42, the cylinder 41, and the sub bearing 43 in the axial direction at a position where the axis O is sandwiched between the discharge holes 64 and 73 described above and faces each other in the radial direction.

FIG. 3 is an enlarged view of a main part of FIG.
As shown in FIG. 3, the rotating shaft 31 of the present embodiment has a thrust sliding portion 90 and a protruding portion 87 located on the inner peripheral side of the thrust sliding portion 90 and projecting downward. ..

The rotating shaft 31 further includes the above-mentioned eccentric portion 51, a main shaft portion 88, and a sub-shaft portion 89.
The spindle portion 88 is a portion of the rotation shaft 31 described above that is located above the eccentric portion 51. The spindle portion 88 is connected above the eccentric portion 51 via the connecting portion 51a. The spindle portion 88 is supported by the spindle bearing 42, and the rotor 36 is fixed to the spindle portion 88.
On the other hand, the sub-shaft portion 89 is a portion of the rotating shaft 31 located below the eccentric portion 51. The sub-shaft portion 89 is connected below the eccentric portion 51 via the connecting portion 51b. The sub-shaft portion 89 is supported by the sub-bearing 43. In the present embodiment, the outer diameter φDs of the sub-shaft portion 89 is smaller than the outer diameter φDm of the main shaft portion 88. However, the sub-shaft portion 89 may have a portion having at least a portion protruding downward from the sub-bearing 43 having a diameter smaller than that of the main shaft portion 88. That is, the portion of the sub-shaft portion 89 located inside the sub-bearing 43 may have an outer diameter equivalent to that of the main shaft portion 88.

The seal portion 82 of the balancer cover 81 receives an axial load acting on the rotating shaft 31 and slidably supports the thrust sliding portion 90 of the rotating shaft 31. By abutting the thrust sliding portion 90 and the seal portion 82 in the axial direction, communication between the inside and outside of the balancer cover 81 through the through hole 84 is blocked. The thrust sliding portion 90 of the present embodiment is the lower end surface of the sub-shaft portion 89. The thrust sliding portion 90 is a flat surface orthogonal to the axial direction. The thrust sliding portion 90 is preferably pressed against the seal portion 82 by the weight of the rotating shaft 31 and the rotor 36, the magnetic force generated between the stator 35 and the rotor 36, and the like. In this embodiment, the base shaft portion is composed of the eccentric portion 51, the main bearing 88, and the auxiliary bearing 89.

A balancer 91 is attached to a portion of the sub-shaft portion 89 that protrudes below the sub-bearing 43. The balancer 91 is formed in a disk shape, for example. A mounting hole 92 that penetrates the balancer 91 in the axial direction is formed at a position eccentric with respect to the center of the balancer 91. A sub-shaft portion 89 of the rotating shaft 31 is fixed in the mounting hole 92 by press-fitting or the like. In this case, the center of the balancer 91 is eccentric with respect to the axis O in the direction opposite to the eccentric direction of the eccentric portion 51 (the same direction as the balancer 39). That is, the balancer 91 and the eccentric portion 51 are arranged with a phase difference of 180 ° in the circumferential direction. The shape of the balancer 91 is not limited to the disk shape.

As described above, in the present embodiment, since the balancer 91 is provided on the sub-shaft portion 89, the balancer 91 and the bearing (in the present embodiment, the sub-bearing) are compared with the case where the balancer is provided on the upper surface of the rotor 36, for example. The distance to 43) can be shortened. As a result, bending of the rotor 36 and the like can be suppressed.

Here, in the compressor main body 11, centrifugal force is generated in the eccentric portion 51 and the balancers 39 and 91 as the rotating shaft 31 rotates. In this case, in order to stabilize the rotational balance of the rotating shaft 31, it is preferable to satisfy the following two equations ((1) and (2)).

Specifically, the centrifugal force acting on the eccentric portion 51 is F0, the centrifugal force acting on the balancer 91 is F1, and the centrifugal force acting on the balancer 39 is F2. In this case, it is preferable that the resultant force of each centrifugal force F0, F1 and F2 becomes 0 (see the following equation (1)). The centrifugal forces F0, F1 and F2 ^{can be calculated by mrω 2} (m: mass, r: radial distance from the axis O, ω: angular velocity).
F0-F1-F2 = 0 ... (1)

The center of action of the centrifugal force F0 is set as a reference point, the axial distance from the reference point to the center of action of the centrifugal force F1 is L1, and the axial distance from the reference point to the center of action of the centrifugal force F2 is L2. .. In this case, it is preferable that the sum of the moments acting on the rotating shaft 31 due to the centrifugal forces F1 and F2 becomes 0 (see the following equation (2)).
F1, L1-F2, L2 = 0 ... (2)

In the present embodiment, the axial distance L1 from the reference point to the center of action of the centrifugal force F1 is preferably equal to or greater than the axial distance L2 from the reference point to the center of action of the centrifugal force F2 ( L1 ≧ L2). As a result, the balancer 91 can be downsized and the amount of eccentricity can be reduced. As a result, the amount of protrusion of the balancer 91 in the radial direction with respect to the axis O can be suppressed, and the size of the compressor main body 11 in the radial direction can be reduced.

The protruding portion 87 projects downward from the inner peripheral portion of the thrust sliding portion 90. The protruding portion 87 projects downward from the lower end opening edge of the through hole 84 through the through hole 84. Specifically, the protruding portion 87 of the present embodiment protrudes below the lowest point (lower surface of the seal portion 82) of the balancer cover 81. The rotating shaft 31 has a predetermined distance in the axial direction with respect to the compression mechanism portion 33 due to the difference between the height of the cylinder chamber 46 and the axial lengths of the connecting portions 51a and 51b provided above and below the eccentric portion 51 and the eccentric portion 51. Only can be displaced (vertical backlash). Therefore, in the present embodiment, the amount of protrusion of the through hole 84 of the protrusion 87 from the lower end opening edge is larger than the predetermined distance, which is the amount of displacement of the rotating shaft 31. That is, the protrusion amount of the protruding portion 87 is set so as to always protrude downward from the lower end opening edge of the through hole 84 of the balancer cover 81 even when the rotating shaft 31 is displaced by the amount of vertical displacement. There is.

To supply the lubricating oil J to the rotating shaft 31 to each sliding portion of the compression mechanism portion 33 (for example, between the eccentric portion 51 and the roller 53, between the rotating shaft 31 and the bearings 42, 43, etc.). Supply path 94 is formed. The supply path 94 has a main flow path 95 extending coaxially with the axis O, and sub-flow paths 96 and 97 extending in the radial direction from the main flow path 95.

The lower end of the main flow path 95 is opened at the lower end surface of the rotating shaft 31 (protruding portion 87). As a result, the lubricating oil J in the case 34 can flow into the main flow path 95.

The upper end of the main flow path 95 is terminated at the lower end of the main shaft portion 88. However, the axial length of the main flow path 95 can be appropriately changed as long as it reaches at least the cylinder 41. For example, the main flow path 95 may penetrate the rotation shaft 31 in the axial direction. A twist plate or the like that promotes the rise of the lubricating oil J as the rotating shaft 31 rotates may be provided on the inner peripheral surface of the main flow path 95.

The first sub-flow path 96 is formed at a connecting portion (connecting portion 51a) between the main shaft portion 88 and the eccentric portion 51 of the rotating shaft 31. The radial inner end of the first sub-flow path 96 communicates with the main flow path 95 described above. On the other hand, the outer end portion in the radial direction of the first sub-flow path 96 is open toward the outer side in the radial direction on the outer peripheral surface of the rotating shaft 31.
The second sub-flow path 97 is formed in a portion of the sub-shaft portion 89 located in the sub-bearing 43. The radial inner end of the second sub-flow path 97 communicates with the main flow path 95 described above. On the other hand, the outer end portion in the radial direction of the second sub-flow path 97 is open toward the outer side in the radial direction on the outer peripheral surface of the rotating shaft 31.

A lower flow passage 99 is formed on the outer peripheral surface of the rotating shaft 31 (sub-shaft portion 89). The lower flow passage 99 is formed by a spiral groove formed on the outer peripheral surface of the rotating shaft 31. The lower end of the lower flow passage 99 communicates with the second sub flow passage 97. On the other hand, the upper end portion of the lower flow passage 99 is located at the upper end portion of the sub-shaft portion 89. The lower flow passage 99 guides the lubricating oil J from the lower side to the upper side when the rotation shaft 31 rotates. The lower flow passage 99 may be provided with lubricating oil J as long as it can be supplied between the outer peripheral surface of the sub-shaft portion 89 and the inner peripheral surface of the sub-bearing 43 (cylinder portion 71). In this case, for example, a groove may be formed on the inner peripheral surface of the tubular portion 71. The shape, layout, etc. of the lower flow passage 99 can be changed as appropriate.

In the main bearing 42, an upper flow passage (not shown) is formed on the inner peripheral surface of the tubular portion 61. The upper flow passage is formed in a spiral groove. The lower end of the upper flow path communicates with the first sub-passage 96. On the other hand, the upper end of the upper flow passage communicates with the inside of the case 34. The upper flow passage guides the lubricating oil J from the lower side to the upper side when the rotation shaft 31 rotates. The upper flow passage may be formed on the outer peripheral surface of the main shaft portion 88.

Next, the operation of the rotary compressor 2 described above will be described.
As shown in FIG. 1, when electric power is supplied to the stator 35 of the motor unit 32, the rotating shaft 31 rotates around the axis O together with the rotor 36. Then, as the rotation shaft 31 rotates, the eccentric portion 51 and the roller 53 rotate eccentrically in the cylinder chamber 46. At this time, the rollers 53 are in sliding contact with the inner peripheral surface of the cylinder 41. As a result, the gas refrigerant is taken into the cylinder chamber 46 through the suction pipe 21, and the gas refrigerant taken into the cylinder chamber 46 is compressed.

Specifically, in the cylinder chamber 46, the gas refrigerant is sucked into the suction chamber 46a through the suction hole 56, and the gas refrigerant previously sucked from the suction hole 56 is compressed in the compression chamber 46b. Of the compressed gaseous refrigerant, the gaseous refrigerant discharged into the muffler 65 through the main bearing discharge hole 64 is discharged into the case 34 through the communication hole 66 of the muffler 65. On the other hand, of the compressed gaseous refrigerant, the gaseous refrigerant discharged into the balancer cover 81 through the auxiliary bearing discharge hole 73 flows into the muffler 65 through the communication hole 85, and then enters the case 34 through the communication hole 66 of the muffler 65. Is discharged to. The gaseous refrigerant discharged into the case 34 is sent to the condenser 3 as described above.

By the way, a pressure equivalent to the discharge pressure of the gaseous refrigerant acts on the lubricating oil J in the case 34. Therefore, the lubricating oil J flows into the main flow path 95 and rises in the main flow path 95 as the rotating shaft 31 rotates. The lubricating oil J rising in the main flow path 95 is distributed to the sub flow paths 96 and 97 by the centrifugal force accompanying the rotation of the rotating shaft 31.

The lubricating oil J distributed to the sub-flow paths 96 and 97 is discharged on the outer peripheral surface of the rotating shaft 31 and supplied to each sliding portion. For example, the lubricating oil J discharged from the first sub-flow path 96 rises in the upper flow path as the rotating shaft 31 rotates, and is supplied between the main shaft portion 88 and the main bearing 42 and the like. On the other hand, the lubricating oil J discharged from the second sub-flow path 97 rises in the lower flow passage 99 with the rotation of the rotating shaft 31, and is between the sub-shaft portion 89 and the sub-bearing 43 and the eccentric portion. It is supplied between the 51 and the roller 53 and the like. The lubricating oil J supplied to each sliding portion is discharged from the compression mechanism portion 33 between the spindle portion 88 and the main bearing 42, through the cylinder chamber 46, and the like.

Here, in the present embodiment, the thrust sliding portion 90 of the rotating shaft 31 and the sealing portion 82 of the balancer cover 81 are brought into contact with each other to seal between the rotating shaft 31 and the balancer cover 81 in the axial direction. ..
According to this configuration, since the rotary shaft 31 and the balancer cover 81 are axially sealed by the seal portion 82, the lubricating oil J contained in the case 34 does not enter the balancer cover 81. Can be suppressed. By suppressing the entry of the lubricating oil J into the balancer cover 81, even when the balancer 91 is provided on the sub-shaft portion 89, the eccentric rotation of the balancer 91 causes the lubricating oil J to rotate when the rotating shaft 31 rotates. It can be suppressed from being inhibited. As a result, the rotational resistance acting on the balancer 91 when the rotating shaft 31 is rotated can be reduced. As a result, the rotating shaft 31 can be efficiently rotated, and the compression performance can be improved.

By the way, in the rotary compressor 2, when the rotating shaft 31 is displaced upward due to vibration or the like accompanying eccentric rotation, the thrust sliding portion 90 and the seal portion 82 may be separated from each other. In this case, the gaseous refrigerant discharged into the balancer cover 81 through the auxiliary bearing discharge hole 73 may leak to the outside of the balancer cover 81 through the through hole 84.

Therefore, in the present embodiment, the protruding portion 87 is configured to protrude downward from the lower end opening edge of the through hole 84 of the balancer cover 81, which is larger than the predetermined distance which is the displacement amount of the rotating shaft 31.
According to this configuration, when the gaseous refrigerant discharged into the balancer cover 81 leaks to the outside of the balancer cover 81 through the through hole 84, it goes around the protrusion 87 and flows into the main flow path 95. Can be suppressed. As a result, it is possible to prevent the gaseous refrigerant from flowing into the supply path 94 and preventing the lubricating oil J from spreading to the sliding portion. That is, in the rotary compressor 2 of the present embodiment, the lubricating oil J can be effectively supplied to the sliding portion, and the desired lubricating performance can be obtained.

Since the refrigeration cycle device 1 of the present embodiment includes the rotary compressor 2 described above, it is possible to provide the refrigeration cycle device 1 capable of improving operation reliability and compression performance over a long period of time. ..

(Second Embodiment)
FIG. 4 is a partial cross-sectional view of the rotary compressor 200 according to the second embodiment. In the following description, the same reference numerals will be given to the same configurations as those of the above-described embodiments, and the description thereof will be omitted.
The rotary compressor 200 of the present embodiment is described above in that a plurality of (for example, three) cylinders (upper cylinder 201, intermediate cylinder 202, and lower cylinder 203) are arranged side by side in the axial direction. It is different from the first embodiment.

In the rotary compressor 200 shown in FIG. 4, the upper cylinder 201 and the intermediate cylinder 202 are butted in the axial direction with the upper partition 210 sandwiched between them. The intermediate cylinder 202 and the lower cylinder 203 are butted in the axial direction with the lower partition portion 211 sandwiched between them. The configuration of each cylinder 201-203 is the same as that of the above-described embodiment. The upper cylinder 201, the lower cylinder 203, the main bearing 42, the sub bearing 43, and the partition portions 210 and 211 constitute the compression mechanism portion 212 of the present embodiment.

The upper end opening of the upper cylinder 201 is closed by the main bearing 42. The space defined by the upper cylinder 201, the main bearing 42, and the upper partition 210 forms the upper cylinder chamber 221.
The space defined by the intermediate cylinder 202 and the partition portions 210 and 211 forms the intermediate cylinder chamber 222.
The lower end opening of the lower cylinder 203 is closed by the auxiliary bearing 43. The space defined by the lower cylinder 203, the auxiliary bearing 43, and the lower partition portion 211 forms the lower cylinder chamber 223.

The rotating shaft 225 includes a base shaft portion 226 provided with a thrust sliding portion 90, and an auxiliary shaft portion 228 fixed to the base shaft portion 226 and forming a protruding portion 227.
The base shaft portion 226 includes a plurality of eccentric portions 231 to 233 housed in the cylinder chambers 221 to 223. Specifically, an upper eccentric portion 231 is formed in a portion of the base shaft portion 226 located in the upper cylinder chamber 221. An intermediate eccentric portion 232 is formed in a portion of the base shaft portion 226 located in the intermediate cylinder chamber 222. A lower eccentric portion 233 is formed in a portion of the base shaft portion 226 located in the lower cylinder chamber 223. The eccentric portions 231 to 233 have the same shape and the same outer shape as seen from the axial direction. Each eccentric portion 231 to 233 is eccentric with respect to the axis O by the same amount in the radial direction with a phase difference of 120 ° in the circumferential direction. That is, the eccentric directions of the eccentric portions 231 to 233 are set to be evenly distributed with each other in the circumferential direction. A roller 53 is fitted to each of the eccentric portions 231 to 233. The lower end surface of the base shaft portion 226 is a thrust sliding portion 90.

A base flow path 235 is formed in the base shaft portion 226. The base flow path 235 extends coaxially with the axis O. The lower end of the base flow path 235 is opened at the lower end surface (thrust sliding portion 90) of the base shaft portion 226. The base flow path 235 communicates with the sub flow paths 96 and 97, respectively. In addition, in the base shaft portion 226, a sub flow path may be provided at a position corresponding to each of the partition portions 210 and 211.

The protruding portion 227 formed of the auxiliary shaft portion 228 is formed in a cylindrical shape extending coaxially with the axis O. That is, the inside of the protruding portion 227 constitutes a protruding portion flow path 236 that penetrates the protruding portion 227 in the axial direction. The upper end of the protrusion 227 is fixed in the base flow path 235 by press fitting or the like. That is, the protruding portion 227 is fixed to the base shaft portion 226 in a state in which the protruding portion 227 protrudes below the thrust sliding portion 90 and the base flow path 235 and the protruding portion flow path 236 communicate with each other. The base flow path 235 and the protruding portion flow path 236 constitute the main flow path 237 of the present embodiment. The method of fixing the base shaft portion 226 of the protruding portion 227 may be a method other than press fitting.

The balancer cover 240 of the present embodiment includes a cover main body 241 that covers the auxiliary bearing 43 from below, and a thrust plate 242 attached to the cover main body 241. Also in this embodiment, the balancer cover 240 communicates with the muffler 65 through a communication hole (not shown).

The cover body 241 is formed in a bottomed cylindrical shape. The upper end portion of the cover body 241 is attached to the flange portion 72 of the auxiliary bearing 43. A storage hole 243 is formed at the bottom of the cover body 241. The accommodating hole 243 penetrates the bottom of the cover body 241 in the axial direction. The lower end of the base shaft portion 226 is accommodated in the accommodating hole 243. In the illustrated example, it is preferable that the thrust sliding portion 90 and the bottom portion (lower surface) of the cover main body 241 are arranged flush with each other.

The thrust plate 242 is formed in a disk shape having a diameter larger than that of the accommodating hole 243 described above. The thrust plate 242 closes the accommodating hole 243 from below with the outer peripheral portion fixed to the bottom of the cover main body 241 by the screw 244. A through hole 245 is formed in a portion of the thrust plate 242 that overlaps the main flow path 237 of the rotating shaft 225 when viewed from the axial direction. The inner diameter of the through hole 245 is smaller than the inner diameter of the accommodating hole 243 and larger than the outer diameter of the protrusion 227. The above-mentioned protrusion 227 penetrates into the through hole 245. As a result, the lower end opening of the main flow path 95 communicates with the inside of the case 34 below the balancer cover 81 (lower surface of the thrust plate 242).

The thrust sliding portion 90 described above is in axial contact with a portion (seal portion 242a) located around the through hole 245 on the upper surface of the thrust plate 242. As a result, the communication between the inside of the balancer cover 81 and the inside of the case 34 is cut off.

In the present embodiment, the radial gap S1 between the inner peripheral surface of the accommodating hole 243 and the outer peripheral surface of the base shaft portion 226 is the radial gap between the inner peripheral surface of the through hole 245 and the outer peripheral surface of the protruding portion 227. It is larger than the gap S2. The gaps S1 and S2 do not have to be uniform in the entire circumferential direction due to dimensional variation or the like. The gap S1 may be equal to or smaller than the gap S2.

Next, a method of manufacturing the rotary compressor 200 of the present embodiment will be described. In the following description, an assembling process of assembling the thrust plate 242 to the cover main body 241 in a state where the rotating shaft 225 and the cover main body 241 are assembled will be described.

FIG. 5 is a process diagram for explaining the assembly process.
As shown in FIG. 5, the assembling step of the thrust plate 242 of the present embodiment includes a positioning step and a fixing step.
In the positioning step, the jig 250 is used to position the thrust plate 242 with respect to the protrusion 227. Specifically, the jig 250 is formed in a cylindrical shape that is arranged coaxially with the axis O. The jig 250 has an operation unit 251 located at the lower part and a plate holding unit 252 located at the upper part.

The outer diameter of the operation unit 251 is larger than the inner diameter of the through hole 245.
The plate holding portion 252 is connected above the operating portion 251. The plate holding portion 252 is formed in a tapered shape in which the outer diameter gradually decreases toward the upper side. The minimum outer diameter of the plate holding portion 252 is smaller than the inner diameter of the through hole 245.

The inside of the jig 250 constitutes an insertion hole 253 into which the protrusion 227 can be inserted. The jig 250 is not limited to a cylindrical shape as long as it has a plate holding portion for holding the inner peripheral surface of the through hole 245 and a housing portion capable of accommodating the protruding portion 227.

In the positioning step, the plate holding portion 252 is inserted into the through hole 245 of the thrust plate 242. Then, the lower end opening edge of the through hole 245 is held by the outer peripheral surface of the plate holding portion 252. The plate holding portion 252 preferably holds the thrust plate 242 in a state where it does not protrude upward from the through hole 245.

Subsequently, the jig 250 is arranged coaxially with the axis O below the rotating shaft 225 (cover body 241), and the thrust plate 242 and the jig 250 are raised. Then, the thrust plate 242 approaches the cover main body 241 while the protruding portion 227 is inserted into the insertion hole 253 of the jig 250. The thrust plate 242 is raised until the thrust plate 242 abuts on the lower surface of the cover body 241. As a result, the size of the gap between the through hole 245 of the thrust plate 242 and the outer peripheral surface of the protrusion 227 becomes substantially uniform in the circumferential direction, and the thrust plate 242 is positioned in the radial direction with respect to the protrusion 227. .. The thrust plate 242 may be rotated in the circumferential direction with respect to the cover main body 241 in order to align the fixed portion between the thrust plate 242 and the cover main body 241.

Next, in the fixing step, the thrust plate 242 is fixed to the cover main body 241 with screws 244 (see FIG. 4). After that, by retracting the jig 250, the assembling step of the thrust plate 242 is completed.

In this embodiment, in addition to exhibiting the same effects as those of the first embodiment described above, the following effects are exhibited.
That is, in the present embodiment, by forming the base shaft portion 226 and the protruding portion 227 (auxiliary shaft portion 228) separately, the rotating shaft is stepped as in the case where the base shaft portion and the protruding portion are integrally formed. There is no need to process it into a attached shape. Therefore, the thrust sliding portion 90 with high accuracy can be easily manufactured, and the rotary compressor 200 having high manufacturing efficiency and low cost can be provided. By forming the base shaft portion 226 and the protruding portion 227 separately, the optimum material or the like for each component can be selected. Therefore, the degree of freedom in design can be improved.
By separating the base shaft portion 226 and the protruding portion 227, the shaft length of each component can be shortened, and each component can be easily formed with high accuracy.

In the present embodiment, the radial gap S1 between the inner peripheral surface of the accommodating hole 243 and the outer peripheral surface of the base shaft portion 226 is the radial gap between the inner peripheral surface of the through hole 245 and the outer peripheral surface of the protruding portion 227. The configuration is larger than the gap S2.
According to this configuration, by increasing the gap S1, the lubricating oil J existing in the balancer cover 240 can be easily accommodated in the gap S1. As a result, the lubricating oil J is likely to intervene between the outer peripheral surface of the base shaft portion 226 and the inner peripheral surface of the accommodating hole 243, and between the thrust sliding portion 90 and the seal portion 242a, thereby improving the lubrication performance. be able to.
On the other hand, by reducing the gap S2, it becomes easy to increase the contact area (seal area) between the thrust sliding portion 90 and the seal portion 242a. As a result, the sealing property can be improved, and the surface pressure acting between the thrust sliding portion 90 and the sealing portion 242a can be reduced.
Therefore, it is possible to provide a high-quality rotary compressor 200 that is power-saving and has excellent operation reliability for a long period of time. When the position of the rotating shaft 225 is displaced upward, the amount of the gaseous refrigerant discharged into the balancer cover 240 leaking to the outside of the balancer cover 240 through the through hole 245 can be suppressed.

In the present embodiment, a jig 250 having a plate holding portion 252 for holding the inner peripheral surface of the through hole 245 and an insertion hole 253 into which the protruding portion 227 is inserted is used to attach the thrust plate 242 to the protruding portion 227. It was configured to be positioned.
According to this configuration, the contact between the protrusion 227 and the thrust plate 242 can be suppressed, so that friction during operation can be suppressed.
By increasing the gap S1 as described above, it becomes easy to avoid contact between the base shaft portion 226 having a large turning radius and the cover main body 241 of the rotating shaft 225. This also makes it possible to suppress friction during operation.
As a result, it is possible to provide a high-quality rotary compressor 200 that is power-saving and has excellent operation reliability for a long period of time.

In the second embodiment, the configuration having three cylinders has been described, but a configuration having a plurality of cylinders other than three may be used.
In the second embodiment, the configuration in which the rotating shaft 225 and the balancer cover 240 are formed separately has been described, but even if any one of the rotating shaft 225 and the balancer cover 240 is formed separately. good.
In the second embodiment, the configuration in which the thrust plate 242 is assembled with the rotating shaft 225 and the cover main body 241 assembled has been described, but the configuration is not limited to this configuration. For example, the cover main body 241 may be assembled to the auxiliary bearing 43 with the cover main body 241 and the thrust plate 242 assembled in advance.

In the above-described embodiment, the configuration in which the roller 53 and the blade 55 are separate bodies has been described, but the configuration is not limited to this configuration. For example, it may be a type in which a blade and a roller are integrated.

According to at least one embodiment described above, desired lubrication performance can be obtained.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, as well as in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... Refrigeration cycle device, 2 ... Rotary compressor, 3 ... Condenser, 4 ... Expansion device, 5 ... Eccentric, 33 ... Compression mechanism, 31 ... Rotating shaft, 33 ... Compression mechanism, 34 ... Case, 41 Cylinder, 42 ... Main bearing, 43 ... Sub bearing, 51 ... Eccentric part, 81 ... Balancer cover, 82 ... Seal part, 84 ... Through hole, 87 ... Protruding part, 90 ... Thrust sliding part, 91 ... Balancer, 94 ... Supply path, 200 ... Rotary compressor, 201 ... Upper cylinder (cylinder), 202 ... Intermediate cylinder (cylinder), 203 ... Lower cylinder (cylinder), 225 ... Rotating shaft, 226 ... Base shaft, 227 ... Protruding 228 ... Auxiliary shaft, 230 ... Balancer cover, 231 ... Upper eccentric part (eccentric part), 232 ... Intermediate eccentric part (eccentric part), 233 ... Lower eccentric part (eccentric part), 240 ... Balancer cover, 241 ... cover body, 242 ... thrust plate, 242a ... seal part, 243 ... accommodating hole, 245 ... through hole, 250 ... jig

Claims (6)

Cases where lubricating oil is stored and
A rotating shaft arranged in the case and having an eccentric portion,
A compression mechanism unit having a cylinder in which the eccentric portion is housed, a main bearing that rotatably supports the rotating shaft above the cylinder, and an auxiliary bearing that rotatably supports the rotating shaft below the cylinder.
A balancer attached to the rotating shaft at a position below the auxiliary bearing, and
A balancer cover that covers the balancer from below is provided.
A through hole is formed at a position of the balancer cover that faces the rotation axis in the axial direction.
The rotating shaft includes a thrust sliding portion that axially contacts the seal portion located around the through hole of the balancer cover.
A protrusion located on the inner peripheral side of the thrust sliding portion and projecting downward from the lower end of the through hole through the through hole.
It is provided with a supply path that opens at the lower end surface of the protrusion and guides the lubricating oil.
Rotary compressor. In the rotary compressor according to claim 1,
The rotating shaft can be displaced by a predetermined distance in the axial direction with respect to the compression mechanism portion.
The protruding portion protrudes from the lower end of the through hole longer than the predetermined distance.
Rotary compressor. In the rotary compressor according to claim 1 or 2.
The rotating shaft includes a base shaft portion provided with the thrust sliding portion and a base shaft portion.
It is provided with an auxiliary shaft portion fixed to the base shaft portion and forming the protruding portion.
Rotary compressor. In the rotary compressor according to any one of claims 1 to 3.
The rotating shaft has a base shaft portion provided with the thrust sliding portion, and the rotating shaft has a base shaft portion.
The balancer cover is
A cover body that is attached to the auxiliary bearing and has an accommodating hole for accommodating the base shaft portion.
A thrust plate with which the through hole is formed and the thrust sliding portion comes into contact with the thrust plate is provided.
The radial gap of the rotating shaft between the outer peripheral surface of the base shaft portion and the inner peripheral surface of the accommodating hole is the diameter between the outer peripheral surface of the protruding portion and the inner peripheral surface of the through hole. Wider than the gap in the direction,
Rotary compressor. The method for manufacturing a rotary compressor according to claim 4.
It has an assembly step of assembling the thrust plate to the cover main body in a state where the base shaft portion is accommodated in the accommodating hole of the cover main body fixed to the auxiliary bearing.
The assembly process is
A positioning step of positioning the thrust plate with respect to the protrusion, and
It has a fixing step of fixing the positioned thrust plate to the cover body.
Manufacturing method of rotary compressor. The rotary compressor according to any one of claims 1 to 4, and the rotary compressor.
A radiator connected to the rotary compressor and
An expansion device connected to the radiator and
A refrigeration cycle apparatus including an evaporator connected between the expansion device and the rotary compressor.

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