JP7241985B1 - hermetic compressor - Google Patents

Abstract

The hermetic compressor includes a closed container forming an outer shell, a discharge pipe provided at the top of the closed container, a core fixedly held in the closed container, and wound around slots formed by the core. a stator in which a coil is housed; a rotor rotatably disposed on the inner peripheral surface side of the stator and having a communicating passage axially penetrating the interior thereof; a main shaft that rotates integrally with the rotor; and an oil separator provided on a portion of the main shaft that protrudes above the rotor. A gap is formed in the circumferential direction between the bundles of coils projecting axially from the slot on the lower end side of the coil end, and the oil separator includes a flat plate portion and a flat plate portion. and a plurality of blades provided on both sides or only on the rotor-side surface so as to stand upright with respect to the flat plate portion, and the flat plate portion includes a coil The end is arranged closer to the rotor than the upper end of the end, and among the plurality of blades, at least a portion of the blades on the rotor side are arranged so as to axially overlap with the connecting wire portion provided above the gap. There is.

Description

The present disclosure relates to a hermetic compressor mounted in an air conditioner or the like.

Conventionally, in a hermetic compressor, the refrigerating machine oil in the hermetic container becomes a spray and flows out of the compressor together with the discharged gas refrigerant, causing the oil in the compressor to run out and the heat transfer efficiency of the heat exchanger to decrease. On the other hand, a centrifugal impeller is installed above the rotor of the electric motor, and the rotation of the centrifugal impeller centrifugally separates the refrigerating machine oil from the refrigerant. There is a technique for preventing accumulation on the upper end surface of the stator (see, for example, Patent Document 1).

Japanese Patent No. 5813215

In the hermetic compressor of Patent Document 1, when there is a flow path from the centrifugal impeller to the inner wall of the closed container at the installation height of the centrifugal impeller, the refrigerating machine oil and the refrigerant accelerated by the centrifugal impeller flow in the centrifugal direction. After it flows out and collides with the inner wall of the closed container, it flows into the upper end surface of the stator, and the refrigerant accumulated on the upper end surface of the stator and the refrigerating machine oil after separation are swirled up again, and the amount of oil outflow to the outside of the compressor. increases. On the other hand, if there is no flow path from the centrifugal impeller to the inner wall of the closed container at the installation height of the centrifugal impeller, it is difficult to obtain the centrifugal effect of the centrifugal impeller, and the pressure near the upper end surface of the stator increases. As a result, there is a problem that the refrigerating machine oil on the upper end surface of the stator tends to accumulate without being returned.

The present disclosure has been made in order to solve the above-described problems. The purpose is to provide a type compressor.

A hermetic compressor according to the present disclosure includes a closed container forming an outer shell, a compression mechanism provided inside the closed container for compressing a refrigerant gas, a discharge pipe provided at the top of the closed container, a stator fixedly held in the sealed container, having a core, and containing coils wound in slots formed by the core; a rotor having a communicating passage through which the refrigerant gas compressed by the compression mechanism passes through in the axial direction ; a main shaft for transmitting rotational force to the compression mechanism ; and an oil separator provided on a portion of the main shaft that protrudes above the rotor, wherein the stator protrudes from the upper end surface of the core. A gap is formed in the circumferential direction between the bundles of the coils projecting axially from the slot on the lower end side of the coil end. , the oil separator comprises a flat plate portion, a fixed portion provided in the center of the flat plate portion and fixed to the main shaft, and a fixed portion on both sides or only the rotor side surface so as to stand upright with respect to the flat plate portion. and a plurality of blades provided, wherein the flat plate portion is arranged closer to the rotor than the upper end of the coil end, and at least part of the blades on the rotor side among the plurality of blades. is arranged so as to overlap in the axial direction with a connecting wire portion provided in the upper part of the gap, and the refrigerant gas and the refrigerant contained in the refrigerant gas that flowed out in the horizontal direction through the blades on the rotor side Machine oil is made to collide with the connecting wire portion, and a passage is provided for returning the refrigerating machine oil from the upper end face of the core to the oil reservoir at the bottom of the hermetic container.

According to the hermetic compressor according to the present disclosure, the oil separator includes the flat plate portion, the fixed portion provided in the center of the flat plate portion and fixed to the main shaft, and the two-sided or rotating portion that is vertically attached to the flat plate portion. a plurality of blades provided only on the rotor-side surface, wherein the flat plate portion is arranged closer to the rotor than the upper end of the coil end, and at least one of the rotor-side blades among the plurality of blades is arranged so as to axially overlap with a connecting wire portion provided above the gap. Therefore, the refrigerating machine oil and refrigerant flowed out in the centrifugal direction by the oil separator collide with the connecting wire portion, and the sprayed oil can be effectively separated into oil lumps. In addition, the collision converts the flow velocity into static pressure, and increases the spatial pressure on the upper end surface of the stator through the clearance on the lower end side of the coil end. As a result, the oil separator does not stir up the refrigerating machine oil accumulated on the upper end surface of the stator , and the oil is returned from the upper end surface of the core to the oil pool at the bottom of the closed container by the pressure difference between the upper and lower spaces of the stator. Refrigerant oil can be returned from the passage to the oil reservoir. As a result, it is possible to suppress the amount of oil that flows out of the compressor and to suppress accumulation of refrigerating machine oil on the upper end surface of the stator.

1 is a schematic vertical cross-sectional view of a hermetic compressor according to Embodiment 1. FIG. FIG. 2 is a view of the AA cross section of FIG. 1 as viewed in the arrow direction; 2 is a schematic side view of the stator of the hermetic compressor according to Embodiment 1. FIG. 2 is a perspective view of an oil separator of the hermetic compressor according to Embodiment 1. FIG. 2 is a schematic plan view of the oil separator of the hermetic compressor according to Embodiment 1. FIG. FIG. 8 is a schematic vertical cross-sectional view of the vicinity of the upper portion of a hermetic compressor according to Embodiment 2; FIG. 11 is a schematic vertical cross-sectional view of the vicinity of the upper portion of a hermetic compressor according to Embodiment 3; FIG. 11 is a schematic vertical cross-sectional view of the vicinity of the upper portion of a hermetic compressor according to Embodiment 4; FIG. 12 is a schematic vertical cross-sectional view of the vicinity of the upper portion of a hermetic compressor according to Embodiment 5; FIG. 11 is a perspective view of an oil separator of a hermetic compressor according to Embodiment 5;

Embodiments of the present disclosure will be described below with reference to the drawings. It should be noted that the present disclosure is not limited by the embodiments described below. Also, in the following drawings, the size relationship of each component may differ from the actual size.

Embodiment 1.
FIG. 1 is a schematic vertical cross-sectional view of a hermetic compressor 100 according to Embodiment 1. FIG. FIG. 2 is a view of the AA cross section of FIG. 1 as viewed in the arrow direction. Hereinafter, the overall configuration of hermetic compressor 100 according to Embodiment 1 will be described with reference to FIGS. 1 and 2. FIG. As the hermetic compressor 100, for example, a one-cylinder rotary compressor having one cylinder 13 as shown in FIG. 1, that is, a single rotary compressor is used. The hermetic compressor 100 is not limited to a single rotary compressor, and may be a rotary compressor having a plurality of cylinders 13, such as a twin rotary compressor having two cylinders 13, for example. Also, although the hermetic compressor 100 is of the vertical type, it is not limited thereto, and may be of the horizontal type as long as the relative positions of the oil separator 60 and each component are similar to those of the vertical type.

As shown in FIG. 1, a hermetic compressor 100 includes a compression mechanism 10 for compressing a refrigerant gas, a rotor 21 and a stator 22 inside a hermetic container 1. and a motor section 20 for driving the section 10 . In the following description, the longitudinal direction of the sealed container 1 is called the axial direction, and the direction perpendicular to the axial direction is called the horizontal direction. The side is the inside, and the closed container 1 side is the outside.

A communication passage 23 is formed inside the rotor 21 so as to extend therethrough in the axial direction. A communicating passage 28 is formed inside the stator 22 so as to extend therethrough in the axial direction.

The compression mechanism 10 is composed of an eccentric shaft 12 that rotates together with the main shaft 11 , a cylinder 13 , an upper bearing 14 , a lower bearing 15 , a piston 16 , vanes (not shown), and a discharge muffler 17 . A compression chamber 30 is formed by the cylindrical cylinder 13, an upper bearing 14 attached to its axial upper end, and a lower bearing 15 attached to its lower axial end. , a vane and a piston 16 slidably fitted to the eccentric shaft portion 12 are arranged.

A horizontal vane groove (not shown) is formed in the cylinder 13, and the vane groove slidably holds the vane. The rear side of the vane is open to the space of the airtight container 1 where the gas is discharged. A horizontally extending suction port 40 is formed in the cylinder 13 and guides the refrigerant sucked from the suction muffler 41 to the compression chamber 30 . A discharge pipe 42 for discharging a high-pressure gas refrigerant to the outside of the closed container 1 is penetrated and fixed to the upper part of the closed container 1 . An oil reservoir 50 is provided at the bottom of the sealed container 1 , and a part of the compression mechanism 10 is immersed in the oil reservoir 50 .

The stator 22 has a core 24, and connecting wires of coils 25 protrude from an upper end surface 24a and a lower end surface 24b of the core 24, respectively. Coil ends 25 a are formed by the connecting wires of the stator 22 . A gap 26 is formed near the base of the coil end 25a on the lower end side, and a connecting wire is hardened with varnish or the like to form an inner wall 27 on the upper portion of the coil end 25a. A plurality of slots 24c are formed in the stator 22 by the core 24, and each slot 24c is formed on both sides of the teeth of the core 24 in the circumferential direction. A wound coil 25 is accommodated in each slot 24c. Further, as shown in FIG. 2, in the vicinity of the slots 24c, the gaps 26 are formed in the circumferential direction between bundles of the coils 25 projecting axially from the respective slots 24c. Above the gap 26 in the axial direction, there is a connecting wire portion 29 as a portion that connects the coils 25 wound around different teeth. In the connecting wire portion 29, the coils 25 densely bundled in the slot 24c spread apart in the circumferential direction from the root portion of the coil end 25a in order to connect with the coil 25 at another position. Although the crossover portion 29 may be composed of only the coil 25, the coils 25 may be fixed to each other with a fixing material such as varnish, or the coils 25 may be fixed using a cylindrical member such as resin. may be configured to

FIG. 3 is a schematic side view of stator 22 of hermetic compressor 100 according to the first embodiment. As shown in FIG. 3, the stator 22 according to Embodiment 1 assumes distributed winding, but is not limited to this. Even if the stator 22 is wound in a concentrated manner, a gap 26 is formed in the circumferential direction between bundles of the coils 25 projecting axially from each slot 24c, and the connecting wire is fixed with a resin member or the like to form an inner wall 27. If so, the same effect as distributed winding can be obtained. When the connecting wire portion 29 is viewed from the axial center side, the outer side of the coil end 25a extends over the entire circumference or almost (for example, the entire circumference 90% or more) are invisible. In the first embodiment, the connecting wire portion 29 refers to a portion of the coil end 25a where such an inner wall 27 is formed.

4 is a perspective view of oil separator 60 of hermetic compressor 100 according to Embodiment 1. FIG. As shown in FIG. 1, in the upper space 1a of the sealed container 1, an oil separator 60 is provided at a portion of the main shaft 11 protruding above the rotor 21. As shown in FIG. As shown in FIG. 4, the oil separator 60 has a circular flat plate portion 61, and a downwardly extending cylindrical fixing portion 64 is provided at the center of the flat plate portion 61. As shown in FIG. Note that the shape of the flat plate portion 61 is not limited to a circular shape. By press-fitting the fixing portion 64 onto the main shaft 11 , the oil separator 60 is fixed to the main shaft 11 . Note that the oil separator 60 is fixed by press-fitting the fixing portion 64 onto the main shaft 11, but this is not a limitation. For example, the fixing portion 64 may be eliminated, a hole may be made in the center of the flat plate portion 61, and the oil separator 60 may be fixed to the upper end of the main shaft 11 by screwing or the like. A plurality of cuts are formed in the flat plate portion 61, and a plurality of blades 62 are provided by bending the flat plate portion 61 up and down from the cuts. A plurality of spaces 63 are formed in the flat plate portion 61 along the circumferential direction by bending the flat plate portion 61 up and down from the cut to provide a plurality of blades 62 . Here, the blade 62 provided by bending the flat plate portion 61 upward is the upper blade 62a, and the blade 62 provided by bending the flat plate portion 61 downward is the lower blade 62b. The upper blade 62a is provided on the surface of the flat plate portion 61 on the discharge pipe 42 side, and the lower blade 62b is provided on the surface on the rotor 21 side. In addition, as shown in FIG. 1, a gap 31 is formed between the lower end of the outer peripheral portion of the lower blade 62b and the upper surface of the rotor 21. As shown in FIG.

As shown in FIGS. 1 and 3, the oil separator 60 has the flat plate portion 61 located below the upper end of the coil end 25a, and at least a portion of the lower blade 62b is axially aligned with the inner wall 27 of the coil end 25a. are placed so as to overlap each other. Here, the lower blade 62b has an axial width W1 (length in the axial direction from the upper surface of the flat plate portion 61 to the lower end of the outer peripheral portion of the lower blade 62b), and the inner wall 27 of the coil end 25a has an axial width W2. (the length from the upper end of the coil end 25a to the gap 26 in the axial direction).

FIG. 5 is a schematic plan view of oil separator 60 of hermetic compressor 100 according to the first embodiment. Regarding the installation position of the blades 62 in the horizontal direction, it is preferable that the oil separator 60 is positioned vertically so that the space 63 does not overlap with the communication passage 23 passing through the rotor 21 in the axial direction when the oil separator 60 is viewed from above. It is desirable to install the blades 62 so that they are axially symmetrical. Such placement of the vanes 62 is desirable from the standpoint of processing and the strength of the oil separator 60 . The vane 62 and the space 63 are provided only on the outer peripheral side of the flat plate portion 61, and are not provided near the center of the flat plate portion 61 for ease of processing and strength. Further, when the oil separator 60 is viewed from above, the flat plate portion 61 is arranged so as to cover the communication passage 23 of the rotor 21 . By arranging the oil separator 60 in this manner, it is possible to suppress the flow from the communication passage 23 across the oil separator 60 to the direct discharge pipe 42 .

In terms of oil flow control, it is desirable that the upper end of the upper blade 62a is higher than the lower end of the discharge pipe 42. The upper end of the upper blade 62a may be lower than the lower end of the discharge pipe 42, as shown in FIG.

Next, operation of hermetic compressor 100 according to Embodiment 1 will be described. A rotational force is transmitted to the main shaft 11 by driving the electric motor portion 20 . The rotational force transmitted to the main shaft 11 is transmitted to the eccentric shaft portion 12 attached to the main shaft 11 , and the piston 16 rotates in the compression chamber 30 together with the eccentric shaft portion 12 . When the piston 16 rotates in the compression chamber 30, low-pressure refrigerant is supplied from the suction port 40 into the compression chamber 30, and the rotation of the piston 16 reduces the volume of the compression chamber 30 and compresses the refrigerant. The vane is pressed against the piston 16 by the high-pressure refrigerant in the closed container 1, and slides horizontally in the vane groove in conjunction with the movement of the piston 16, thereby separating the low-pressure space and the high-pressure space of the compression chamber 30. play a decisive role. The compressed refrigerant passes through the discharge muffler 17 and the communication passage 23 from a discharge mechanism (not shown) formed in the upper bearing 14 and reaches the oil separator 60 installed above the rotor 21 . At this time, the refrigerant contains the refrigerating machine oil supplied to compression chamber 30 and upper bearing 14 .

Here, as the main shaft 11 rotates, the oil separator 60 rotates, and the lower blade 62b provided on the lower side of the flat plate portion 61 functions as a centrifugal fan, and the axial flow of the refrigerant that has passed through the communication passage 23 is generated. And change the direction of the flow of refrigerating machine oil to the horizontal direction. The horizontally flowing refrigerant and refrigerating machine oil are separated by the difference in density due to centrifugal force. At this time, the lower blade 62b is arranged at a height that partially overlaps the inner wall 27 of the coil end 25a formed by the connecting wire of the stator 22 in the horizontal direction. As a result, the refrigerant and refrigerating machine oil flowing out horizontally from the lower blade 62b collide with the inner wall 27, the velocity of the refrigerant flow is reduced and converted into static pressure, and the refrigerating machine oil drops as oil lumps.

In addition, since the gap 26 is formed on the lower end side of the coil end 25a, the static pressure increased by the centrifugal effect of the oil separator 60 is easily propagated to the vicinity of the upper end surface 24a of the core 24 of the stator 22, effectively boost to Moreover, not all of the refrigerating machine oil is separated, and a part of the refrigerating machine oil rises to the upper space 1a of the sealed container 1 together with the refrigerant. The refrigerating machine oil circulating in the upper space 1a adheres to the surface of the closed container 1 to form oil lumps, and accumulates along the surface of the closed container 1 on the upper end surface 24a of the core 24 of the stator 22. Since the vicinity of the upper end surface 24a of the core 24 of the stator 22 is effectively pressurized, the pressure difference between the vicinity of the lower end surface 24b of the core 24 of the stator 22 causes the stator 22 to move through the communication passage 28 of the stator 22. The refrigerating machine oil accumulated on the upper end surface 24a of the core 24 is returned to the oil reservoir 50 at the bottom of the closed container 1. As shown in FIG.

Although the refrigerating machine oil discharged into the upper space 1a of the closed container 1 adheres to the surface of the closed container 1, part of the oil cannot be completely separated and flows to the discharge pipe 42 together with the refrigerant. In Embodiment 1, the oil separator 60 is also provided with an upper blade 62 a on the upper side of the flat plate portion 61 . Since the refrigerating machine oil flowing in the direction of the discharge pipe 42 is again centrifuged by the upper blade 62a, the amount of refrigerating machine oil flowing out from the discharge pipe 42 located above the center of the oil separator 60 can be suppressed.

As shown in FIG. 4 , the oil separator 60 according to Embodiment 1 has a flat plate portion 61 on the upper and lower sides thereof based on the easiness of molding, the amount of pressure increase, and the position of the communication passage 23 of the rotor 21 . Three blades 62 are provided at a pitch of 120°. These blades 62 are bent so as to stand upright on the flat plate portion 61 in the centrifugal direction. As the number of blades 62 increases, the centrifugal separation effect and the amount of pressure rise increase, but the flow path resistance received by the blades 62 also increases, causing a decrease in compressor efficiency due to an increase in torque. For this reason, the number of blades 62 should be appropriately selected. It is also desirable to design the inclination angle and shape of the blades 62 based on the same concept. That is, in the first embodiment, the blades 62 are designed to be enlarged by bending. good.

As for the molding method, the flat plate portion 61 is cut and bent in the first embodiment, but the blades may be fixed to the flat plate portion 61 by welding or the like. The blade 62 according to Embodiment 1 has a trapezoidal shape with a low inner side and a high outer side. Here, since a general centrifugal fan sucks fluid from the inside, it is necessary to increase the height of the inside of the blades in order to increase the refrigerant flow rate. On the other hand, in the hermetic compressor 100 according to Embodiment 1, the refrigerant is pushed out from the discharge muffler 17 and flows into the oil separator 60 through the communication passage 23 of the rotor 21. Refrigerant flow rate is also ensured. Therefore, by reducing the area of the impeller 62 with a trapezoidal shape in which the inner side is low and the outer side is high, centrifugal separation can be effectively performed while reducing agitation loss.

Further, in Embodiment 1, at least a part of the lower blade 62b overlaps the inner wall 27 in the axial direction. Since the spray oil is made to collide with the inner wall 27, the rise of the spray oil can be suppressed.

Furthermore, the opening area of the gap 26 when viewed from the outer diameter side in the horizontal direction is preferably 80% or more on average. Here, the opening area of the gap 26 when viewed from the outer diameter side in the horizontal direction is the area of the portion of the gap 26 that does not overlap the rotor 21 . Conventionally, the rotor 21 is installed above the stator 22 in order to suppress vertical movement of the main shaft 11 . Therefore, since the upper end of the rotor 21 is located above the upper end surface 24a of the core 24 of the stator 22, the rotor 21 slightly closes the opening area of the gap 26 when viewed from the outer radial side in the horizontal direction. When the amount of blockage increases, it becomes difficult to propagate the pressure in the lower blade 62b.

In addition, it is preferable that the axial width of the outer peripheral portion of the lower blade 62b is larger than the axial width of the gap 31 . The lower blade 62b generates a swirling flow in the narrow space between the connecting wire portion 29 and the outer peripheral portion of the lower blade 62b. By increasing the axial width W1 of the outer peripheral portion of the lower blade 62b, the oil collides with the inner wall 27 due to the centrifugal action of the swirling flow, promoting separation of the oil. On the other hand, it is preferable not to generate a strong swirling flow in the clearance 26 on the lower end side of the coil end 25a through which the oil flows outward in order to prevent the oil from being swirled up. Therefore, the axial width W1 of the lower blade 62b is made larger than the axial width of the gap 31 (the length from the lower end of the outer peripheral portion of the lower blade 62b in the axial direction to the upper end of the rotor 21) to prevent the swirling flow. It is preferable to both promote the utilized oil and prevent the separated oil from being rolled up.

As described above, the hermetic compressor 100 according to the first embodiment includes the hermetic container 1 forming the outer shell, the compression mechanism 10 provided inside the hermetic container 1 for compressing the refrigerant gas, and the a discharge pipe 42 provided, a stator 22 fixedly held in the sealed container 1, having a core 24 and containing coils 25 wound in slots 24c formed by the core 24, and a stator A rotor 21 rotatably disposed on the inner peripheral surface side of the rotor 22 and having a communication passage 23 through which the refrigerant gas compressed by the compression mechanism 10 passes through in the axial direction; A main shaft 11 that is housed and rotates integrally with the rotor 21 to transmit rotational force to the compression mechanism 10 ; The stator 22 has a coil end 25a formed by a connecting wire of the coil 25 projecting from the upper end surface 24a of the core 24, and on the lower end side of the coil end 25a, from the slot 24c in the axial direction A gap 26 is formed in the circumferential direction between the bundles of the protruding coils 25 . The oil separator 60 includes a flat plate portion 61 , a fixed portion 64 provided in the center of the flat plate portion 61 and fixed to the main shaft 11 , and a fixed portion 64 on both sides or on the rotor 21 side so as to stand upright with respect to the flat plate portion 61 . and a plurality of blades 62 provided only on the surface, wherein the flat plate portion 61 is arranged on the rotor 21 side from the upper end of the coil end 25a, and among the plurality of blades 62, the blade on the rotor 21 side 62 is arranged so as to overlap in the axial direction with the connecting wire portion 29 provided in the upper portion of the gap 26 , and the refrigerant gas and the refrigerant flowed out in the horizontal direction through the blades 62 on the rotor 21 side. Refrigerating machine oil contained in the gas collides with the connecting wire portion 29, and a passage is provided for returning the refrigerating machine oil from the upper end surface 24a of the core 24 to the oil reservoir 50 at the bottom of the sealed container 1. .

According to hermetic compressor 100 according to Embodiment 1, oil separator 60 includes flat plate portion 61, fixed portion 64 provided at the center of flat plate portion 61 and fixed to main shaft 11, and flat plate portion 61. and a plurality of blades 62 provided on both surfaces or only on the rotor 21 side surface so as to stand upright against the coil end 25a, the flat plate portion 61 being disposed closer to the rotor 21 than the upper end of the coil end 25a, and Among the plurality of blades 62 , at least a portion of the blades 62 on the rotor 21 side are arranged so as to axially overlap the connecting wire portion 29 provided above the gap 26 . Therefore, the refrigerating machine oil and refrigerant flowed out in the centrifugal direction by the oil separator 60 collide with the connecting wire portion 29, and the sprayed oil can be effectively turned into oil lumps and separated. Further, the collision converts the flow velocity into static pressure, and increases the space pressure on the upper end surface of the stator 22 through the clearance 26 on the lower end side of the coil end 25a. As a result, the oil separator 60 does not stir up the refrigerating machine oil accumulated on the upper end surface of the stator 22 , and the pressure difference between the upper and lower spaces of the stator 22 causes the oil pool at the bottom of the sealed container 1 to move from the upper end surface 24 a of the core 24 to the oil pool at the bottom of the sealed container 1 . Refrigerating machine oil can be returned to the oil reservoir 50 from the passage for oil return to 50. - 特許庁As a result, it is possible to suppress the amount of oil flowing out of the compressor and to suppress accumulation of refrigerating machine oil on the upper end surface of the stator 22 .

Further, in the hermetic compressor 100 according to Embodiment 1, a plurality of cuts are formed in the flat plate portion 61 , and the plurality of blades 62 are bent from the cuts so as to stand upright with respect to the flat plate portion 61 . is provided.

According to hermetic compressor 100 according to Embodiment 1, the manufacturing cost of oil separator 60 can be suppressed.

In the hermetic compressor 100 according to Embodiment 1, when the oil separator 60 is viewed from above, the flat plate portion 61 of the oil separator 60 is arranged to cover the communication passage 23 of the rotor 21. .

According to the hermetic compressor 100 according to Embodiment 1, it is possible to suppress the flow from the communication passage 23 across the oil separator 60 to the discharge pipe 42 directly.

In the hermetic compressor 100 according to Embodiment 1, the axial width of the outer peripheral portion of the blades 62 on the rotor 21 side of the oil separator 60 is equal to the lower end portion of the blades 62 on the rotor 21 side. It is larger than the axial width of the gap 31 between the upper surface of the child 21 .

According to the hermetic compressor 100 according to Embodiment 1, it is possible to achieve both promotion of oil using swirling flow and prevention of separated oil from being stirred up.

Further, in the hermetic compressor 100 according to Embodiment 1, the plurality of blades 62 has a trapezoidal shape in which the inner side is lower than the outer side.

According to hermetic compressor 100 according to Embodiment 1, centrifugation can be effectively performed while reducing agitation loss.

Embodiment 2.
Embodiment 2 will be described below, but descriptions of parts that overlap with those of Embodiment 1 will be omitted, and parts that are the same as or correspond to those of Embodiment 1 will be given the same reference numerals.

FIG. 6 is a vertical cross-sectional schematic diagram of the vicinity of the upper portion of hermetic compressor 100 according to Embodiment 2. As shown in FIG. The configuration other than the oil separator 60 is the same as that shown in the first embodiment.

As shown in FIG. 6, the oil separator 60 according to Embodiment 2 is installed such that all of the lower blades 62b overlap the inner wall 27 in the axial direction. In Embodiment 1, a portion of the lower blade 62b overlaps the gap 26 in the axial direction, that is, a portion of the lower blade 62b covers the gap 26, so that the horizontal coolant flow directly reaches the gap 26. There is a risk that the refrigerating machine oil that has flowed in and accumulated on the upper end face 24a of the core 24 of the stator 22 will be swirled up again. However, in Embodiment 2, all of the lower blades 62b are installed so as to overlap the inner wall 27 in the axial direction so that the lower blades 62b do not cover the gap 26 . In this manner, by adjusting the arrangement of the oil separator 60 so that all of the horizontal refrigerant flow from the lower blades 62b collides with the inner wall 27, oil separation can be effectively promoted.

As described above, in hermetic compressor 100 according to the second embodiment, oil separator 60 is arranged such that all blades 62 on rotor 21 side overlap connecting wire portion 29 in the axial direction.

According to the hermetic compressor 100 according to Embodiment 2, the oil separator 60 is arranged such that the lower blades 62 b do not cover the gap 26 and the entire horizontal refrigerant flow from the lower blades 62 b collides with the inner wall 27 . is arranged, it is possible to effectively promote oil separation.

Embodiment 3.
Embodiment 3 will be described below, but the description of the parts that overlap with Embodiments 1 and 2 will be omitted, and the same or corresponding parts as those in Embodiments 1 and 2 will be given the same reference numerals.

FIG. 7 is a schematic vertical cross-sectional view of the vicinity of the upper portion of hermetic compressor 100 according to Embodiment 3. As shown in FIG. The configuration other than the oil separator 60 is the same as that shown in the first embodiment.

As shown in FIG. 7, the oil separator 60 according to Embodiment 3 has blades 62 provided only on the lower side of the flat plate portion 61 . That is, the flat plate portion 61 is provided with only the lower blade 62b. Although the oil separator 60 is installed such that all of the lower blades 62b overlap the inner wall 27 in the axial direction as in the second embodiment, the oil separator 60 is not limited thereto. Oil separator 60 may be installed such that at least a portion of lower blade 62b overlaps inner wall 27 in the axial direction, as in the first embodiment.

Since the blades 62 are provided by cutting and bending the flat plate portion 61 , there is a limit to the number or size of the blades 62 provided on the flat plate portion 61 . Therefore, in the oil separator 60 according to Embodiment 3, only the lower blade 62b is used, and the number of blades on the lower side of the flat plate portion 61 is increased. is increasing. Above and below the oil separator 60, since the amount of refrigerating machine oil contained in the refrigerant is larger on the lower side, which is the separation upstream, by increasing the separation efficiency of the lower blade 62b, the refrigeration that flows out to the upper space 1a of the closed container 1 You can reduce the amount of machine oil.

Embodiment 4.
Embodiment 4 will be described below, but descriptions of the same parts as those in Embodiments 1 to 3 will be omitted, and parts that are the same as or correspond to those in Embodiments 1 to 3 will be given the same reference numerals.

FIG. 8 is a schematic vertical cross-sectional view of the vicinity of the upper portion of hermetic compressor 100 according to Embodiment 4. As shown in FIG. The configuration other than the oil separator 60 is the same as that shown in the first and second embodiments.

As shown in FIG. 8, the upper blade 62a of the oil separator 60 according to Embodiment 4 has a trapezoidal shape with a higher inner side and a lower outer side. Moreover, a feature of the fourth embodiment resides in the positional relationship with the lead wire 70 . The lead wire 70 extends from the coil end 25 a of the stator 22 and is connected to the terminal 2 provided on the top of the sealed container 1 . In general, the greater the height of the blades 62, the more the centrifugal separation effect is promoted. Therefore, the oil separator 60 according to Embodiment 4 has a shape that takes into account both the enlargement of the blades 62 and the securing of the distance between the blades 62 and the lead wires 70 . Since the lead wire 70 is generally deformed along the coil end 25a and connected to the terminal 2, there is a risk of contact with the blade 62 only near the outside of the upper blade 62a. That is, if only the outer side of the upper blade 62a is lowered, the interference with the lead wire 70 is not affected even if the inner side is raised. Therefore, by increasing the height of the inner upper blade 62a, the flow rate of the centrifugal refrigerant can be increased and the sprayed oil can be effectively separated. Further, by lowering the outer side of the upper blade 62a, the stirring loss can be reduced without affecting the interference with the lead wire 70.

In FIG. 8, only the upper blade 62a has a trapezoidal shape in which the inside is high and the outside is low. Further, as shown in the modified example of the first embodiment, considering the molding method and the centrifugal separation effect, the shape may be appropriately changed instead of the trapezoidal shape.

As described above, in the hermetic compressor 100 according to the fourth embodiment, at least the blades 62 provided on the surface on the discharge pipe 42 side among the plurality of blades 62 have a trapezoidal shape in which the inner side is higher than the outer side.

According to the hermetic compressor 100 according to Embodiment 4, the refrigerant flow rate for centrifugal separation can be increased, and the sprayed oil can be effectively separated. In addition, stirring loss can be reduced without affecting interference with the lead wire 70 .

Embodiment 5.
Embodiment 5 will be described below, but the description of the parts overlapping those of Embodiments 1 to 4 will be omitted, and the same reference numerals will be given to parts that are the same as or correspond to those of Embodiments 1 to 4.

FIG. 9 is a schematic vertical cross-sectional view of the vicinity of the upper portion of hermetic compressor 100 according to Embodiment 5. As shown in FIG. FIG. 10 is a perspective view of oil separator 60 of hermetic compressor 100 according to the fifth embodiment. The configuration other than the oil separator 60 is the same as that shown in the first and second embodiments.

In Embodiment 5, two oil separators 60 provided with only the lower blades 62b are stacked in opposite directions in the axial direction. Specifically, as shown in FIG. 10, the other oil separator 60 is turned upside down against the surface of the flat plate portion 61 of the one oil separator 60 on which the blades 62 are not formed, and the flat plate portion 61 is formed. The planes on which the blades 62 are not formed are overlapped so that the mutual spaces 63 are closed.

The refrigerant and refrigerating machine oil that have flowed into the oil separator 60 from the communication passage 23 of the rotor 21 change their flow from the axial direction to the horizontal direction. There is a risk of direct outflow to 42. Embodiment 5 prevents this, and by closing the space 63 with the flat plate portions 61 of the two oil separators 60 , the flow path across the oil separators 60 can be blocked. Further, unlike the first embodiment, it is not necessary to allocate the bending directions of the blades 62 vertically. The number of blades on the upper side of 61 is also increased to obtain a further separating effect. However, since the torque increases as the number of blades increases, it is necessary to appropriately select the torque according to the specification conditions.

Moreover, in Embodiment 5, since only two oil separators 60 having only the lower blades 62b having the same structure are stacked, the manufacturing cost can be reduced. good too. For example, the oil separator 60 provided with only the upper blades 62a may be superimposed on the upper side of the oil separator 60 provided with only the lower blades 62b. 64 can be shortened. Alternatively, the blades may be fixed by welding or the like so as to stand upright on a complete flat plate portion without cuts. In either case, the oil separation effect can be promoted by closing the space 63 .

As described above, in the hermetic compressor 100 according to Embodiment 5, the oil separator 60 is provided with a plurality of blades 62 only on one side so as to stand upright with respect to the flat plate portion 61, and two oil separators are provided. 60 are arranged so that the surfaces on which the blades 62 are not formed are overlapped, and a plurality of spaces 63 formed in one flat plate portion 61 along the circumferential direction are closed by the other flat plate portion 61. are arranged as

According to the hermetic compressor 100 according to Embodiment 5, the space 63 of each of the two oil separators 60 is blocked by the flat plate portions 61 of the two oil separators 60 , thereby blocking the passage across the oil separators 60 . Further, since it is not necessary to allocate the bending directions of the blades 62 vertically, the effect of increasing the number of blades on the lower side of the flat plate portion 61 is obtained, and the number of blades on the upper side of the flat plate portion 61 is also increased to obtain a further separating effect.

1 Closed container 1a Upper space 2 Terminal 10 Compression mechanism 11 Main shaft 12 Eccentric shaft 13 Cylinder 14 Upper bearing 15 Lower bearing 16 Piston 17 Discharge muffler 20 Electric motor 21 Rotor 22 stator, 23 communication passage, 24 core, 24a upper end surface, 24b lower end surface, 24c slot, 25 coil, 25a coil end, 26 clearance, 27 inner wall, 28 communication passage, 29 connecting wire portion, 30 compression chamber, 31 clearance , 40 suction port, 41 suction muffler, 42 discharge pipe, 50 oil reservoir, 60 oil separator, 61 flat plate portion, 62 blade, 62a upper blade, 62b lower blade, 63 space, 64 fixed portion, 70 lead wire, 100 Hermetic compressor.

Claims (10)

a closed container forming an outer shell;
a compression mechanism provided inside the sealed container for compressing a refrigerant gas;
a discharge pipe provided at the top of the closed container;
a stator fixedly held in the closed container, having a core, and containing coils wound in respective slots formed by the core;
a rotor rotatably disposed on the inner peripheral surface side of the stator and having a communication passage extending through the interior in the axial direction through which the refrigerant gas compressed by the compression mechanism passes;
a main shaft that is housed in the closed container in the longitudinal direction, rotates integrally with the rotor, and transmits rotational force to the compression mechanism;
an oil separator provided on a portion of the main shaft protruding above the rotor,
The stator has coil ends formed by connecting wires of the coil protruding from the upper end surface of the core,
At the lower end side of the coil end, a gap is formed in the circumferential direction between the bundles of the coils projecting axially from the slot,
The oil separator is
a flat plate;
a fixing portion provided at the center of the flat plate portion and fixed to the main shaft;
a plurality of blades provided on both surfaces or only on the rotor side surface so as to stand upright with respect to the flat plate portion;
The flat plate portion is arranged closer to the rotor than the upper end of the coil end, and at least a part of the blades on the rotor side among the plurality of blades is a crossover wire provided above the gap. so that the refrigerant gas and the refrigerating machine oil contained in the refrigerant gas flowing out in the horizontal direction through the blades on the rotor side collide with the connecting wire portion. ,
A hermetic compressor comprising a passage for returning the refrigerating machine oil from the upper end face of the core to an oil reservoir at the bottom of the hermetic container. The oil separator is
The hermetic compressor according to claim 1, wherein all of the rotor-side blades are arranged so as to axially overlap with the connecting wire portion. A notch is formed in a part of the flat plate portion,
The hermetic compressor according to claim 1 or 2, wherein the plurality of blades are bent so as to stand upright with respect to the flat plate portion. The oil separator is
having a gap between the lower end of the blade on the rotor side and the upper surface of the rotor;
3. The rotor-side blade according to claim 1, wherein the axial width of the outer periphery of the rotor-side blade is larger than the axial width of the gap between the lower end of the rotor-side blade and the upper surface of the rotor. hermetic compressor. Planar view of the oil separator,
The oil separator is
The hermetic compressor according to claim 1 or 2, wherein the flat plate portion is arranged to cover the communication passage of the rotor. The hermetic compressor according to claim 1 or 2, wherein the plurality of blades have a trapezoidal shape in which the inner side is lower than the outer side. 3. The hermetic compressor according to claim 1, wherein at least the blades provided on the surface on the discharge pipe side among the plurality of blades have a trapezoidal shape in which the inner side is higher than the outer side. The oil separator is
The plurality of blades are provided only on one side so as to stand upright with respect to the flat plate portion,
The two oil separators are arranged so that the surfaces on which the plurality of blades are not formed are superimposed,
The hermetic compressor according to claim 1 or 2, wherein a plurality of spaces formed in one of the flat plate portions along the circumferential direction are arranged so as to be closed by the other of the flat plate portions. The oil separator is
The plurality of blades are provided on both sides so as to stand upright with respect to the flat plate portion,
The discharge pipe is arranged directly above the centers of the plurality of blades provided on the surface on the discharge pipe side.
A hermetic compressor according to claim 1 . The plurality of vanes have a trapezoidal shape that is lower on the inside than on the outside.
A hermetic compressor according to claim 1 .

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