Hermetically sealed compressor

Abstract

A hermetic compressor is provided with: a hermetic container that constitutes a contour; the discharge pipe is arranged at the upper part of the closed container; a stator which is fixedly held in the sealed container, has a core, and houses a coil wound around each tooth space formed by the core; a rotor that is rotatably disposed on the inner peripheral surface side of the stator and has a communication path therein that passes through the stator in the axial direction; a main shaft accommodated in the longitudinal direction inside the sealed container and rotating integrally with the rotor; and an oil separator provided in a portion of the main shaft protruding toward an upper portion of the rotor, the stator having a coil end portion formed by a lap line of a coil protruding from an upper end surface of the core, a gap being formed in a circumferential direction between bundles of coils protruding in an axial direction from the tooth slots on a lower end side of the coil end portion, the oil separator having: a flat plate portion; the fixing part is arranged at the center of the flat plate part and fixes the main shaft; and a plurality of blades provided on both surfaces so as to be upright with respect to the flat plate section or only on the rotor-side surface, the flat plate section being disposed on the rotor side with respect to the upper end of the coil end section, and at least a portion of the rotor-side blade among the plurality of blades being disposed so as to overlap in the axial direction with a lap line section provided on the upper portion of the gap.

Description

Technical Field

[0001] The present disclosure relates to a hermetic compressor mounted on an air conditioner or the like. Background Art

[0002] In the past, in a sealed compressor, the refrigeration oil in the sealed container becomes a spray and flows out of the compressor together with the exhaust gas refrigerant, causing the oil in the compressor to dry up and the heat transfer efficiency of the heat exchanger to decrease. In response to this, there is a structure in which a centrifugal impeller is provided above the rotor of the motor, the refrigeration oil is centrifugally separated from the refrigerant by the rotation of the blades of the centrifugal impeller, and the upper space of the motor is pressurized to prevent the separated refrigeration oil from stagnating on the upper end surface of the stator (for example, refer to Patent Document 1).

[0003] Prior Art Literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent No. 5813215 Summary of the invention

[0006] Problems to be solved by the invention

[0007] In the sealed compressor of Patent Document 1, when there is a flow path from the centrifugal impeller to the inner wall of the sealed container at the installation height of the centrifugal impeller, the refrigeration oil and refrigerant accelerated by the centrifugal impeller flow out in the centrifugal direction and collide with the inner wall of the sealed container, and then flow into the upper end surface of the stator, and the refrigerant and the separated refrigeration oil accumulated on the upper end surface of the stator are rolled up again, and the oil outflow to the outside of the compressor increases. On the other hand, when there is no flow path from the centrifugal impeller to the inner wall of the sealed 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 is difficult to increase. There is a problem that the refrigeration oil on the upper end surface of the stator is not returned and is easily accumulated.

[0008] The present disclosure has been made to solve the above-mentioned problems, and an object of the present disclosure is to provide a hermetic compressor capable of suppressing the outflow of oil to the outside of the compressor and suppressing the accumulation of refrigeration oil on the upper end surface of the stator.

[0009] Solutions to Solve Problems

[0010] The hermetic compressor involved in the present disclosure comprises: a hermetic container, which forms a contour; a discharge pipe, which is arranged at the upper part of the above-mentioned hermetic container; a stator, which is fixedly held in the above-mentioned hermetic container, the above-mentioned stator has a core and accommodates a coil, and the above-mentioned coil is wound in each tooth slot formed by the above-mentioned core; a rotor, which is rotatably arranged on the inner peripheral surface side of the above-mentioned stator and has a connecting path penetrating in the axial direction inside; a main shaft, which is accommodated in the longitudinal direction of the above-mentioned hermetic container and rotates integrally with the above-mentioned rotor; and an oil separator, which is arranged at a portion of the above-mentioned main shaft protruding toward the upper part of the above-mentioned rotor, and the above-mentioned stator has a connecting passage extending from the upper end of the above-mentioned core. The coil end is formed by the overlap line of the above-mentioned coil protruding from the surface, and a gap is formed in the circumferential direction between the bundles of the above-mentioned coil protruding axially from the above-mentioned tooth slot on the lower end side of the above-mentioned coil end. The above-mentioned oil separator comprises: a flat plate portion; a fixing portion, which is arranged at the center of the above-mentioned flat plate portion and fixes the above-mentioned main shaft; and a plurality of blades, which are arranged on both surfaces or only on the surface of the above-mentioned rotor side in a manner upright relative to the above-mentioned flat plate portion, and the above-mentioned flat plate portion is arranged on the above-mentioned rotor side compared to the upper end of the above-mentioned coil end, and at least a part of the blades on the above-mentioned rotor side among the above-mentioned plurality of blades is arranged in a manner overlapping in the axial direction with the overlap line portion arranged at the upper part of the above-mentioned gap.

[0011] Effects of the Invention

[0012] According to the hermetic compressor involved in the present disclosure, the oil separator has a flat plate portion, a fixing portion provided at the center of the flat plate portion and fixing the main shaft, and a plurality of blades provided on both surfaces or only on the surface on the rotor side in a manner of being upright relative to the flat plate portion, the flat plate portion is arranged on the rotor side relative to 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 arranged in a manner of overlapping in the axial direction with the overlap line portion provided at the upper part of the gap. Therefore, the refrigeration oil and the refrigerant flowing out of the oil separator in the centrifugal direction can collide with the overlap line portion, and the spray oil can be effectively separated into oil blocks. In addition, the flow velocity is converted into static pressure by collision, and the spatial pressure of the upper end surface of the stator is increased through the gap on the lower end side of the coil end. As a result, the refrigeration oil accumulated on the upper end surface of the stator will not be rolled up by the oil separator, and the refrigeration oil can be returned to the oil storage tank from the axial flow path of the stator through the pressure difference between the upper and lower spaces of the stator. As a result, the amount of oil outflow to the outside of the compressor can be suppressed, and the accumulation of refrigeration oil on the upper end surface of the stator can be suppressed. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a schematic longitudinal sectional view of the hermetic compressor according to the first embodiment.

[0014] Figure 2 Look in the direction of the arrow Figure 1 A-A section diagram.

[0015] Figure 3 This is a schematic diagram showing a stator of the sealed compressor according to the first embodiment when viewed from the side.

[0016] Figure 4 It is a perspective view of the oil separator of the hermetic compressor according to the first embodiment.

[0017] Figure 5 It is a schematic diagram which shows a plan view of the oil separator of the hermetic compressor according to the first embodiment.

[0018] Figure 6 It is a schematic longitudinal sectional view showing the vicinity of the upper portion of the hermetic compressor according to the second embodiment.

[0019] Figure 7 It is a schematic longitudinal sectional view showing the vicinity of the upper portion of the sealed compressor according to the third embodiment.

[0020] Figure 8 It is a schematic longitudinal sectional view showing the vicinity of the upper portion of the hermetic compressor according to the fourth embodiment.

[0021] Fig. 9 It is a schematic longitudinal sectional view showing the vicinity of the upper portion of the hermetic compressor according to the fifth embodiment.

[0022] Fig.10 It is a perspective view of an oil separator of a hermetic compressor according to a fifth embodiment. DETAILED DESCRIPTION

[0023] Hereinafter, embodiments of the present disclosure will be described based on the drawings. In addition, the present disclosure is not limited by the embodiments described below. In addition, in the following drawings, the size relationship of each component may be different from the actual one.

[0024] Implementation method 1.

[0025] Figure 1 It is a schematic longitudinal sectional view of the hermetic compressor 100 according to the first embodiment. Figure 2 Look in the direction of the arrow Figure 1 Below, we use Figure 1 as well as Figure 2 The overall structure of the sealed compressor 100 according to the first embodiment is described. Figure 1The single-cylinder rotary compressor having one cylinder 13 as shown in the figure is a single-cylinder rotary compressor. In addition, the sealed compressor 100 is not limited to a single-cylinder rotary compressor, and may be a rotary compressor having a plurality of cylinders 13, such as a double-cylinder rotary compressor having two cylinders 13. In addition, the sealed compressor 100 is a longitudinal type, but is not limited thereto, and may be a transverse type if the relative positions of the oil separator 60 and each component are the same as those of the longitudinal type.

[0026] like Figure 1 As shown, the sealed compressor 100 is provided inside the sealed container 1 with: a compression mechanism 10 for compressing refrigerant gas; and a motor 20 composed of a rotor 21 and a stator 22 and driving the compression mechanism 10 via a main shaft 11. In addition, in the following description, the length direction of the sealed container 1 is referred to as an axial direction, the direction perpendicular to the axial direction is referred to as a horizontal direction, the upper side of the paper in the axial direction is referred to as an upper direction, the lower side of the paper is referred to as a lower direction, the axial center side in the horizontal direction is referred to as an inner side, and the sealed container 1 side is referred to as an outer side.

[0027] A communication passage 23 penetrating in the axial direction is formed inside the rotor 21. Also, a communication passage 28 penetrating in the axial direction is formed inside the stator 22.

[0028] 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, a vane (not shown), and a discharge muffler 17. In addition, a compression chamber 30 is formed by the cylindrical cylinder 13, the upper bearing 14 installed at the upper end portion thereof in the axial direction, and the lower bearing 15 installed at the lower end portion. In the compression chamber 30, the piston 16 and the vane that are slidably fitted to the eccentric shaft 12 are arranged.

[0029] A blade groove (not shown) is formed in the cylinder body 13 in the horizontal direction, and the blade groove holds the blade in a sliding manner. The back side of the blade is open to the space of the exhaust gas atmosphere of the closed container 1. In addition, a suction port 40 extending in the horizontal direction is formed in the cylinder body 13, and the refrigerant sucked from the suction muffler 41 is guided to the compression chamber 30. In addition, a discharge pipe 42 is fixed through the upper part of the closed container 1 to discharge the high-pressure gas refrigerant to the outside of the closed container 1. In addition, an oil storage tank 50 is provided at the bottom of the closed container 1, and a part of the compression mechanism 10 is immersed in the oil storage tank 50.

[0030] The stator 22 has a core 24, and the lap wires of the coil 25 protrude from the upper end surface 24a and the lower end surface 24b of the core 24, respectively. And the coil end 25a is formed by the lap wire of the stator 22. A gap 26 is formed near the root of the coil end 25a, that is, on the lower end side, and the lap wire is fixed to the upper part of the coil end 25a by varnish or the like to form an inner wall 27. In the stator 22, a plurality of tooth slots 24c are formed by the core 24, and each tooth slot 24c is formed on both sides of the circumference of the tooth portion of the core 24. And the wound coil 25 is accommodated in each tooth slot 24c. In addition, as Figure 2 As shown in FIG. 1 , the above-mentioned gap 26 is formed in the circumferential direction between the bundles of coils 25 protruding from each tooth slot 24c in the axial direction near the tooth slot 24c. From the gap 26 portion, a lap line portion 29 is provided as a portion for connecting the coils 25 wound on other tooth portions. In the lap line portion 29, the coils 25 tightly bundled in the tooth slot 24c are spread out in a dispersed manner in the circumferential direction from the root portion of the coil end 25a in order to connect with the coils 25 at other positions. In addition, the lap line portion 29 is sometimes composed of only the coils 25, but it can also be composed of fixing materials such as varnish to fix the coils 25 to each other, or fixing the coils 25 by a cylindrical member such as resin.

[0031] Figure 3 2 is a schematic diagram of the stator 22 of the sealed compressor 100 according to Embodiment 1 as viewed from the side. Figure 3 As shown in the figure, the stator 22 involved in the first embodiment is assumed to be distributed winding, but it is not limited to this. Even if the stator 22 is set as concentrated winding, if a gap 26 is formed in the circumferential direction between the bundles of coils 25 protruding axially from each tooth slot 24c, and the overlap line is fixed by a resin member or the like to form an inner wall 27, the same effect as distributed winding can be obtained. By extending a plurality of coils 25 in a staggered manner in the circumferential direction or using a cylindrical member or the like, an inner wall 27 is formed such that when the overlap line portion 29 is viewed from the axial center side, the outer side of the coil end 25a is not visible on the entire circumference or almost on the entire circumference (for example, more than 90% of the entire circumference). In addition, in the first embodiment, the overlap line portion 29 refers to the portion of the coil end 25a that forms such an inner wall 27.

[0032] Figure 4 1 is a perspective view of the oil separator 60 of the hermetic compressor 100 according to Embodiment 1. Figure 1 As shown in FIG. 1 , an oil separator 60 is provided in the upper space 1a of the closed container 1 at a portion of the main shaft 11 protruding toward the upper portion of the rotor 21. Figure 4As shown, the oil separator 60 has a circular flat plate portion 61, and a cylindrical fixing portion 64 extending downward is provided at the center of the flat plate portion 61. In addition, the shape of the flat plate portion 61 is not limited to a circle. And, the oil separator 60 is fixed to the main shaft 11 by pressing the fixing portion 64 onto the main shaft 11. In addition, the oil separator 60 is fixed by pressing the fixing portion 64 onto the main shaft 11, but it is not limited to this. For example, it is also possible not to provide the fixing portion 64, but to open a hole in the center of the flat plate portion 61, and fix the oil separator 60 to the upper end of the main shaft 11 by screw fixing 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 upward and downward from the cuts. In addition, a plurality of blades 62 are provided by bending the flat plate portion 61 upward and downward from the cuts, and a plurality of spaces 63 are formed in the flat plate portion 61 along the circumferential direction. 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. Figure 1 As shown, a gap 31 is formed between the lower end of the outer peripheral portion of the lower blade 62 b and the upper surface of the rotor 21 .

[0033] like Figure 1 as well as Figure 3 As shown in the figure, the oil separator 60 is arranged so that the flat plate portion 61 is located below the upper end of the coil end portion 25a and at least a portion of the lower blade 62b overlaps with the inner wall 27 of the coil end portion 25a in the axial direction. Here, the lower blade 62b has an axial width W1 (the length from the upper surface of the flat plate portion 61 to the lower end of the outer peripheral portion of the lower blade 62b in the axial direction), and the inner wall 27 of the coil end portion 25a has an axial width W2 (the length from the upper end of the coil end portion 25a to the gap 26 in the axial direction).

[0034] Figure 5 1 is a schematic diagram of the oil separator 60 of the hermetic compressor 100 according to the first embodiment when viewed from above. With regard to the horizontal position of the blade 62, it is preferably arranged such that the space 63 does not overlap with the communication path 23 penetrating the axial direction of the rotor 21 when viewed from above, and the blade 62 is arranged so as to be axially symmetrical on the upper and lower sides of the oil separator 60. It is preferable to arrange the blade 62 in this way from the perspective of processing and making the oil separator 60 strong. In addition, from the perspective of ease of processing and strength, the blade 62 and the space 63 are only arranged on the outer peripheral side of the flat plate portion 61, and are not arranged near the center of the flat plate portion 61. In addition, when viewed from above, the oil separator 60 is arranged so that the flat plate portion 61 covers the communication path 23 of the rotor 21. By arranging the oil separator 60 in this way, it is possible to suppress the oil from flowing directly from the communication path 23 to the discharge pipe 42 across the oil separator 60.

[0035] In addition, it is preferred that the upper end of the upper blade 62a is higher than the lower end of the discharge pipe 42 in terms of suppressing the oil outflow, but considering the interference with the lead wire (not shown) of the stator 22 and the discharge pressure loss, it is also possible to Figure 1 As shown in the figure, the upper end of the upper blade 62a is lower than the lower end of the discharge pipe 42.

[0036] Next, the operation of the sealed compressor 100 according to Embodiment 1 is described. The rotational force is transmitted to the main shaft 11 by driving the motor part 20. The rotational force transmitted to the main shaft 11 is transmitted to the eccentric shaft part 12 mounted on the main shaft 11, and the piston 16 rotates together with the eccentric shaft part 12 in the compression chamber 30. When the piston 16 rotates in the compression chamber 30, low-pressure refrigerant is supplied from the suction port 40 to the compression chamber 30. As the piston 16 rotates, the volume of the compression chamber 30 is reduced and the refrigerant is compressed. The blade is pushed onto the piston 16 by the high-pressure refrigerant in the sealed container 1, and slides in the blade groove in the horizontal direction in conjunction with the movement of the piston 16, playing the role of separating the low-pressure space and the high-pressure space of the compression chamber 30. The compressed refrigerant passes through the discharge silencer 17 and the communication path 23 from the discharge mechanism (not shown) formed on the upper bearing 14, and reaches the oil separator 60 provided on the upper part of the rotor 21. At this time, the refrigerant contains refrigeration oil which is supplied to the compression chamber 30 and the upper bearing 14 .

[0037] 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 becomes a centrifugal fan, changing the flow direction of the refrigerant and the refrigeration oil flowing axially through the connecting passage 23 to a horizontal direction. The refrigerant and the refrigeration oil flowing in the horizontal direction are subjected to centrifugal force and separated due to their respective density differences. At this time, the lower blade 62b is arranged at a height that partially overlaps with the inner wall 27 of the coil end 25a formed by the lap wire of the stator 22 in the horizontal direction. Therefore, the refrigerant and the refrigeration oil flowing out in the horizontal direction from the lower blade 62b collide with the inner wall 27, the speed of the refrigerant flow is reduced and converted into static pressure, and the refrigeration oil becomes an oil block and falls.

[0038] In addition, since a gap 26 is formed at 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, and the pressure is effectively increased. In addition, not all of the refrigeration oil is separated, and a part of it rises to the upper space 1a of the closed container 1 together with the refrigerant. The refrigeration oil circulating in the upper space 1a adheres to the surface of the closed container 1 and becomes an oil block, which accumulates on the upper end surface 24a of the core 24 of the stator 22 along the surface of the closed container 1. Since the vicinity of the upper end surface 24a of the core 24 of the stator 22 is effectively increased in pressure, the refrigeration oil accumulated on the upper end surface 24a of the core 24 of the stator 22 is returned to the oil storage tank 50 at the bottom of the closed container 1 through the communication path 28 of the stator 22 according to the pressure difference with the vicinity of the lower end surface 24b of the core 24 of the stator 22.

[0039] In addition, the refrigeration oil discharged into the upper space 1a of the sealed container 1 adheres to the surface of the sealed container 1, and a part of it is not completely separated and flows to the discharge pipe 42 together with the refrigerant. In the first embodiment, the oil separator 60 is also provided with an upper blade 62a on the upper side of the flat plate portion 61. In addition, the refrigeration oil flowing toward the discharge pipe 42 is centrifugally separated again by the upper blade 62a, so that the amount of refrigeration oil flowing out of the discharge pipe 42 located above the center of the oil separator 60 can be suppressed.

[0040] like Figure 4 As shown in the figure, the oil separator 60 involved in the first embodiment is provided with three blades 62 at intervals of 120° on the upper and lower sides of the flat plate portion 61 based on the ease of forming, the amount of pressure increase, and the position of the communication path 23 of the rotor 21. And these blades 62 are bent in a manner that they stand upright on the flat plate portion 61 in the centrifugal direction. In addition, the more the number of blades 62 increases, the greater the centrifugal separation effect and the amount of pressure increase, and the flow path resistance received by the blades 62 also increases, resulting in a decrease in compressor efficiency due to an increase in torque. Therefore, the number of blades 62 can be appropriately selected according to the necessary amount of pressure increase and the efficiency reduction ratio. In addition, the inclination angle and shape of the blades 62 are also preferably designed with the same concept. That is, in the first embodiment, it is designed to make the blades 62 larger by forming by bending, and the shape of the blades 62 can be either a rectangular or triangular shape, or a three-dimensional shape such as that seen in a turbo compressor.

[0041] In addition, regarding the molding method, in Embodiment 1, a cut is made in the flat plate portion 61 and the flat plate portion 61 is bent, but the present invention is not limited thereto, and the blades may be fixed to the flat plate portion 61 by welding or the like. The blades 62 involved in Embodiment 1 have a trapezoidal shape with a low inner side and a high outer side. Here, a general centrifugal fan inhales fluid from the inner side, and therefore, in order to increase the refrigerant flow rate, it is necessary to set the inner side of the blades high. On the other hand, in the sealed compressor 100 involved in Embodiment 1, the refrigerant is pushed out from the discharge muffler 17 and flows into the oil separator 60 from the connecting passage 23 of the rotor 21, and therefore, even if the inner side of the blade 62 is low, the refrigerant flow rate can be ensured. Therefore, the trapezoidal shape with a low inner side and a high outer side reduces the area of ​​the blade 62, thereby reducing the stirring loss and effectively performing centrifugal separation.

[0042] In the first embodiment, at least a portion of the lower blade 62b overlaps the inner wall 27 in the axial direction. If the overlap ratio is 50% or more, the centrifugally separated oil can effectively collide with the inner wall 27, thereby suppressing the rise of the sprayed oil.

[0043] Furthermore, the opening area of ​​the gap 26 when viewed from the horizontal outer diameter side is preferably 80% or more on average. Here, the opening area of ​​the gap 26 when viewed from the horizontal outer diameter side refers to the area of ​​the portion of the gap 26 that does not overlap with the rotor 21. Conventionally, the rotor 21 is arranged on the upper side so that its magnetic center is offset from the magnetic center of the stator 22 in order to suppress the up and down 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 opening area of ​​the gap 26 when viewed from the horizontal outer diameter side is closed by the rotor 21. If the amount of closure becomes larger, it is difficult to propagate the boost pressure at the lower blade 62b, and therefore, it is preferable to set the opening area of ​​the gap 26 as large as possible.

[0044] In addition, it is preferred 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 vortex flow in the narrow space between the overlap line 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 can be collided with the inner wall 27 by the centrifugal action of the vortex flow, and the separation of the oil can be promoted. On the other hand, in the gap 26 on the lower end side of the coil end 25a where the oil flows out to the outside, it is preferred not to generate a strong vortex flow in terms of preventing the oil from rolling up. Therefore, it is preferred that the axial width W1 of the lower blade 62b is set 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 to the upper end of the rotor 21 in the axial direction), so as to achieve the promotion of the oil by the vortex flow and the prevention of the separation oil from rolling up.

[0045] As described above, the sealed compressor 100 involved in embodiment 1 comprises: a sealed container 1 forming an outline; a discharge pipe 42 provided at the upper part of the sealed container 1; a stator 22 fixedly held in the sealed container 1 and having a core 24 and accommodating wound coils 25 in tooth slots 24c formed by the core 24; a rotor 21 rotatably arranged on the inner circumferential surface side of the stator 22 and having a connecting passage 23 passing axially therethrough inside; a main shaft 11 accommodated in the length direction in the sealed container 1 and rotating integrally with the rotor 21; and an oil separator 60 provided at a portion of the main shaft 11 protruding toward the upper part of the rotor 21, the stator 22 having a coil end 25a formed by a lap wire of the coil 25 protruding from the upper end surface 24a of the core 24, and at the lower end side of the coil end 25a, a gap 26 is formed in the circumferential direction between bundles of the coil 25 protruding axially from the tooth slots 24c. Furthermore, the oil separator 60 includes: a flat plate portion 61; a fixing portion 64 provided at the center of the flat plate portion 61 and fixing the main shaft 11; and a plurality of blades 62 provided on both surfaces or only on the surface on the rotor 21 side in an upright manner relative to the flat plate portion 61, wherein the flat plate portion 61 is arranged on the rotor 21 side relative to the upper end of the coil end portion 25a, and at least a portion of the blades 62 on the rotor 21 side among the plurality of blades 62 is arranged in a manner that axially overlaps with the overlap line portion 29 provided on the upper portion of the gap 26.

[0046] According to the sealed compressor 100 of the first embodiment, the oil separator 60 includes: a flat plate portion 61; a fixing portion 64 provided at the center of the flat plate portion 61 and fixing the main shaft 11; and a plurality of blades 62 provided on both surfaces or only on the surface on the rotor 21 side in a manner of standing upright relative to the flat plate portion 61, the flat plate portion 61 is arranged on the rotor 21 side relative to the upper end of the coil end 25a, and at least a part of the blades 62 on the rotor 21 side of the plurality of blades 62 is arranged in a manner of overlapping with the overlap line portion 29 provided at the upper part of the gap 26 in the axial direction. Therefore, the refrigerator oil and the refrigerant flowing out in the centrifugal direction through the oil separator 60 collide with the overlap line portion 29, and the spray oil can be effectively separated into oil blocks. In addition, the flow velocity is converted into static pressure by the collision, and the space pressure of the upper end surface of the stator 22 is increased through the gap 26 on the lower end side of the coil end 25a. Thus, the refrigeration oil accumulated on the upper end surface of the stator 22 is not rolled up by the oil separator 60, and the refrigeration oil can be returned to the oil storage tank 50 from the axial flow path of the stator 22 according to the pressure difference between the upper and lower spaces of the stator 22. As a result, the amount of oil outflow to the outside of the compressor can be suppressed, and the accumulation of refrigeration oil on the upper end surface of the stator 22 can be suppressed.

[0047] In the sealed compressor 100 according to the first embodiment, the plurality of cutouts are formed in the flat plate portion 61 , and the plurality of blades 62 are provided by being bent so as to stand upright from the cutouts relative to the flat plate portion 61 .

[0048] According to the hermetic compressor 100 according to the first embodiment, the manufacturing cost of the oil separator 60 can be suppressed.

[0049] Furthermore, in the hermetic compressor 100 according to Embodiment 1, the oil separator 60 is arranged such that the flat plate portion 61 covers the communication path 23 of the rotor 21 when the oil separator 60 is viewed from above.

[0050] According to the sealed compressor 100 according to the first embodiment, it is possible to suppress the oil from flowing directly from the communication passage 23 to the discharge pipe 42 by bypassing the oil separator 60 .

[0051] In the sealed compressor 100 according to Embodiment 1, the axial width of the outer peripheral portion of the blade 62 on the rotor 21 side of the oil separator 60 is larger than the axial width of the gap 31 between the lower end of the blade 62 on the rotor 21 side and the upper surface of the rotor 21 .

[0052] According to the hermetic compressor 100 according to the first embodiment, it is possible to simultaneously achieve the promotion of oil flow by the swirl flow and the prevention of separation oil swirling.

[0053] Furthermore, in the hermetic compressor 100 according to Embodiment 1, the plurality of blades 62 have a trapezoidal shape in which the inner side is lower than the outer side.

[0054] According to the hermetic compressor 100 according to the first embodiment, centrifugal separation can be performed efficiently while reducing stirring loss.

[0055] Implementation method 2.

[0056] Hereinafter, Embodiment 2 will be described, and description of contents overlapping with those of Embodiment 1 will be omitted, and portions identical to or corresponding to those of Embodiment 1 will be denoted by the same reference numerals.

[0057] Figure 6 1 is a schematic longitudinal sectional view of the vicinity of the upper portion of the hermetic compressor 100 according to Embodiment 2. The configuration other than the oil separator 60 is the same as that shown in Embodiment 1.

[0058] The oil separator 60 according to the second embodiment is as follows: Figure 6As shown in the figure, the lower blades 62b are all arranged in a manner that they overlap with the inner wall 27 in the axial direction. In the first embodiment, a part of the lower blades 62b overlaps with the gap 26 in the axial direction, that is, a part of the lower blades 62b covers the gap 26, so that the refrigerant flow in the horizontal direction directly flows into the gap 26, and there is a possibility that the refrigeration oil accumulated on the upper end surface 24a of the core 24 of the stator 22 is rolled up again. However, in the second embodiment, in order to prevent the lower blades 62b from covering the gap 26, the lower blades 62b are all arranged in a manner that they overlap with the inner wall 27 in the axial direction. In this way, by adjusting the configuration of the oil separator 60 in a manner that all the refrigerant flows in the horizontal direction formed by the lower blades 62b collide with the inner wall 27, oil separation can be effectively promoted.

[0059] As described above, in the hermetic compressor 100 according to the second embodiment, the oil separator 60 is arranged so that all of the blades 62 on the rotor 21 side overlap with the overlapped line portion 29 in the axial direction.

[0060] According to the sealed compressor 100 of Embodiment 2, the lower blades 62b do not cover the gap 26, and the oil separator 60 is arranged so that all horizontal refrigerant flows formed by the lower blades 62b collide with the inner wall 27, thereby effectively promoting oil separation.

[0061] Implementation method 3.

[0062] Hereinafter, Embodiment 3 will be described, and description of contents overlapping with Embodiments 1 and 2 will be omitted, and portions identical to or corresponding to those in Embodiments 1 and 2 will be denoted by the same reference numerals.

[0063] Figure 7 1 is a schematic longitudinal sectional view of the vicinity of the upper portion of the hermetic compressor 100 according to Embodiment 3. The configuration other than the oil separator 60 is the same as that shown in Embodiment 1.

[0064] The oil separator 60 according to the third embodiment is as follows: Figure 7 As shown in the figure, the blade 62 is only provided on the lower side of the flat plate portion 61. That is, only the lower blade 62b is provided on the flat plate portion 61. In addition, the oil separator 60 is provided so that all the lower blades 62b overlap with the inner wall 27 in the axial direction, as in the second embodiment, but it is not limited to this. The oil separator 60 may also be provided so that at least a part of the lower blade 62b overlaps with the inner wall 27 in the axial direction, as in the first embodiment.

[0065] In addition, since the blades 62 are provided by opening a cutout in the flat plate portion 61 and being bent, 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 involved in the third embodiment, by providing only the lower blades 62b, the number of blades on the lower side of the flat plate portion 61 is increased, thereby improving the separation efficiency of the refrigeration oil flowing in from the communication path 23 of the rotor 21. In the upper and lower parts of the oil separator 60, the amount of refrigeration oil contained in the refrigerant is large on the lower side which becomes the separation upstream, and therefore, by improving the separation efficiency of the lower blades 62b, the amount of refrigeration oil flowing out to the upper space 1a of the closed container 1 can be reduced.

[0066] Implementation method 4.

[0067] Hereinafter, Embodiment 4 will be described, and description of contents overlapping with Embodiments 1 to 3 will be omitted, and portions identical to or corresponding to those in Embodiments 1 to 3 will be denoted by the same reference numerals.

[0068] Figure 8 1 is a schematic longitudinal sectional view of the vicinity of the upper portion of the hermetic compressor 100 according to Embodiment 4. The configuration other than the oil separator 60 is the same as that shown in Embodiments 1 and 2.

[0069] The upper blade 62a of the oil separator 60 according to the fourth embodiment is as follows: Figure 8 As shown in FIG. 1 , the inner side is high and the outer side is low. In addition, the characteristic of the fourth embodiment lies in the positional relationship with the lead wire 70. The lead wire 70 extends from the coil end 25a of the stator 22 and is connected to the terminal 2 provided at the upper part of the sealed container 1. Generally speaking, the greater the height of the blade 62, the more the centrifugal separation effect can be promoted, but since it is close to the lead wire 70, there is a possibility that the lead wire 70 is broken. Therefore, in the oil separator 60 involved in the fourth embodiment, it is set to a shape that is committed to achieving the expansion of the blade 62 and ensuring the distance between the blade 62 and the lead wire 70 at the same time. Generally speaking, since the lead wire 70 is connected to the terminal 2 due to deformation along the coil end 25a, the part that may contact the blade 62 is only near the outer side of the upper blade 62a. That is, if only the outer side of the upper blade 62a is set low, even if the inner side is set high, there will be no influence on the interference with the lead wire 70. Therefore, by increasing the height of the inner upper blade 62a, the refrigerant flow rate of centrifugal separation can be increased, and the spray oil can be effectively separated. In addition, by setting the outer side of the upper blade 62a low, there will be no influence on the interference with the lead 70, and the stirring loss can be reduced.

[0070] In addition, Figure 8In the embodiment, only the upper blade 62a is in a trapezoidal shape with a high inner side and a low outer side, but the lower blade 62b may be formed in the same shape according to the molding method of the blade 62. In addition, as shown in the modified example of embodiment 1, the shape may not be a trapezoidal shape, and the shape may be appropriately changed in consideration of the molding method and the centrifugal separation effect.

[0071] 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.

[0072] According to the hermetic compressor 100 according to the fourth embodiment, the flow rate of the refrigerant to be centrifugally separated can be increased, and the spray oil can be separated efficiently. In addition, there is no influence on the interference with the lead wire 70, and the stirring loss can be reduced.

[0073] Implementation method 5.

[0074] Hereinafter, Embodiment 5 will be described, and description of contents overlapping with Embodiments 1 to 4 will be omitted, and portions identical to or corresponding to those in Embodiments 1 to 4 will be denoted by the same reference numerals.

[0075] Fig. 9 1 is a schematic longitudinal sectional view showing the vicinity of the upper portion of the hermetic compressor 100 according to the fifth embodiment. Fig.10 1 is a perspective view of the oil separator 60 of the hermetic compressor 100 according to Embodiment 5. The configuration other than the oil separator 60 is the same as that shown in Embodiments 1 and 2.

[0076] In the fifth embodiment, two oil separators 60 each having only the lower blades 62b are arranged to overlap each other in opposite directions in the axial direction. Fig.10 As shown, the other oil separator 60 is turned over so that the surfaces of the flat plate portion 61 without the blades 62 overlap with each other, and the spaces 63 between them are closed.

[0077] The refrigerant and refrigeration oil flowing from the communication passage 23 of the rotor 21 into the oil separator 60 change their flow direction from the axial direction to the horizontal direction, but there is a possibility that a part of them flows out to the upper side of the oil separator 60 through the space 63 and flows directly to the discharge pipe 42. In order to prevent this possibility, the fifth embodiment can block the flow path across the oil separator 60 by closing the mutual spaces 63 by the flat plate portions 61 of the two oil separators 60. In addition, unlike the first embodiment, since it is not necessary to distribute the bending direction of the blades 62 upward and downward, the effect of increasing the number of blades on the lower side of the flat plate portion 61 as shown in the third embodiment can be obtained, and at the same time, the number of blades on the upper side of the flat plate portion 61 can also be increased to obtain a further separation effect. However, since the torque increases with the increase in the number of blades, it is necessary to select appropriately according to the specification conditions.

[0078] In the fifth embodiment, since only two oil separators 60 with the same structure and only the lower blades 62b are overlapped, the manufacturing cost can be suppressed, but the shape can be appropriately changed. For example, an oil separator 60 with only the upper blades 62a can be overlapped on the upper side of the oil separator 60 with only the lower blades 62b. By so arranging, the length of the fixing part 64 of the main shaft 11 can be shortened. In addition, the blades can be fixed by welding or the like in a manner of standing upright on a complete flat plate without a cutout. In any case, the oil separation effect can be promoted by closing the space 63.

[0079] As described above, in the sealed compressor 100 involved in embodiment 5, the oil separator 60 is provided with a plurality of blades 62 only on one side in an upright manner relative to the flat plate portion 61, and the two oil separators 60 are arranged so that the surfaces on which the blades 62 are not formed overlap with each other, and are arranged in a manner such that a plurality of spaces 63 formed along the circumferential direction on the flat plate portion 61 of one side are closed by the flat plate portion 61 of the other side.

[0080] According to the sealed compressor 100 involved in the fifth embodiment, the space 63 between the two oil separators 60 is closed by the respective flat plate portions 61, thereby blocking the flow path across the oil separator 60. In addition, since there is no need to distribute the bending directions of the blades 62 upward and downward, the effect of increasing the number of blades on the lower side of the flat plate portion 61 can be obtained, and at the same time, the number of blades on the upper side of the flat plate portion 61 can also be increased to obtain a further separation effect.

[0081] Description of Reference Numerals

[0082] 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 silencer, 20 motor, 21 rotor, 22 stator, 23 communication path, 24 core, 24a upper end surface, 24b lower end surface, 24c tooth groove, 25 coil, 25a coil end, 26 gap, 27 inner wall, 28 communication path, 29 lap wire, 30 compression chamber, 31 gap, 40 suction port, 41 suction silencer, 42 discharge pipe, 50 oil storage tank, 60 oil separator, 61 flat plate, 62 blade, 62a upper blade, 62b lower blade, 63 space, 64 fixing part, 70 lead wire, 100 closed compressor

Claims

1. A hermetic compressor, characterized in that: The above-mentioned hermetic compressor has: a closed container, the closed container forming the outline; A discharge pipe, which is arranged at the upper part of the sealed container; A stator, the stator being fixedly held in the sealed container, the stator having a core and accommodating a coil, the coil being wound in each tooth slot formed by the core; a rotor rotatably disposed on the inner peripheral surface side of the stator and having a communication path penetrating in the axial direction therein; a main shaft which is accommodated in the longitudinal direction of the sealed container and rotates integrally with the rotor; and an oil separator provided at a portion of the main shaft protruding toward an upper portion of the rotor, The stator has a coil end portion formed by a lap wire of the coil protruding from an 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 protruding in the axial direction from the tooth slots. The above oil separator has: Flat plate department; a fixing portion, which is disposed at the center of the flat plate portion and fixes the main shaft; and a plurality of blades, the plurality of blades being provided on both surfaces or only on the surface on the rotor side in a manner of standing upright relative to the flat plate portion, The flat plate portion is arranged on the rotor side relative to an upper end of the coil end portion, and at least a portion of the blades on the rotor side of the plurality of blades is arranged to overlap an overlap line portion provided at an upper portion of the gap in the axial direction.

2. The hermetic compressor according to claim 1, wherein: The oil separator is arranged so that all the blades on the rotor side overlap with the overlapped line portion in the axial direction.

3. The hermetic compressor according to claim 1 or 2, wherein: A notch is formed in a portion of the flat plate portion. The plurality of blades are bent and arranged to stand upright relative to the flat plate portion.

4. The hermetic compressor according to any one of claims 1 to 3, wherein: In the oil separator, an axial width of an outer peripheral portion of the rotor-side blade is larger than an axial width of a gap between a lower end portion of the rotor-side blade and an upper surface of the rotor.

5. The hermetic compressor according to any one of claims 1 to 4, wherein: The oil separator is arranged such that the flat plate portion covers the communication path of the rotor in a plan view of the oil separator.

6. The hermetic compressor according to any one of claims 1 to 5, wherein: The plurality of blades have a trapezoidal shape in which the inner side is lower than the outer side.

7. The hermetic compressor according to any one of claims 1 to 5, wherein: At least one of the plurality of blades provided on a surface on the discharge pipe side has a trapezoidal shape with an inner side higher than an outer side.

8. The hermetic compressor according to any one of claims 1 to 7, wherein: The oil separator is provided with the plurality of blades only on one side thereof in a manner standing upright relative to the flat plate portion. The two oil separators are arranged so that the surfaces on which the plurality of blades are not formed overlap each other. A plurality of spaces formed along the circumferential direction in one of the flat plate portions are arranged so as to be closed by the other of the flat plate portions.

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