JP6715671B2 - Rotary compressor - Google Patents

Description

The present invention relates to the reliability and efficiency of a refrigerating compressor for refrigeration and air conditioning, a rotary compressor used in air and other electric compressors, and the like.

As a background art in this technical field, there is Patent Document 1. In Patent Document 1, "a rolling bearing is arranged on the upper side of the electric motor, and a rolling bearing (secondary bearing) constituting a main part of the auxiliary bearing portion is arranged on the lower side of the electric motor. The rolling bearings are provided on both sides of the electric motor. Configures a main shaft bearing that supports the main shaft part.Since the main shaft part is supported by rolling bearings on both sides of the electric motor, while suppressing the power loss of the main shaft bearing, the main shaft part of the rotating shaft is prevented from tilting. It is possible.”

JP, 2009-281165, A

The crankshaft of the compressor described in Patent Document 1 rotates substantially upright by being supported by the bearing and the centrifugal force due to the eccentricity of the compression mechanism and the centrifugal force of the balance weight that balances with the centrifugal force. However, the crankshaft is deformed by the centrifugal force, and bending occurs at the bearing as a fulcrum, and the bending causes an inclination angle of the shaft in the bearing portion. The tilt angle of the shaft causes the bearing to be unevenly contacted, which lowers the reliability of the bearing and reduces the compressor efficiency by increasing the sliding loss. In particular, there is a problem that the load on the bearing increases due to the increase in capacity and size, and the centrifugal force increases due to high-speed rotation, and the crankshaft is more easily deformed.

To suppress the deformation of the crankshaft, it is effective to increase the rigidity of the crankshaft by increasing the diameter of the crankshaft. It is necessary to increase the diameter.

An object of the present invention is to improve the rigidity of a crankshaft without being restricted by the bearing diameter and the motor diameter, thereby suppressing the deformation of the crankshaft, and improving the reliability of the bearing and the compressor efficiency.

In order to solve the above problems, the present invention includes, for example, a hermetically sealed container and a compression mechanism and an electric motor housed inside the hermetically sealed container, and the compression mechanism is an electric motor via a crankshaft. A rotary compressor that is driven and has a balance weight that is supported by at least two bearings and that balances the eccentric weight of the compression mechanism, and that has an outer diameter larger than that of the crankshaft. The ring member is configured to be closely fixed to the crankshaft.

According to the present invention, it is possible to realize a rotary compressor having high reliability and high compressor efficiency.

FIG. 1 is a diagram showing an overall structure of a scroll compressor according to a first embodiment. 3 is a schematic diagram for explaining a state in which the deformation of the crankshaft is suppressed by the ring member of the scroll compressor in Embodiment 1. FIG. 6 is an enlarged view of the balance weight and its surroundings of the scroll compressor in Embodiment 2. FIG. FIG. 7 is a diagram showing an overall structure of a scroll compressor in a third embodiment. FIG. 8 is a schematic diagram for explaining a state in which deformation of a crankshaft is suppressed by a ring member of a scroll compressor according to a third embodiment. FIG. 7 is an enlarged view of the vicinity of a ring member of a scroll compressor according to a fourth embodiment. FIG. 10 is a diagram for explaining a state in which the deformation of the crankshaft is suppressed by the ring member of the scroll compressor according to the fourth embodiment. FIG. 9 is an enlarged view of the vicinity of a ring member of a scroll compressor according to a fifth embodiment. FIG. 11 is a diagram for explaining a state in which the deformation of the crankshaft is suppressed by the ring member of the scroll compressor according to the fifth embodiment.

Embodiments of the present invention will be described below with reference to the drawings.

INDUSTRIAL APPLICABILITY The present invention is generally applicable to rotary compressors that have an eccentric weight in the compression mechanism section and balance the eccentric weight of the compression mechanism section, but a scroll compressor will be described as an example. In addition to the scroll compressor, the rotary compressor to which the present invention is applied includes a rotary compressor, a screw compressor, and the like.

This embodiment will be described with reference to FIGS.

FIG. 1 is a view showing a vertical section of a scroll compressor according to this embodiment. In FIG. 1, the scroll compressor 1 is configured by accommodating the compression mechanism unit 2, the drive unit 3, the crankshaft 300, and the like in a closed container 700.

The compression mechanism unit 2 is configured as a scroll compression mechanism including the fixed scroll 100, the orbiting scroll 200, and the frame 400 as basic elements. The frame 400 is fixed to the closed container 700 and constitutes a member for arranging the rolling bearing 401. The fixed scroll 100 includes a fixed scroll base plate 101, a scroll spiral body 102 that is a spiral wrap, an intake port 103, and a discharge port 104 as basic components, and is fixed to a frame 400 by bolts 402. The scroll spiral body 102 is erected vertically on one side of the base plate 101. The orbiting scroll 200 includes a base plate 201 for the orbiting scroll, a scroll spiral body 202 which is a spiral wrap, an orbiting scroll bearing portion 203, and a slide bearing 204 arranged in the orbiting scroll bearing portion 203 as basic components. ing. The scroll spiral body 202 is erected vertically on one side of the base plate 201. The orbiting scroll bearing portion 203 is formed so as to vertically project to the other side (the side opposite to the spiral body) of the base plate 201.

The compression chamber 130 formed by engaging the fixed scroll 100 and the orbiting scroll 200 with each other performs a compression operation in which the volume of the compression chamber 130 decreases due to the orbiting movement of the orbiting scroll 200.

The drive unit 3 that orbitally drives the orbiting scroll 200 includes an electric motor 600 including a stator 601 and a rotor 602, a crankshaft 300, an Oldham coupling 500 that is a main component of a rotation preventing mechanism of the orbiting scroll 200, a frame 400, and rolling bearings 401 and 803. The orbiting scroll bearing portion 203 and the slide bearing 204 arranged in the orbiting scroll bearing portion 203 are used as basic elements.

The Oldham's joint 500 is arranged on the back surface of the base plate 201 of the orbiting scroll 200. One set of two orthogonal key portions formed on the Oldham coupling 500 slides in the key groove that is the receiving portion of the Oldham coupling 500 configured on the frame 400, and the remaining one set is formed on the back side of the scroll scroll 202. Slide the keyway. As a result, the orbiting scroll 200 makes an orbiting motion relative to the fixed scroll 100 in the plane perpendicular to the axial direction, which is the direction in which the scroll scroll 202 is erected, without rotating about its axis.

When the crankpin 301 is eccentrically rotated by the rotation of the crankshaft 300 connected to the electric motor 600, the compression mechanism unit 2 causes the orbiting scroll 200 to orbit without rotating with respect to the fixed scroll 100 by the rotation preventing mechanism of the Oldham coupling 500. As a result, the gas is sucked into the compression chamber 130 formed by the scroll scroll 102 and the scroll scroll 202 through the suction pipe 702 and the suction port 103. By the orbiting motion of the orbiting scroll 200, the compression chamber 130 moves to the central portion to reduce the volume and compress the gas, and the compressed gas is discharged from the discharge port 104 to the discharge chamber. The gas discharged into the discharge chamber circulates around the compression mechanism section 2 and the electric motor 600, and then is discharged from the discharge pipe 701 to the outside of the compressor.

The crankshaft 300 has a main shaft portion 302, a crankpin 301, and an auxiliary bearing support portion 303 that are integrally formed. The main shaft portion 302 and the sub bearing support portion 303 are formed at the same axis center and constitute a main shaft portion. The rolling bearings 401 and 803 form a crankshaft support portion that rotatably engages the main shaft portion 302 and the auxiliary bearing support portion 303 of the crankshaft 300. The orbiting scroll bearing portion 203 is provided with the orbiting scroll 200 so that the slide bearing 204 is press-fitted into its inner diameter and the crank pin 301 of the crankshaft 300 is movably and rotatably engaged in the thrust direction which is the crankshaft direction. Has been.

The rolling bearing 401 is arranged above the electric motor 600, and the rolling bearing 803 is arranged below the electric motor 600. The rolling bearings 401 and 803 function as main shaft bearings that support the main shaft portion 302 on both sides of the electric motor 600, and respectively form a main bearing portion and a sub bearing portion. That is, the rolling bearing 401 constitutes a main bearing portion which is a part of the frame 400, and the rolling bearing 803 constitutes a main portion of the sub bearing portion 800. Since the main shaft part is supported by the rolling bearings 401 and 803 on both sides of the electric motor 600, it is possible to prevent the main shaft part of the crankshaft from tilting while suppressing the power loss of the main shaft bearing.

A housing 802 is fixed to a lower frame 801 fixed to the closed container 700 via bolts 804, and a rolling bearing 803 is inserted into the housing 802 from above.

The balance weight 403 is provided on the crankshaft 300 at a position closer to the electric motor (opposite to the crankpin) than the rolling bearing 401, which is a bearing for the main shaft.

The crankshaft 300 rotates substantially upright by being supported by the centrifugal force due to the eccentricity of the orbiting scroll 200, the centrifugal force of the balance weight 403 that balances with the centrifugal force, and the rolling bearings 401 and 803. However, the crankshaft 300 is deformed by the centrifugal force, and bending is generated around the rolling bearings 401 and 803 as fulcrums, and the bending causes a shaft inclination angle in the bearing portion. The inclination angle of the shaft causes the bearing to come into partial contact, which lowers the reliability of the rolling bearings 401 and 803 and increases the sliding loss, thereby lowering the compressor efficiency.

In order to suppress the deformation of the crank shaft 300, it is effective to increase the rigidity of the crank shaft 300 by increasing the diameter of the crank shaft 300. However, since the inner ring of the rolling bearing 401 and the rotor 602 are fixed to the crankshaft 300 by press fitting or shrink fitting, increasing the diameter of the crankshaft 300 requires increasing the diameter of the rolling bearing 401 and the rotor 602 as well. There is.

Therefore, in this embodiment, a structure in which a ring member 404 having an outer diameter larger than that of the crankshaft 300 is closely fixed to the crankshaft 300 is adopted. Deformation cannot be suppressed unless it is tightly fixed, so that, for example, tight fitting is performed by tight fitting. The interference fit includes press fit, shrink fit, and the like.

According to this embodiment, since it is not necessary to increase the diameter of the crankshaft 300, the rigidity of the crankshaft 300 can be improved without being restricted by the bearing diameter and the motor diameter.

FIG. 2 shows a schematic diagram for explaining a state in which the deformation of the crankshaft is suppressed by the ring member of the scroll compressor in the present embodiment. In FIG. 2, the crankshaft 300 is supported at two points, a main bearing and an auxiliary bearing, and the left-right direction of the drawing shows the amount of deformation of the crankshaft. Further, the balance weight and the ring member are arranged between the main bearing and the sub bearing. The one-dot chain line at the center shows a state where there is no axial deformation when the operation is stopped. On the other hand, during operation, due to the centrifugal force of the orbiting scroll and the centrifugal force of the balance weight, conventionally, as shown by the dotted line, Axial deformation occurs. On the other hand, according to the present embodiment, as shown by the solid line, by fixing the ring member in close contact with the crankshaft, the shaft deformation can be suppressed.

In this embodiment, the main shaft bearing for supporting the main shaft part 302 has a configuration having two main bearing parts and sub bearing parts. However, the present invention is not limited to this, and a main shaft bearing 3 You may have one or more.

As described above, the present embodiment includes the closed container, the compression mechanism and the electric motor housed inside the closed container, the compression mechanism is driven by the electric motor via the crankshaft, and the crankshaft has at least two crankshafts. A rotary compressor that is supported by bearings and has a balance weight for balancing the eccentric weight of the compression mechanism, so that a ring member having an outer diameter larger than the outer diameter of the crankshaft is closely fixed to the crankshaft. Configured to.

As a result, by fixing a ring member having an outer diameter larger than that of the crankshaft to the crankshaft in close contact, deformation of the crankshaft can be suppressed, and a rotary compressor with high reliability and high compressor efficiency can be obtained. Can be realized.

In this embodiment, an example in which the ring member and the balance weight are integrated will be described.

FIG. 3 is an enlarged view around the balance weight of the scroll compressor in this embodiment. In FIG. 3, except for the structure of the balance weight 403 and the ring member 404, the structure is the same as that of the first embodiment, and the description of the parts having the same functions will be omitted.

In the structure of the first embodiment, the balance weight 403 and the ring member 404 are separate components, but in the structure of the present embodiment, as shown in FIG. 3, the ring member 404 is provided integrally with the balance weight 403, Both the balance weight portion and the ring portion are fixed to the crankshaft 300 by an interference fit. As a result, the effect shown in FIG. 2 can be obtained as in the first embodiment, and further, the balance weight 403 and the ring member 404 are integrally molded, so that the number of parts can be reduced and an increase in cost can be suppressed.

The scroll compressor in this embodiment will be described with reference to FIGS. The present embodiment is the same as the first embodiment except the arrangement of the balance weight 403 and the ring member 404, and the description of the parts having the same functions will be omitted.

FIG. 4 is a view showing a vertical cross section of the scroll compressor in this embodiment. In the structure of the first embodiment, the balance weight 403 is located on the electric motor 600 side (opposite the crankpin 301 side) of the rolling bearing 401 that is the bearing for the main shaft, but in the structure of the present embodiment, as shown in FIG. A balance weight 403 is arranged between the slide bearing 204 and the rolling bearing 401. By arranging the balance weight 403 at a position close to the orbiting scroll 200, it is not necessary to place the balance weight 403 in the range from the main bearing portion to the electric motor 600, so that the ring member 404 can be arranged in a wide range. Become. Similar to the first embodiment, the ring member 404 has an outer diameter larger than that of the crankshaft 300, and has a structure in which the ring member 404 is tightly fitted to the crankshaft 300 by tight fitting.

FIG. 5 is a schematic diagram for explaining a state in which deformation of the crankshaft is suppressed by the ring member of the scroll compressor in this embodiment. In FIG. 5, as in FIG. 2, the crankshaft 300 is supported at two points of the main bearing and the sub bearing, and the horizontal direction of the drawing shows the amount of deformation of the crankshaft. The one-dot chain line at the center shows a state where there is no axial deformation when the operation is stopped. On the other hand, during operation, due to the centrifugal force of the orbiting scroll and the centrifugal force of the balance weight, conventionally, as shown by the dotted line, Axial deformation occurs. On the other hand, according to the present embodiment, as shown by the solid line, the ring deformation can be further suppressed by closely fixing the ring member to the crankshaft in a wide range.

The scroll compressor according to this embodiment will be described with reference to FIGS. The present embodiment is the same as the first embodiment except for the structure of the ring member 404, and the description of the parts having the same functions is omitted.
FIG. 6 is an enlarged view around the ring member 404 of the scroll compressor in this embodiment. In this embodiment, as shown in FIG. 6, a first ring portion 404a having a first diameter and a second ring portion 404b having a diameter larger than that of the first ring portion 404a are provided. To do. According to the present embodiment, as shown in FIG. 7, by arranging the second ring portion 404b having a large diameter at the position where the crankshaft 300 has the largest deflection, the deflection can be efficiently suppressed. By arranging the first ring portion 404a having a small diameter in this range, an increase in cost can be suppressed.

The scroll compressor in this embodiment will be described with reference to FIGS. The present embodiment is the same as the first embodiment except for the structure of the ring member 404, and the description of the parts having the same functions will be omitted.

FIG. 8 is an enlarged view around the ring member 404 of the scroll compressor in this embodiment. In the present embodiment, as shown in FIG. 8, a first ring portion 404a having a first diameter and a second ring portion 404b having a diameter larger than that of the first ring portion 404a are provided, and a second ring portion 404b is provided. The ring portion 404b is located closer to the balance weight 403 than the first ring portion 404a. According to this embodiment, the second ring portion 404b having a large diameter is arranged at a position close to the balance weight, and the first ring portion 404a having a small diameter is arranged on the rotor 602 side, so that there is a space limitation. The ring member 404 can be arranged around the electric motor 600 as well, and the deformation of the crankshaft can be suppressed as shown in FIG. 9.

Although the embodiments have been described above, the present invention is not limited to the above-described embodiments and includes various modifications. For example, the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of a certain embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of a certain embodiment.

1: scroll compressor, 2: compression mechanism part, 3: drive part, 100: fixed scroll, 101: base plate, 102: scroll spiral body, 103: suction port, 104: discharge port, 130: compression chamber, 200: Orbiting scroll, 201: base plate, 202: scroll spiral body, 203: orbiting scroll bearing part, 204: sliding bearing, 300: crankshaft, 301: crankpin, 302: main shaft part, 303: auxiliary bearing support part, 400: Frame, 401: Rolling bearing, 402: Bolt, 403: Balance weight, 404: Ring member, 404a: First ring part, 404b: Second ring part, 500: Oldham coupling, 600: Electric motor, 601: Stator, 602: Rotor, 700: Airtight container, 701: Discharge pipe, 702: Suction pipe, 800: Sub bearing part, 801: Lower frame, 802: Housing, 803: Rolling bearing, 804: Bolt

Claims (4)

An airtight container and a compression mechanism and an electric motor housed inside the airtight container are provided, the compression mechanism is driven by the electric motor via a crankshaft, and the crankshaft is supported by at least two bearings. A rotary compressor having a balance weight for balancing the eccentric weight of a compression mechanism,
A ring member having an outer diameter larger than the outer diameter of the crank shaft is closely fixed to the crank shaft ,
The balance weight and the ring member are arranged between the two bearings,
The rotary compressor is characterized in that the ring member includes a first ring portion having a first diameter and a second ring portion having a diameter larger than that of the first ring portion . The rotary compressor according to claim 1, wherein
The rotary compressor, wherein the second ring portion is arranged at a position closer to the balance weight than the first ring portion . The rotary compressor according to claim 1, wherein
A rotary compressor, wherein the ring member is provided integrally with the balance weight. The rotary compressor according to any one of claims 1 to 3 ,
It said compression mechanism is a rotary compressor, wherein the scroll compression mechanism der Rukoto which the fixed scroll and the orbiting scroll and the frame and base element.

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