JP2006144602A - Compressor and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor effectively reducing vibrations generated from a shaft or a rotor installed thereto in operation in a non-steady state or low rotation number, and to provide an air conditioner including the compressor. <P>SOLUTION: The compressor 1 has a drive part 3, a compression mechanism part 4, and a weight part 5. The drive part 3 has a stator 31 and the rotator 32, and the rotator 32 is connected with the shaft 33, so that rotation of the rotator 32 transmits motive energy to the shaft 33. The compression mechanism 4 has a rotor and a compression chamber 42 housing the rotor 41, and the rotor 41 is disposed to be eccentric with respect to a rotational shaft of the shaft 33, so that the shaft 33 is rotated for eccentric movement of the rotor 41 and fluid sucked into the compression chamber 42 is compressed. The weight part 5 is installed to the rotator 32 or the shaft 33 to enhance moment of inertia around the rotation shaft of the shaft 33. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor and an air conditioner, and more specifically, a compressor capable of effectively reducing vibrations generated in a shaft and a rotor attached to the shaft during operation at an unsteady state or at a low rotational speed, and The present invention relates to an air conditioner including such a compressor.

  Since the rotor of the compressor is generally eccentric with respect to the rotation axis of the shaft, in particular, a compressor composed of a single rotor (single rotor compressor) is not suitable for operation at an unsteady state or at a low rotational speed. There is a problem that vibration is generated in the shaft.

  In conventional single rotary compressors, due to its structure, load fluctuations during the intake, compression, and exhaust strokes are large, and it is fixed by controlling the motor torque according to the load torque pattern as opposed to the control that applied a constant voltage. The acceleration of the child was kept constant, and the vibration of the shaft during unsteady operation was suppressed.

Sharp Technical Bulletin 82 April 2002

  The present invention has been made in view of the above, and a compressor capable of effectively reducing vibration generated in a shaft and a rotor mounted thereon during operation at an unsteady time or at a low rotation speed, and An object is to provide an air conditioner including such a compressor.

  In order to achieve the above object, a compressor according to the present invention includes a stator and a rotor, and the rotor is connected to a shaft, and the drive unit transmits power to the shaft by rotating the rotor. A rotor and a compression chamber for housing the rotor, and the rotor is installed eccentrically with respect to the rotation axis of the shaft, and the rotor is eccentrically moved by the rotation of the shaft and sucked into the compression chamber. A compression mechanism that compresses the fluid, and a weight that is installed on the rotor or the shaft to enhance the moment of inertia around the rotation axis of the shaft.

  In this compressor, the moment of inertia around the rotation axis of the shaft is enhanced by providing a weight portion on the rotor or the shaft. As a result, since the shaft rotates stably during operation, there is an advantage that vibrations generated during operation at unsteady times or at low rotational speeds are reduced. In particular, the above configuration is useful in a compressor having a single rotor structure.

  Further, in the compressor according to the present invention, the diameter of the weight portion around the rotation axis is expanded because the weight portion has an enlarged diameter portion.

  In this compressor, since the weight portion has an enlarged diameter portion, the diameter around the rotation axis is expanded, so that the moment of inertia of the shaft is further enhanced by installing the weight portion on the rotor or the shaft. Is done. Thereby, since the shaft rotates more stably during operation, there is an advantage that vibration during unsteady operation or the like is more effectively reduced.

  In the compressor according to the present invention, the enlarged diameter portion has a substantially plate shape or a substantially disk shape.

  In this compressor, since the enlarged diameter portion of the weight portion has a substantially plate shape or a substantially disk shape, an advantage that the moment of inertia around the rotation axis of the weight portion can be effectively increased while suppressing an increase in the thickness of the weight portion. There is.

  In the compressor according to the present invention, the weight portion is eccentric with respect to the rotation axis of the shaft, and an intermediate weight portion is installed between the weight portion and the rotor. The rotational balance of the shaft is adjusted by balancing the eccentricity of the rotor by the eccentricity and the intermediate weight portion.

  In the compressor, the eccentricity of the rotor is balanced by the eccentricity of the weight part and the intermediate weight part, and thereby the rotational balance of the shaft is adjusted. In such a configuration, since the shaft rotates stably during operation, there is an advantage that the occurrence of vibration during unsteady operation or the like is more effectively reduced. In particular, such a configuration is useful in a compressor having a single rotor type compression mechanism section 4.

  In the compressor according to the present invention, the eccentricity of the weight portion is formed by an eccentric hole provided in the weight portion.

  In this compressor, since the eccentricity of the weight part is formed by an eccentric hole provided in the weight part, the thickness of the weight part can be increased compared to a configuration in which a balance weight is separately provided for the weight part. There is an advantage that can be reduced.

  Further, in the compressor according to the present invention, one end of the shaft is supported by a thrust bearing, and the weight portion has an airfoil shape so that a propulsive force is generated at the time of rotation. The shaft is configured to act in the direction of floating from the thrust bearing.

  In this compressor, since the weight portion has an airfoil shape, a propulsive force is generated at the time of rotation, and the propulsive force acts in a direction to lift the shaft from the bearing. In such a configuration, since the thrust force on the bearing is reduced, there is an advantage that the seizure of the bearing is suppressed during operation at a high rotational speed.

  In the compressor according to the present invention, at least a portion having the airfoil shape among the weight portions is configured by laminating thin plate members.

  In this compressor, since at least a portion having the airfoil shape of the weight portion is configured by laminating thin plate members, there is an advantage that an arbitrary airfoil shape can be easily formed.

  Moreover, the air conditioner concerning this invention contains the compressor in any one of said.

  In this air conditioner, since the above-described compressor is employed, vibration of the compressor (shaft) during operation is effectively reduced. Thereby, there exists an advantage which can suppress the noise of a system (outdoor unit) effectively.

  According to the compressor according to the present invention, since the moment of inertia around the rotation axis of the shaft is enhanced by installing the weight portion on the rotor or the shaft, the shaft rotates stably during operation. Thus, there is an advantage that vibrations generated during operation at unsteady times or at low rotational speeds are reduced.

  Hereinafter, the present invention will be described in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. In addition, constituent elements of the embodiments described below include those that can be easily replaced by those skilled in the art or those that are substantially the same.

  FIG. 1 is a sectional view showing a compressor according to an embodiment of the present invention. 2 and 3 are a plan view (FIG. 2) and a front view (FIG. 3) showing the weight portion of the compressor shown in FIG. 4-9 is a figure which shows the modification of the weight part described in FIG. 2 and FIG.

  This compressor 1 is applied to an air conditioner, for example. Such an air conditioner includes, for example, an outdoor unit disposed outside and a plurality of indoor units disposed indoors, and a refrigerant is circulated between the outdoor unit and each indoor unit so as to be indoors and outdoors. What can perform indoor air-conditioning, heating, and air-conditioning by performing heat exchange is known. In such an air conditioner, the compressor 1 is disposed in the outdoor unit and has a function of sucking and compressing the refrigerant and supplying the refrigerant to each element of the outdoor unit and the indoor unit.

  The compressor 1 has a sealed structure and is connected to other components (components of an air conditioner such as an accumulator and a heat exchanger) via a suction pipe 24 and a discharge pipe 25 (see FIG. 1). ). The compressor 1 sucks refrigerant (fluid) into the inside from the suction pipe 24, compresses it, and discharges it from the discharge pipe 25 to the outside. Thereby, the pressurized refrigerant circulates in the air conditioner. The compressor 1 includes a housing 2, a drive unit 3, a compression mechanism unit 4, and a weight unit 5.

  The housing 2 has a sealed structure in which an upper lid 22 and a bottom lid 23 are fitted into a substantially cylindrical body portion 21, and houses a drive unit 3, a compression mechanism unit 4, and the like therein. The casing 2 is arranged with its longitudinal direction standing vertically, a suction pipe 24 is installed on the lower side surface thereof, and a discharge pipe 25 is installed on its upper lid 22. Thereby, in the compressor 1, the refrigerant | coolant is comprised so that the inside of the housing | casing 2 may flow upwards from the perpendicular downward direction. Further, the bottom portion (bottom lid 23) of the housing 2 is an oil reservoir, and lubricating oil supplied to the compression mechanism portion 4 is stored in the oil reservoir. In the compressor 1, as the definition of the direction, the upper lid 22 side of the housing 2 is referred to as the upper side, and the bottom lid 23 side is referred to as the lower side.

  The drive unit 3 is a slot motor and includes a stator 31, a rotor 32, and a shaft 33. The drive unit 3 is fixed to the inner wall surface of the housing 2 by a stator 31 and is installed with the shaft 33 facing vertically downward (see FIG. 1). In addition, a gap serving as a refrigerant flow path is provided between the stator 31 and the inner wall surface of the housing 2. The lower end of the shaft 33 is supported by a bearing 34 disposed in the compression mechanism unit 4. The drive unit 3 is supplied with power from the outside of the housing 2 via wiring.

  The compression mechanism unit 4 is disposed below the drive unit 3 in the housing 2 and includes a rotor 41 and a compression chamber (cylinder) 42 that accommodates the rotor 41 (see FIG. 1). ). The compression mechanism unit 4 is connected to the shaft 33 of the drive unit 3, and power is transmitted from the drive unit 3 via the shaft 33. In the compression mechanism section 4, the rotor 41 is eccentrically moved by the rotation of the shaft 33, and the refrigerant in the compression chamber 42 is compressed. Then, the compressed refrigerant is jetted out of the compression mechanism unit 4 (inside the housing 2) through a flow path formed in the shaft 33.

  The weight portion 5 includes a substantially cylindrical main body portion 51 and a substantially disc-shaped enlarged diameter portion 52, and is installed at the upper end portion of the main body portion 51 so that the enlarged diameter portion 52 is concentric with the main body portion 51. (See FIG. 2). The weight portion 5 is made of steel or other heavy materials. Further, in the weight portion 5, the diameter of the main body portion 51 around the rotation axis is expanded when the enlarged diameter portion 52 protrudes in a bowl shape with respect to the main body portion 51 in a side view. The weight portion 5 is disposed above the drive portion 3 (on the discharge pipe 25 side), and the drive portion is provided at the lower end portion of the main body portion 51 so that the rotation axis thereof is concentric with the rotation axis of the rotor 32. 3 is fixed to the rotor 32. In addition, the weight portion 5 has a diameter that is slightly smaller than the inner diameter of the housing 2, and the weight portion 5 is located between the outer periphery of the enlarged diameter portion 52 and the inner wall surface of the housing 2 in the installed state. A gap is formed. The gap serves as a refrigerant flow path from the compression mechanism 4 to the discharge pipe 25. In the compressor 1, the weight portion 5 is attached to the rotor 32 of the driving portion 3. However, the present invention is not limited to this, and the weight portion 5 may be attached to the shaft 33.

  In the compressor 1, the refrigerant is sucked into the housing 2 from the suction pipe 24 and supplied to the compression chamber 42 of the compression mechanism unit 4. When the shaft 33 is rotationally driven by the drive unit 3, the rotary 41 moves eccentrically, and the refrigerant in the compression chamber 42 is compressed. The compressed refrigerant is sent into the housing 2 from a discharge hole in a bearing 34 installed so as to communicate with the compression chamber 42. Lubricating oil is supplied to the compression mechanism unit 4 from an oil reservoir at the bottom of the housing 2 during operation. The lubricating oil rises from the lower end of the shaft 33 through the flow path in the shaft 33 due to the centrifugal force generated by the rotation of the shaft 33, and is supplied into the compression chamber 42 of the compression mechanism unit 4. The supplied lubricating oil lubricates the compression mechanism portion 4 and then is discharged into the housing 2 through the discharge hole provided in the bearing 34 and the flow path in the shaft 33. The refrigerant containing the lubricating oil flows in the housing 2 through the gap between the driving unit 3 (stator 31) and the inner wall surface of the housing 2, and the diameter of the weight unit 5 is increased above the driving unit 3. Part 52 is reached. Then, since the enlarged diameter portion 53 rotates together with the rotor 32, when the refrigerant collides with the enlarged diameter portion 53, the lubricating oil is centrifuged from the refrigerant. Thereby, the refrigerant with reduced oil content is discharged to the outside of the housing 2 through the discharge pipe 25. Note that the lubricating oil separated from the refrigerant travels along the inner wall surface of the housing 2 and falls downward due to its own weight, and returns to the oil reservoir of the housing 2.

  According to the compressor 1, since the weight portion 5 made of a weight member is installed on the rotor 32 (or the shaft 33) of the drive unit 3, the moment of inertia around the rotation axis of the shaft 33 is enhanced. Thereby, since the shaft 33 rotates stably at the time of operation, there is an advantage that vibrations generated during operation at an unsteady time or at a low rotation speed are reduced.

  In the conventional compressor, torque control is performed when the rotor is driven in order to stabilize the rotation of the shaft. However, in such a configuration, since the drive current is inevitably increased, there is a problem in that the operating efficiency is greatly deteriorated, the capacity of the power transistor is increased, and the manufacturing cost of the inverter is increased. In this respect, the compressor 1 can stabilize the rotation of the shaft 33 with the simple configuration as described above, and therefore has an advantage that such a problem does not occur.

  Further, in the conventional compressor, the oil level of the lubricating oil in the oil reservoir below the casing 2 is applied to the side surface of the casing 2 due to the centrifugal effect caused by the rotation of the shaft and the rotor attached thereto at a high rotational speed. It is pressed and the oil level rises in a pseudo manner. At this time, naturally, the lubricating oil is likely to pass through the flow path provided between the stator 31 and the casing 2, so that it is easy to take the lubricating oil out of the compressor 1, causing a decrease in reliability. It was. In this respect, according to this compressor 1, the centrifugal separation effect of the enlarged diameter portion 5 becomes larger at higher rotational speeds, and the amount of lubricating oil taken out of the compressor 1 at higher rotational speeds can be greatly reduced. This has the advantage of reducing OC%.

  Moreover, in this compressor 1, while the weight part 5 consists of the main-body part 51 and the enlarged diameter part 52, and the enlarged diameter part 52 has a substantially plate shape (substantially disk shape), the diameter around the rotating shaft becomes small. Has been extended. In other words, the weight portion 5 has a diameter-enlarged portion 52 that protrudes like a bowl in a side view, so that the diameter around the rotation axis is expanded. Therefore, by installing the weight portion 5 on the rotor 32 (or the shaft 33), the inertia moment of the shaft 33 is further enhanced. Thereby, since the shaft 33 rotates more stably at the time of operation, there is an advantage that vibration during unsteady operation or the like is more effectively reduced. Further, since the enlarged diameter portion 52 has a substantially plate shape (substantially disk shape), there is an advantage that the moment of inertia around the rotation axis of the weight portion 5 can be effectively increased while suppressing an increase in the thickness of the weight portion 5. is there.

  Moreover, in this compressor 1, the eccentric part (eccentric hole) 53 is formed in the weight part 5 (refer FIGS. 1-3). The eccentric hole 53 is eccentric with respect to the rotation axis of the weight portion 5, and is formed so as to penetrate the weight portion 5 in the thickness direction of the weight portion 5 while being located at the approximate center of the weight portion 5 in plan view. ing. In the weight part 5, the eccentricity of the weight around the rotation axis is formed by the eccentric hole 53. Further, an intermediate weight portion 6 is installed on the lower side (compression mechanism portion 4 side) of the rotor 32 of the drive unit 3. The intermediate weight portion 6 is installed approximately in the middle of the center of gravity of the rotor 41 and the weight portion 5. Further, as described above, the rotor 41 of the compression mechanism unit 4 is installed eccentrically with respect to the rotation axis of the shaft 33.

  Here, the eccentricity of the weight part 5 and the installation position and weight of the intermediate weight part 6 are defined based on the eccentricity of the rotor 41, and the eccentricity of the rotor 41 is balanced by these so that the rotational balance of the shaft 33 is balanced. Has been adjusted. In other words, the eccentricity of the rotor 41, the eccentricity of the weight part 5, and the installation position and weight of the intermediate weight part 6 are configured to balance each other with respect to the rotation axis of the shaft 33. In such a configuration, since the shaft 33 rotates stably during operation, there is an advantage that the occurrence of vibration during unsteady operation or the like is more effectively reduced. In particular, this configuration is useful in the compressor 1 having the single rotor type compression mechanism section 4.

  In the compressor 1, the rotation balance of the shaft 33 is adjusted by forming the eccentric hole 53 in the weight portion 5 as described above. However, such a configuration is separately provided for the weight portion 5. Compared with a configuration in which a balance weight is installed (see FIGS. 4 and 5), an increase in the thickness of the weight portion 5 can be reduced, so that the length of the housing 2 can be shortened and a compact compressor can be provided. . However, the present invention is not limited thereto, and a configuration may be adopted in which a balance weight 54 is separately installed on the enlarged diameter portion 52 of the weight portion 5 and the rotational balance of the shaft 33 is adjusted by the balance weight 54 (FIGS. 4 and 5). reference). Thereby, there exists an advantage which can form the eccentricity of the weight part 5 easily.

  Moreover, in this compressor 1, the moment of inertia around the rotating shaft of the weight part 5 may be further increased by forming a thick part 55 on the circumference of the enlarged diameter part 52 of the weight part 5 ( (See FIG. 6). Thereby, there exists an advantage which can stabilize rotation of the shaft 33 with a simple structure. Further, in the above-described configuration, the rotation balance of the shaft 33 may be adjusted by forming a bias in the thickness of the thick portion 55 (not shown). Thereby, there exists an advantage which can stabilize rotation of the shaft 33 more effectively with a simple structure.

  Moreover, in this compressor 1, it is good also as a structure in which the weight part 5 (the enlarged diameter part 52) has an airfoil shape (refer FIG. 7 and FIG. 8). Specifically, for example, a plurality of slits 56 may be formed in the circumferential direction with respect to the enlarged diameter portion 52, and the slits 56 may be inclined in the thickness direction of the enlarged diameter portion 52. Further, the airfoil shape of the weight portion 5 is configured such that a propulsive force is generated in the direction in which the shaft 33 floats from the bearing 34 when rotating (upward in the housing 2). In such a configuration, when the shaft 33 rotates, the shaft floats from the bearing 34 due to the propulsive force from the weight portion 5, so that the thrust force applied to the bearing 34 is reduced. Thereby, there exists an advantage by which the seizure of the bearing 34 at the time of operation | movement at high rotation speed is suppressed. Moreover, since the flow rate of the refrigerant gas in the vicinity of the drive unit 3 is increased by the rotation of the weight unit 5 and the drive unit 3 is cooled, there is an advantage that the drive efficiency of the drive unit 3 is improved.

  Moreover, in this compressor 1, the weight part 5 is shape | molded, for example by casting. However, the present invention is not limited to this, and in the configuration in which the weight portion 5 (the enlarged diameter portion 52) has an airfoil shape as described above (see FIGS. 7 and 8), at least a part of the weight portion 5 (the enlarged diameter portion 51). Alternatively, the airfoil-shaped portion may have a structure in which thin plate members are stacked (see FIG. 9). In such a configuration, an arbitrary three-dimensional shape (airfoil shape) can be easily formed by processing the thin plate member, which is a component, into an arbitrary shape and stacking the plurality of thin plate members. Thereby, there exists an advantage which can form the inclination of the slit 56 concerning the shape of the slit 56 of the enlarged diameter part 52, and the thickness direction of the enlarged diameter part 52 easily and with high precision. In such a configuration, the thin plate members that are constituent elements are coupled by pressure bonding, bolt coupling, or the like.

  The compressor 1 is particularly preferably applied to an air conditioner. That is, (1) since the vibration of the compressor 1 (shaft 33) during operation is effectively reduced, there is an advantage that the noise of the system (outdoor unit) can be effectively suppressed. Moreover, since the weight part 5 has the effect | action which isolate | separates lubricating oil from a refrigerant | coolant, (2) Lubricating oil discharged from the compressor 1 is reduced, the reliability of a compressor improves, and it connects to this. The heat exchange efficiency of the heat exchanger is not hindered and the system maintenance burden is reduced.

  As described above, the compressor according to the present invention is useful in that vibration generated in the shaft can be effectively reduced at the time of unsteady operation or operation at a low rotation speed.

It is sectional drawing which shows the compressor concerning the Example of this invention. It is a top view which shows the weight part of the compressor described in FIG. It is a front view which shows the weight part of the compressor described in FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG. It is a figure which shows the modification of the weight part described in FIG. 2 and FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Case 21 Body 22 Upper lid 23 Bottom lid 24 Suction pipe 25 Discharge pipe 3 Drive part 31 Rotor 32 Stator 33 Shaft 34 Bearing 4 Compression mechanism part 41 Rotor 42 Compression chamber 5 Weight part, Weight part 51 Main body Part 52 Expanded part 53 Eccentric hole 54 Balance weight 55 Thick part 56 Slit 6 Intermediate weight part

Claims (8)

A drive unit that includes a stator and a rotor, and the rotor is coupled to a shaft, and transmits power to the shaft by rotating the rotor;
A fluid that has a rotor and a compression chamber that accommodates the rotor, and that the rotor is installed eccentrically with respect to the rotation axis of the shaft, and the rotor is eccentrically moved by the rotation of the shaft to be sucked into the compression chamber A compression mechanism for compressing
A weight portion that increases the moment of inertia around the rotation axis of the shaft by being installed on the rotor or the shaft;
The compressor characterized by including.   The compressor according to claim 1, wherein the weight portion has a diameter-expanded portion so that a diameter of the weight portion around a rotation axis is expanded.   The compressor according to claim 2, wherein the enlarged diameter portion has a substantially plate shape or a substantially disk shape.   The weight part is eccentric with respect to the rotation axis of the shaft, and an intermediate weight part is installed between the weight part and the rotor, and the eccentric part of the weight part and the intermediate weight part of the rotor The compressor according to any one of claims 1 to 3, wherein the rotational balance of the shaft is adjusted by balancing the eccentricity.   The compressor according to claim 4, wherein the eccentricity of the weight part is formed by an eccentric hole provided in the weight part. One end of the shaft is supported by a thrust bearing, and
6. The structure according to claim 1, wherein the weight portion has an airfoil shape to generate a propulsive force when rotating, and the propulsive force acts in a direction to float the shaft from the thrust bearing. The compressor as described in one.   The compressor according to claim 6, wherein at least a portion having the airfoil shape of the weight portion is configured by laminating thin plate members.   The air conditioner containing the compressor as described in any one of Claims 1-7.

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