JP5274361B2 - Rotary hermetic compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce vibration while minimizing mass increase without increasing outer diameters of a hermetic vessel and accumulator. <P>SOLUTION: A rotary hermetic compressor keeps an electric element M in an upper part in a hermetic vessel S, and has, in the lower part, a compression element C having: a cylinder 1; bearings 4, 5; a rolling piston 2; and a vane 3 stacked in an axial direction. An additional mass part 13 in which a height (wall thickness) in an axial direction is made higher (thicker) than an inner peripheral part is integrated with an outer peripheral edge of the compression element C. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a rotary hermetic compressor that compresses refrigerant gas used in a refrigeration air conditioning system or a hot water supply system, such as a room air conditioner, a refrigerator, and a water heater, and more particularly, a rotary hermetic compressor that can efficiently reduce vibration. Related to the machine.

  2. Description of the Related Art Conventionally, a rotary hermetic compressor having an electric element in an upper part of a sealed container and a compression element in which a cylinder, a bearing, a rolling piston, and a vane are arranged in an axial direction on the lower part is known. .

  In such a thing, there are mainly two vibration generation sources: a vibration of the rotor in the electric element and a vibration associated with the refrigerant load fluctuation in the compression chamber in the compression element.

  Vibrations from these vibration sources are transmitted through peripheral components inside the sealed container, and vibrate outer parts such as the sealed container and accumulator to generate noise.

As a conventional vibration reduction method,
a. In the upper electric element, balance weights are arranged on the upper and lower parts of the rotor, respectively, thereby reducing the vibration by balancing the rotation of the rotor and the crankshaft eccentric shaft part b. Enlarge the outer diameter of the sealed container or the outer diameter of the accumulator and increase the moment of inertia of the compressor by increasing the mass to suppress vibration c. The mass member is pressed against the cylinder by a spring and slidably held, causing the displacement between the mass member and the cylinder due to the excitation force, and the cylinder movement is suppressed by the friction generated at this time. In any case, a method involving mass increase is the mainstream (see, for example, Patent Document 1).

In addition,
d. There has also been proposed an anti-vibration ring that does not have resonance characteristics with the hermetic container, by fixing it to the inner wall of the hermetic container directly under the cylinder block by press fitting, so that a vibration-damping / sound-proofing effect can be obtained (for example, , See Patent Document 2).

Japanese Laid-Open Patent Publication No. 03-037395 (FIG. 1) JP 59-068592 (FIGS. 3 and 4)

  However, in the rotational balance adjustment by the balance weight as in the above a, even if the vibration suppression effect of the vibration component in the sealed container centrifugal direction under the high speed rotation operation of the compressor is obtained, it is most dominant during the normal speed operation to the low speed operation. The vibration suppression effect of the vibration component in the sealed container tangential direction cannot be sufficiently obtained.

  Further, increasing the outer diameter of the sealed container or the accumulator as in b above not only increases the cost of parts and materials due to the increase in the mass of the compressor but also deteriorates the environmental load that has become a problem in recent years (raw materials) Increase in usage). Furthermore, since the size of the compressor becomes larger, it is necessary to secure a mounting space when incorporating it into products such as room air conditioners, refrigerators, and water heaters, which is a major problem in promoting the downsizing and weight reduction of the final product. .

  In addition, as in c, the mass member is pressed against the cylinder by a spring to cause a displacement deformation between the mass member and the cylinder due to the excitation force, and the cylinder movement is suppressed by the friction generated at this time. In the thing, the moment of inertia of the compressor body per mass to be added is small. That is, in order to increase the moment of inertia, there is a difficulty in that the additional mass must be increased more than necessary.

  A vibration reduction technique that can expand the refrigerant discharge amount without increasing the cost of the compressor and without greatly changing the outer diameter of the sealed container and the outer diameter of the accumulator is most desired. . However, in this case, the increase in the required torque of the electric element accompanying the expansion of the refrigerant discharge amount causes an increase in rotor vibration and an increase in refrigerant load fluctuation in the compression chamber, resulting in a new problem that the vibration of the compressor increases. Occur. Such a problem has remarkably appeared in a compressor using a R410A refrigerant or a high-pressure refrigerant such as carbon dioxide as a refrigerant.

  In addition, the vibration-proof ring that does not have resonance characteristics with the sealed container as in the above d is fixed to the inner wall of the sealed container just below the cylinder block by press fitting, so that a vibration-damping and sound-proofing effect can be obtained. In this case, there is an effect of shifting the resonance characteristics of the sealed container, but it is not effective in reducing the vibration component in the tangential direction of the sealed container. Furthermore, the effect of the welded portion distortion of the compression mechanism section and the distortion of the sealed container that occurs when the compression mechanism section is welded to the sealed container through a vibration isolating ring that is press-fitted into the inner peripheral surface of the sealed container is compressed. There is a possibility that the distortion propagates to the inside of the room and deforms to cause a reduction in compressor efficiency and reliability such as stoppage of component contact.

  The technical problem of the present invention is to make it possible to reduce vibrations while minimizing an increase in mass without increasing the outer diameter of a closed container or an accumulator.

The rotary hermetic compressor according to the present invention has the following configuration. That is, the electric element having a stator and a rotor on top of the sealed container, a cylinder in its lower, bearing, rolling piston, vane Chi also compression element disposed to overlap in the axial direction, the compression element is an electric In the rotary hermetic compressor that is connected to and driven by the rotor of the element, an additional mass part is provided integrally on the outer peripheral edge of the compression element over the entire circumference .

In the rotary hermetic compressor according to the present invention, the additional mass portion provided integrally on the outer peripheral edge of the compression element over the entire circumference effectively acts to increase the moment of inertia with respect to the rotor center. . Further, the inertia moment of the compressor body per mass to be added is larger than that in which the frictional force between the mass member and the cylinder is used to suppress the movement of the cylinder as described above. For this reason, it is possible to reduce the vibration while suppressing an increase in mass to a minimum without increasing the outer diameter of the sealed container or the accumulator. For this reason, it becomes possible to expand a refrigerant | coolant discharge capacity. In addition, it is possible to effectively promote reduction of environmental burden (reduction of the amount of raw materials used), improving compressor efficiency and facilitating ensuring reliability.

It is a longitudinal cross-sectional view which shows the whole structure of the rotary hermetic compressor which concerns on Embodiment 1 of this invention. It is a cross-sectional view which shows the compression element part of the rotary hermetic compressor which concerns on Embodiment 1 of this invention. It is a schematic diagram of the additional mass part which is the principal part of the rotary hermetic compressor which concerns on Embodiment 1 of this invention. It is a schematic diagram of the additional mass part which is the principal part of the rotary hermetic compressor which concerns on Embodiment 2 of this invention. It is a schematic diagram of the additional mass part which is the principal part of the rotary hermetic compressor which concerns on Embodiment 3 of this invention. It is a schematic diagram of the additional mass part which is the principal part of the rotary hermetic compressor which concerns on Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the whole structure of the rotary type hermetic compressor which concerns on Embodiment 5 of this invention. It is a schematic diagram of the additional mass part which is the principal part of the rotary hermetic compressor which concerns on Embodiment 5 of this invention.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing the overall configuration of a rotary hermetic compressor according to Embodiment 1 of the present invention, FIG. 2 is a transverse sectional view of a compression element portion thereof, and FIG. 3 is an additional mass portion that is a main portion thereof. FIG.

  In the rotary hermetic compressor of the present embodiment, the electric element M is housed in the upper part of the hermetic container S as shown in FIG.

  1 and 2, the compression element C includes a crankshaft 6, an eccentric shaft portion 7 formed integrally with the crankshaft 6, a rolling piston 2 mounted on the eccentric shaft portion 7, and a cylinder 1 Are attached to the inside of the cylinder, and the upper bearing 4 and the lower bearing 5, the upper bearing fastening bolt 8 for fastening the upper bearing 4 and the cylinder 1, and the lower bearing 5 and the cylinder 1 are fastened. A lower bearing fastening bolt 9 is provided. Further, as shown in FIGS. 1 and 3, the height (wall thickness) in the axial direction (vertical direction) is integrally formed on the outer peripheral edge portions of the upper and lower end surfaces of the cylinder 1 so as to be higher (thicker) than the inner peripheral portion. An additional mass portion 13 composed of a thick portion is provided.

  The additional mass portion 13 escapes with a gap L from the inner peripheral surface of the sealed container S as shown in FIG. In the compression element C, the cylinder 1 is fixed to the sealed container S by spot welding at an intermediate portion in the axial direction. Usually, on the inner peripheral surface of the sealed container around the spot welded portion, due to the influence of welding, the sealed container S is deformed and deformed over the entire inner peripheral surface of the sealed container in the upper and lower cross-sections with the welding point W as the center. In the inside of the compression chamber, the cylinder 1, the rolling piston 2, and the vane 3 are selectively fitted so as to have a gap of about several μm to several tens of μm so that predetermined characteristics can be exhibited with respect to performance, reliability, and the like. However, if the influence of this distortion deformation propagates to the inside of the compression chamber, it will be adversely affected by performance degradation and reliability degradation. Therefore, the gap L is necessary to escape from the sealed container S deformed by welding, and it is sufficient to ensure 0.2 mm or more. Note that the additional mass portion 13 may be provided on either the upper end surface or the lower end surface of the cylinder 1.

  The electric element M includes a stator M1 and a rotor M2 as shown in FIG. A crankshaft 6 is connected to the rotor M2. An upper balance weight M2a and a lower balance weight M2b are provided above and below the rotor M2 in order to balance the rotation with the eccentric shaft portion 7 of the crankshaft 6.

  In the rotary hermetic compressor of the present embodiment having the above configuration, the refrigerant gas discharged from the compression element C is sent out from the discharge pipe 10 into the refrigeration circuit. In addition, the refrigerant gas flowing in from the refrigeration circuit is temporarily stored in the accumulator 11 and returned from the accumulator 11 to the cylinder 1 through the suction connecting pipe 12.

  In the present embodiment, as described above, the additional mass portion 13 composed of the integrally formed thick portion is provided on the outer peripheral edge portions of the upper and lower end surfaces of the cylinder 1, and therefore, between the mass member and the cylinder. Compared to the conventional one that suppresses the movement of the cylinder by using the frictional force, the inertia moment of the compressor body per mass to be added can be increased more effectively. For this reason, it is possible to reduce vibrations while minimizing an increase in mass without increasing the outer diameter of the sealed container S or the accumulator 11. And it becomes possible to expand a refrigerant | coolant discharge | emission capacity | capacitance, environmental load reduction (raw material usage-amount reduction) can be promoted effectively, compressor efficiency improves, and ensuring of reliability becomes easy. In particular, in a compressor using a R410A refrigerant or a high-pressure refrigerant such as carbon dioxide as the refrigerant, vibration tends to be larger. However, as described above, the additional mass portion is provided on the outer peripheral edge of the upper and lower end surfaces of the cylinder 1. By providing 13 integrally, vibration can be effectively reduced.

Embodiment 2. FIG.
FIG. 4 is a schematic diagram of an additional mass section that is a main part of the rotary hermetic compressor according to the second embodiment of the present invention. In the figure, the same functional parts as those of the first embodiment are the same. The code | symbol is attached | subjected. In the description, reference is made to FIG. 1 and FIG.

  In the rotary hermetic compressor of the present embodiment, the spot welding position of the compression element C to the hermetic container S of the cylinder 1 as shown in FIG. The other structures are the same as those of the first embodiment described above, and all the functions of the first embodiment are provided.

  In the rotary hermetic compressor of the present embodiment, the spot welding position of the cylinder 1 to the hermetic container S is shifted upward rather than the intermediate portion of the cylinder 1 in the axial direction. Propagation to the inside of the room can be suppressed.

Embodiment 3 FIG.
FIG. 5 is a schematic diagram of an additional mass unit that is a main part of the rotary hermetic compressor according to the third embodiment of the present invention. In the figure, the same functional parts as those of the first embodiment are the same. The code | symbol is attached | subjected. In this case as well, the description will be made with reference to FIGS. 1 and 2 described above.

  In the rotary hermetic compressor of the present embodiment, as shown in FIG. 5, the additional mass portion 13 of the compression element C is not the cylinder 1 portion, but the outer peripheral edge portions of the flanges 4a and 5a of the upper bearing 4 and the lower bearing 5. The other features are the same as those of the first embodiment described above, and all the functions of the first embodiment are provided.

  In the rotary hermetic compressor of the present embodiment, the additional mass portion 13 is integrally formed on the outer peripheral edge portions of the flanges 4a and 5a of the upper bearing 4 and the lower bearing 5, respectively. The vibration can be reduced without increasing the mass without minimizing the outer diameter of the insulator 11. In addition, the refrigerant discharge capacity can be increased. In particular, in a compressor using R410A refrigerant or high-pressure refrigerant such as carbon dioxide as the refrigerant, vibration can be reduced more effectively.

  The additional mass portion 13 may be provided on either the upper bearing 4 or the lower bearing 5.

Embodiment 4 FIG.
FIG. 6 is a schematic diagram of an additional mass unit that is a main part of the rotary hermetic compressor according to the fourth embodiment of the present invention. In the figure, the same functional parts as those of the first embodiment are the same. The code | symbol is attached | subjected. In this case as well, the description will be made with reference to FIGS. 1 and 2 described above.

  The rotary hermetic compressor of the present embodiment is characterized in that the additional mass portion 13 is fixed to the outer peripheral edge portions of the upper and lower end surfaces of the cylinder 1 so as to be separable by fastening bolts 14 as shown in FIG. The rest of the configuration is the same as that of the first embodiment described above, and all the functions of the first embodiment are provided.

  In the machining process of the cylinder 1, in the final finishing process, the upper and lower end surfaces of the cylinder 1 are usually sandwiched with a grindstone and polished. Therefore, if the additional mass part 13 can be separated as in the present embodiment, the cylinder 1 can be polished by a conventional method without obstructing the cylinder polishing process. Further, the additional mass portion 13 can be disposed only in the compressor model having the maximum refrigeration capacity, that is, the refrigerant discharge amount in which vibration is a problem, for example, and the specification change according to the compressor capacity is facilitated.

  Note that the additional mass portion 13 may be provided on either the upper end surface or the lower end surface of the cylinder 1.

Embodiment 5 FIG.
FIG. 7 is a longitudinal sectional view showing the overall configuration of a rotary hermetic compressor according to Embodiment 5 of the present invention.
FIG. 8 is a schematic diagram of an additional mass part, which is the main part, in which the same reference numerals are given to the same functional parts as those of the first embodiment.

  In the rotary hermetic compressor of the present embodiment, as shown in FIGS. 7 and 8, the additional mass portion 13 is not provided at the cylinder 1 portion but at the outer peripheral edge portions of the flanges 4a and 5a of the upper bearing 4 and the lower bearing 5. , Each having a feature that it is separably fixed by a fastening bolt 14, and the other configurations are all the same as those of the first embodiment, and have all the functions of the first embodiment. It is.

  In the rotary hermetic compressor of the present embodiment, the additional mass portion 13 is separably fixed to the outer peripheral edge portions of the flanges 4a and 5a of the upper bearing 4 and the lower bearing 5, respectively. Without disturbing, the cylinder 1 can be polished by a conventional method. Further, the additional mass portion 13 can be disposed only in the compressor model having the maximum refrigeration capacity, that is, the refrigerant discharge amount in which vibration is a problem, for example, and the specification change according to the compressor capacity is facilitated.

  The additional mass portion 13 may be provided on either the upper bearing 4 or the lower bearing 5.

  S closed container, M electric element, C compression element, 1 cylinder, 2 rolling piston, 3 vane, 4 upper bearing, 5 lower bearing, 13 additional mass part.

Claims (5)

An electric element having a stator and a rotor on top of the sealed container, a cylinder in its lower, bearing, rolling piston, vane Chi also compression element disposed to overlap in the axial direction, the compression element is the electric In a rotary hermetic compressor connected to and driven by the rotor of the element ,
A rotary hermetic compressor characterized in that an additional mass portion is integrally provided on the outer peripheral edge of the compression element over the entire circumference .   2. The rotary hermetic compressor according to claim 1, wherein the additional mass portion is formed at an outer peripheral edge portion of the cylinder with a gap with respect to an inner peripheral surface of the sealed container.   3. The rotary hermetic compressor according to claim 2, wherein a welding position of the outer peripheral surface of the cylinder to the sealed container is welded at a position higher than an intermediate position in the vertical direction of the cylinder. .   2. The rotary hermetic compressor according to claim 1, wherein the additional mass portion is detachably fixed to an outer peripheral edge portion of the compression element.   The rotary hermetic compressor according to any one of claims 1 to 4, wherein a high-pressure refrigerant such as R410A refrigerant or carbon dioxide is used as the refrigerant.

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