KR20110015851A - Compressor - Google Patents

Abstract

PURPOSE: A compressor is provided to reduce the rubbing between vanes and components contacted with the vanes since oil is supplied to a vane fixture. CONSTITUTION: A compressor comprises a sealed container, a stator(120), a fixing member, a rotating member, and an oil supply hole(137h). The oil is stored in the sealed container. The stator is fixed within the sealed container. A fixed axis(141) of the fixing member is installed in the sealed container and is extended inside the sealed container. The rotating member is located inside the stator and rotates around the fixed shaft by mutual electromagnetic force. The rotating member comprises a vane and a vane fixture. The oil supply hole connects a part of the vane fixture to the internal space of the sealed container and supplies the oil of the internal space to the vane fixture.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor for compressing a refrigerant while rotating while being supported on a bearing while the rotating member is suspended by a fixed member. In particular, the present invention not only provides structural stabilization but also improves assembly performance and improves lubrication performance of the vane. The present invention relates to a compressor that can.

Generally, a compressor is a mechanical device that increases power by receiving air from a power generator such as an electric motor or a turbine and compressing air, a refrigerant, or various other working gases, and a home appliance such as a refrigerator and an air conditioner. Or widely used throughout the industry.

These compressors can be classified into reciprocating compressors for compressing refrigerant while linearly reciprocating inside the cylinders by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder. ), A rotary compressor for compressing the working gas in a compression space formed between an eccentrically rotating roller and a cylinder, and between an orbiting scroll and a fixed scroll. It is divided into a scroll compressor (Scroll compressor) for compressing the refrigerant while the rotating scroll is rotated along the fixed scroll to form a compression space in which the working gas is absorbed and discharged.

Reciprocating compressors have good mechanical efficiency, while these reciprocating motions cause serious vibration and noise problems. Because of these problems, rotary compressors have been developed because of their compactness and excellent vibration characteristics.

The rotary compressor is configured such that the motor portion and the compression mechanism portion are mounted on the drive shaft in a sealed container. A roller located around the eccentric portion of the drive shaft is positioned in a cylinder forming a cylindrical compression space, and at least one vane It extends between the compression spaces and partitions the compression space into the suction zone and the compression zone, and the roller is located eccentrically in the compression space. In general, the vane is supported by a spring in the groove portion of the cylinder to pressurize the surface of the roller, and by this vane, the compression space is divided into a suction zone and a compression zone as described above. As the suction shaft gradually grows as the drive shaft rotates, the suction zone or the working fluid is sucked into the suction zone, and the compression zone gradually decreases, thereby compressing the refrigerant or the working fluid therein.

In the conventional rotary compressor, since the motor part and the compression mechanism part are stacked up and down, the height of the compressor is inevitably increased as a whole. In addition, in the conventional rotary compressor, since the weight of the motor portion and the compression mechanism portion are different from each other, not only a difference in inertia force is generated but also an unbalance inevitably occurs on the upper and lower sides of the driving shaft. Therefore, in order to compensate for the imbalance of the motor portion and the compression mechanism portion, the weight member can be added to the relatively small weight, but this causes a result of applying an additional load to the rotating body, which causes a problem of lowering driving efficiency and compression efficiency. . In addition, in the conventional rotary compressor, since the eccentric portion is formed in the drive shaft at the compression mechanism, as the drive shaft rotates, the eccentric portion is rotated together to drive the roller outside the eccentric portion. As a result, the eccentric rotation of the drive shaft and the eccentric portion in the compression mechanism is performed. There is a problem that the vibration inevitably occurs. In addition, in the conventional rotary compressor, the eccentric portion of the drive shaft rotates to continuously slide contact with the inner surface of the stationary cylinder on which the roller is fixed, and also continuously slides with the end surface of the vane on which the roller is fixed. Because of the contact, friction losses occur due to the presence of high relative speeds between these slidingly contacting components, which leads to a decrease in the efficiency of the compressor, and furthermore the possibility of refrigerant leakage at the contact surface between the sliding contacting vanes and rollers. The mechanical reliability is also lowered.

Conventional rotary compressors have a configuration in which a drive shaft rotates inside a fixed cylinder, whereas in Japanese Patent Laid-Open Nos. 62-284985 and 64-100291, a shaft having a suction port in the axial direction and larger than the shaft is provided. A fixed shaft integrally formed with a piston part eccentric in diameter and having a port communicating with the suction port of the shaft in a radial direction; Vanes installed in a rotatable manner; A rotor rotatable with the vane received; An upper bearing having a discharge port; Lower bearing; A permanent magnet having a height larger than the difference between the outer diameter and the inner diameter and fixed to the lower bearing; Coils that do not rotate on the outer periphery of the permanent magnet; including, but by rotating the upper bearing and the rotor and the lower bearing in order to rotate, the vane surrounds the space between the rotor, the upper bearing and the lower bearing and the piston portion volume This changing rotary compressor is disclosed.

In the rotary compressor disclosed in the Japanese Laid-Open Patent Publication, since the permanent magnet in the shape of a hollow cylinder is located inside the stator, and the rotor and the compression mechanism part including the vane are located inside the permanent magnet, the motor part and the compression mechanism part of the conventional rotary compressor are high. It is considered that the problem caused by the installation in the direction can be solved.

However, the rotary compressor disclosed in the Japanese Laid-Open Patent Publication is conventionally provided between the vane and the eccentric portion (piston portion) because the vane is in sliding contact with the outer surface of the eccentric portion (piston portion) which is fixed and supported at the same time by the rotating rotor. As with the rotary compressor, there is a problem that a high relative speed difference exists, not only causes friction loss but also a possibility of refrigerant leakage at the contact surface between the sliding contact vane and the eccentric part. In addition, the rotary compressor disclosed in the Japanese Patent Laid-Open Publications is practically applicable because it does not disclose any possible configuration for the suction and discharge flow paths of the working fluid, the lubricating oil in the compression mechanism part, and the mounting of the bearing member. There is not enough.

Alternatively, US Patent Publication No. 7,217,110 discloses a rotary compressor in which a fixed shaft and an eccentric part are integrally formed, and a compression space is formed between the outer surface of the roller rotatably positioned in the eccentric and the inner surface of the rotating rotor. . Here, the rotational force of the rotor has a configuration that is transmitted to the roller through the vane fixed to the upper and lower plates of the rotor that rotates integrally with the rotor, by using the pressure difference in the sealed container and the pressure difference in the compression space, the center of the fixed shaft The working fluid and the lubricating oil are introduced into the compression space through the formed longitudinal flow path.

Therefore, since the rotary compressor disclosed in the US Patent Publication also forms a compression mechanism inside the rotor, it is considered that the problems caused by the motor portion and the compression mechanism portion installed in the height direction in the conventional rotary compressor can be solved. In addition, unlike the above-described Japanese Patent Laid-Open Publications, since the rotor, vanes and rollers all rotate integrally, there is no difference in relative speed between them, and there is no fear of friction loss due to them.

However, the rotary compressor disclosed in the U.S. Patent Publication discloses that one end of the fixed shaft is fixed to the hermetically sealed container, but the other end of the fixed shaft is manufactured to be suspended in the sealed container in a state in which the other end of the fixed shaft is separated from the hermetically sealed container. It is difficult to center, very vulnerable to lateral vibrations due to the inevitable eccentric rotation due to the nature of the rotary compressor, the actual production is quite difficult, or assembly productivity is poor. In addition, since the vanes protrude inwardly from the rotor and the vane grooves are formed in the rollers to guide the movement trajectory of the vanes, the rollers inevitably become large in order to form the vane grooves. There is a problem that results in the excitation of the lateral vibration by the eccentric rotation. Also disclosed is a configuration that does not use lubricating oil, but for this purpose, there is a problem in that components must be made of a very expensive material. In the case of using a lubricating oil, the lubricating oil is used by using a pressure difference in a sealed container and a compression space. Since it is configured to circulate with the working fluid by pulling up into the compression space, in this case, inevitably a large amount of lubricating oil is incorporated into the working fluid, and there is a problem in that the lubrication performance can be lowered because the compressor can exit the compressor together with the working fluid.

The present invention has been made to solve the above problems of the prior art, an object of the present invention is to provide a compressor that can be easily assembled to center the parts in the sealed container to increase the structural safety.

In addition, an object of the present invention is to provide a compressor that not only reduces the lateral vibration due to eccentric rotation but also is easy to assemble in actual production.

In addition, an object of the present invention is to provide a compressor that can easily lubricate the vanes by allowing the oil stored in the sealed container to be easily introduced into the vane mounting holes equipped with vanes.

Compressor according to the present invention for solving the above problems is a sealed container in which the refrigerant is sucked and discharged, the oil is stored; A stator fixed in a sealed container; A fixing member installed at an upper end of the fixed shaft so as not to move in the sealed container and extending in the sealed container at the same time; Located inside the stator, it can suck and compress the refrigerant into the compression space formed therein while rotating around the fixed axis by mutual electromagnetic force with the stator, and the compression space is compressed and discharged into the suction pocket and the refrigerant suction A rotating member including a vane reciprocating so as to be partitioned into a compression pocket, and a vane mounting hole accommodating the vanes; It characterized in that it comprises a; oil supply hole for communicating a portion of the vane mounting port to the inner space of the sealed container to supply the oil of the inner space to the vane mounting port.

In addition, in the present invention, the rotating member, the rotor is installed between the stator and the holding member to rotate about the holding member by mutual electromagnetic force with the stator, and is laminated on the rotor to rotate with the rotor and the compression space is provided therein A vane elastically supported by the cylinder so as to partition the cylinder, the compression space between the eccentric portion and the cylinder into a suction pocket into which the refrigerant is sucked, and a compression pocket through which the refrigerant is compressed and discharged, to rotate together with the cylinder, and to make sliding contact with the outer surface of the eccentric part; A vane mounting hole formed in a slot shape on the inner circumferential surface of the cylinder, a vane spring stopper for blocking the vane mounting hole for installing the vane spring to elastically support the vane, and an upper and lower portion of the compression space to be fixed together with the rotating member. And an upper and lower bearing cover that rotates about the member.

In addition, in the present invention, the oil supply hole is formed in the vane spring stopper at a position lower than the oil level of the oil stored in the sealed container so as to communicate with the vane mounting hole, so that the oil can be supplied to the vane mounting hole.

Further, in the present invention, the vane mounting hole extends to the vane evacuation protrusion formed by protruding from the cylinder outer circumferential surface, and the open space of the vane evacuation protrusion which is not closed by at least one of the upper and lower bearing covers functions as an oil supply hole to the vane mounting hole. Characterized in that.

Further, in the present invention, the lower open space of the vane evacuation protrusion, which is not closed by the lower bearing cover, is an oil supply hole communicating with the oil stored in the sealed container.

In addition, in the present invention, the upper open space of the vane evacuation protrusion, which is not closed by the upper bearing cover, is an oil supply hole communicating with oil collected on the upper bearing cover.

In addition, in the present invention, the rotating member is a cylindrical rotor which is rotatably supported by the fixed member so as to rotate about a fixed shaft by a rotating electromagnetic field from the stator, and receives the rotational force of the cylindrical rotor and the eccentric with the cylindrical rotor. A vane that rotates around the roller to form a compression space between the cylindrical rotor and the rotating force from the cylindrical rotor to the roller, and divides the compression space into a suction pocket where the refrigerant is sucked in and a compression pocket where the refrigerant is compressed and discharged. , A vane mounting hole formed integrally with the roller so as to protrude toward the cylindrical rotor from the outer circumferential surface of the roller and at the same time, the upper and lower parts which rotate about the fixing member together with the rotating member by forming upper and lower portions of the compression space. It is characterized by consisting of a bearing cover.

In addition, in the present invention, the open space of the vane mounting holes that are not closed by at least one of the upper and lower bearing cover functions as an oil supply hole to the vane mounting holes.

In addition, in the present invention, the lower open space of the vane mounting hole not closed by the lower bearing cover is characterized in that the oil supply hole in communication with the oil stored in the sealed container.

In addition, in the present invention, the upper open space of the vane mounting hole not closed by the upper bearing cover is characterized in that the oil supply hole in communication with the oil collected on the upper bearing cover.

In addition, in the present invention, the fixing member is provided with a first fixing member including an eccentric portion formed so as to be eccentric to the fixed shaft and the fixed shaft is installed on its upper end and is elongated into the sealed container so as not to move in the sealed container, the first fixing member It is formed so as to be spaced apart from the bottom of the sealed container is divided into a second fixing member that is installed so as not to move, the rotating member is rotated about the first fixing member, rotatable while applying a load to the second fixing member It is characterized in that it is supported.

In addition, in the present invention, the rotating member further includes a cylinder having a compression space therein, and an upper and lower bearing cover which forms an upper and lower portion of the compression space and rotates about a fixed shaft together with the rotating member. The cover includes an upper shaft portion surrounding the fixed shaft, and an upper cover portion coupled to the cylinder to form an upper portion of the compression space. An inner surface of the upper shaft portion is rotatably journal-supported on an outer surface of the fixed shaft, and a bottom surface of the upper cover portion is an upper surface of the eccentric portion. The thrust is rotatably supported.

In addition, in the present invention, the rotating member further includes a cylinder having a compression space therein, and upper and lower bearing covers forming upper and lower portions between the compression holes and rotating about a fixed shaft together with the rotating member, and the lower bearing The cover includes a lower shaft portion surrounding the fixed shaft, and a lower cover portion coupled to the cylinder to form a lower portion of the compression space. An inner surface of the lower shaft portion is rotatably journal-supported on an outer surface of the fixed shaft, and an upper surface of the lower cover portion is a bottom surface of the eccentric portion. The thrust is rotatably supported.

In addition, in the present invention, the rotating member further includes a cylinder having a compression space therein, and an upper and lower bearing cover which forms upper and lower portions of the compression space and rotates about a fixed shaft together with the rotating member, and the lower bearing The lower shaft portion formed to surround the fixed shaft is formed to extend from the lower end of the fixed shaft, and an end portion of the lower shaft portion is rotatably supported while applying a load of the rotating member to the second fixing member.

Further, in the present invention, the second fixing member further includes a cylindrical bearing portion having a step therein, the lower end of the lower shaft portion is thrust supported by the step of the second fixing member, and the outer surface of the lower shaft portion is journal-supported on the inner surface of the cylindrical bearing portion. It is characterized by.

The compressor according to the present invention configured as described above is assembled to suspend the rotating member to the fixing member, and then the fixing member is fixed to the upper bearing and the rotating member is rotatably supported on the lower bearing, and the upper and lower bearings are sealed. Since the parts are fixed to the container, the parts can be easily assembled and centered in the sealed container, thereby increasing structural safety and assemblability.

In addition, the compressor according to the present invention, even if the eccentric portion is eccentric from the axial center of the fixed shaft is projected in all the radial directions of the fixed shaft to maintain a stationary state, eccentric rotation because the rotating member rotates around the fixed shaft or eccentric portion around the Is not generated, and as a result, not only the lateral vibration due to the eccentric rotation can be reduced, but also the balance weight employed to reduce the vibration due to the eccentric rotation can be omitted, so that the efficiency can be increased, and the actual production assembly is easy. have.

In addition, the compressor according to the present invention, even if the vane is elastically supported by the vane spring, or even if the vanes are installed to abut between the bushes, the oil supply hole for communicating the vane mounting hole with the vane and the inner space of the sealed container in which the oil is stored. Since the oil level is maintained higher than the oil supply hole, the oil can be easily introduced into the vane mounting hole to increase the lubrication performance of the vane, and reduce the friction and wear of the vane and its parts, as well as the movement of the vane. This can be done smoothly to increase operational reliability.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 to 3 are side cross-sectional perspective and exploded perspective and side cross-sectional views showing a first embodiment of the compressor according to the present invention.

The first embodiment of the compressor according to the present invention is a sealed container 110, a stator 120 fixed in the sealed container 110, and a rotating electromagnetic field from the stator 120 as shown in FIGS. The rotating member 130 is rotatably installed inside the stator 120 to compress the refrigerant, and the rotating member 130 is installed to hang on the outer circumferential surface thereof, and the upper and lower ends of the fixed shaft 141 are sealed in the container 110. Fixed member 140 fixed to not move in the upper portion, the upper bearing 150 for fixing the upper end of the fixed shaft 141 inside the sealed container 110, and the lower end of the fixed shaft 141 and at the same time rotating member 130 includes a lower bearing 160 fixed inside the sealed container 110 so as to be rotatably supported on the upper surface. At this time, the electric mechanism for providing power through the electrical action comprises a rotor 131 of the rotating member 130, including the stator 120, the compressor mechanism for compressing the refrigerant through the mechanical action rotating member 130 It includes a fixing member 140, including. Therefore, by partially stacking the electric mechanism part and the compression mechanism part in the vertical direction and providing the radial direction, the overall compressor height can be lowered.

The airtight container 110 has a cylindrical body part 111, upper and lower shells 112 and 113 coupled to the upper and lower parts of the body part 111, and a lower shell to fasten and fix the airtight container 110 to another product. 113 is made of a mounting portion 114 provided in the radial direction on the bottom surface, the oil lubricating the rotating member 130 and the fixing member 140 may be stored up to an appropriate height therein. An example of a suction tube (not shown) in which the refrigerant is sucked is provided at the center of the upper shell 112 so that the fixed shaft 141 is directly exposed, and a discharge tube capable of discharging the refrigerant at a predetermined position of the upper shell 112 ( 115) is provided, and the inside of the sealed container 110 is determined to be high-pressure or low-pressure depending on whether the inside of the sealed container 110 is filled with a compressed refrigerant or a refrigerant before being compressed, and the suction tube and the discharge tube may be changed accordingly. In the embodiment of the present invention is configured as a high-pressure type, the fixed shaft 141 which is a suction pipe is provided to protrude to the outside of the sealed container (110). However, the fixed shaft 141 does not need to protrude excessively outside the sealed container 110, it is preferable to install a suitable fixed structure outside the sealed container 110 to connect to the external refrigerant pipe. In addition, the upper shell 112 is provided with a terminal 116 for supplying power to the stator 120.

The stator 120 is composed of a core and a coil wound around the core, and fixed to the inside of the body portion 111 of the sealed container 110 by shrinkage. The core employed in the existing BLDC motor has nine slots along the circumference, whereas in the preferred embodiment of the present invention, the diameter of the stator 120 is relatively large so that the core of the BLDC motor has twelve slots along the circumference. It is composed. As the number of slots of the core increases, the number of turns of the coil increases, so that the height of the core may be lowered in order to generate the electromagnetic force of the stator 120 as in the prior art.

The rotating member 130 includes a rotor 131, a cylinder 132, a vane 133, a vane spring 134, an upper bearing cover 135, and a lower bearing cover 138. The rotor 131 is provided with a plurality of permanent magnets in the axial direction so as to rotate by the rotating electromagnetic field from the stator 120, and is installed to maintain a gap inside the stator 120. The cylinder 132 is formed in a cylindrical shape provided with a compression space therein, the inner circumferential surface is provided with a vane mounting hole (132H) formed long in the radial direction so that the vanes 133 and the vane spring 134 can be mounted. The rotor 131 and the cylinder 132 are coupled such that the rotor 131 and the cylinder 132 are stacked up and down on the basis of the upper bearing cover 135 so as to rotate integrally. The vane 133 is one end is supported on the outer peripheral surface of the eccentric portion 142 to be described below, while the other end is installed to be elastically supported by the vane spring 134 in the vane mounting hole 132H of the cylinder 132, the cylinder The compressed space between the 132 and the eccentric portion 142 is divided into a suction pocket (S: shown in FIG. 4) into which the refrigerant is sucked and a compression pocket (D: shown in FIG. 4) into which the refrigerant is compressed and discharged. Of course, it is preferable that the lubrication structure is applied to the vanes 133 to move smoothly in the eccentric portion 142 and the vane mounting holes 132H of the cylinder 132.

The upper bearing cover 135 is installed in contact with the fixing member 140 in contact with the journal bearing or the thrust bearing, and is coupled to the rotor 131 and the cylinder 132 so as to be stacked in the vertical direction. At this time, the outer peripheral portion of the upper surface of the upper bearing cover 135 is formed to be stepped so that the rotor 131 can be fastened, while the rotor 131 is mounted on the stepped portion on the outer peripheral surface of the upper bearing cover 135. The bolt is fastened, and the cylinder 132 is bolted to the center of the bottom surface of the upper bearing cover 135. In addition, the upper bearing cover 135 is provided with a discharge port (not shown) through which the refrigerant compressed in the compression space can be discharged, and a discharge valve 135A installed therein. The discharge hole of the upper bearing cover 135 is provided to reduce the dead volume. It is preferably located adjacent to the vane 133. The upper bearing cover 135 is coupled to the bottom of the rotor 131 and the upper surface of the cylinder 132, the lower bearing cover 135 is coupled to the bottom of the cylinder 131, a fastening member such as a kind of long bolt Each is fastened by

The fixed member 140 has a fixed shaft 141 provided in a cylindrical shape and a fixed shaft in all radial directions of the fixed shaft 141 to have a cylindrical shape having a larger diameter than the cylinder of the fixed shaft 141. Protruding from the 141 and at the same time eccentric portion 142 formed eccentrically on the fixed shaft (141). A lower portion of the fixed shaft 141 is formed with a first oil supply passage 141A through which oil stored in the sealed container 110 can be supplied, while a lower pressure refrigerant can be sucked into the upper portion of the fixed shaft 141. Since the vertical suction passage 141B is formed and the first oil supply passage 141A and the vertical suction passage 141B are formed to be isolated, the oil may be prevented from escaping together with the refrigerant. The eccentric portion 142 is formed to extend in all radial directions of the fixed shaft 141, and extends to the outer circumferential surface in the radial direction of the eccentric portion 142 so as to communicate with the vertical suction passage 141B of the fixed shaft 141. The horizontal suction passage 142B is provided, and the vane 133 may pass along the horizontal suction passage 142B. In this case, since the upper and lower surfaces of the eccentric portion 142 abut the upper and lower bearing covers 135 and 136 and act as a trust surface, it is preferable that a supply passage for lubricating oil is formed on the upper and lower surfaces of the eccentric portion 142. Since the outer circumferential surface of the eccentric portion 142 is installed to be in contact with the vane 133, it is preferable that a supply passage of lubricating oil for lubricating between the vane 133 and the eccentric portion 142 is formed.

The upper and lower bearings 150 and 160 fix the fixed shaft 141 to the airtight container 110 so as not to move and at the same time rotatably support the rotating member 130. The upper bearing 150 is fixed to the upper shell 112 of the sealed container 110 by welding, the upper portion of the fixed shaft 141 is fitted. At this time, the upper bearing 150 is formed smaller in the radial direction than the lower bearing 160, in order to prevent interference with the suction pipe 115 or the terminal 116 provided in the upper shell (112). On the other hand, the lower bearing 160 is spaced apart from the lower portion of the fixed shaft 141, the shaft portion of the lower bearing cover 136 surrounding the lower portion of the fixed shaft 141 is rotatably supported by the thrust bearing 161 , Is fixed to the body portion 111 side of the sealed container 110 by shrinkage or three-point welding. The upper and lower bearings 150 and 160 are manufactured by press working, but the vanes 133, the upper and lower bearing covers 135 and 136, the fixed shaft 141 and the eccentric portion 142 are all cast from cast iron, It is manufactured by grinding and further machining.

On the other hand, looking at the structure in which the rotating member 130 is rotatably assembled to the fixing member 140, the upper and lower bearing covers 135, 136 are rotatably installed on the fixing member 130 and the lower bearing 160. More specifically, the upper bearing cover 135 is composed of an upper shaft portion 135a surrounding an upper portion of the fixed shaft 141, and upper cover portions 135b and 135c contacting the upper surface of the eccentric portion 142, and the upper cover portion ( 135b and 135c have a relatively thick thickness to withstand the pressure of the compression space, and a relatively thin thickness so that the cylinder mounting portion 135b is bolted to the bottom surface of the cylinder 132 and the outer peripheral surface of the cylinder mounting portion 135b is stepped. At the same time, the rotor mounting portion 135c is bolted in the state where the rotor 131 is seated on the upper surface. At this time, the inner circumferential surface of the upper shaft portion (135a) is provided with a journal bearing for journal supporting the upper outer circumferential surface of the fixed shaft (142), the eccentric portion (142) on the bottom surface of the upper cover portion (135b, 135c) or the cylinder coupling portion (135b) The thrust bearing which thrust-supports the upper surface is provided. In addition, the lower bearing cover 136 includes a lower shaft portion 136a surrounding the lower portion of the fixed shaft 141 and a lower cover portion 136b in contact with the bottom surface of the eccentric portion 142. At this time, the inner circumferential surface of the lower shaft portion 136a is provided with a journal bearing for journal-supporting the lower outer circumferential surface of the fixed shaft 142, and a thrust bearing for thrust supporting the bottom of the eccentric portion 142 is provided on the upper surface of the lower cover portion 136b. do. In addition, the lower bearing 160 has a stepped cylindrical bearing portion 160a surrounding the lower shaft portion 136b, and a mounting portion 160b extended in the radial direction of the bearing portion 160a to be welded and fixed inside the sealed container 110. ) At this time, the inner circumferential surface of the bearing portion 160a is provided with a journal bearing for journal-supporting the outer circumferential surface of the lower shaft portion 136a, and a thrust bearing for supporting the lower end of the lower axial portion 136a on the stepped bottom surface of the bearing portion 160a. It may be provided, or a separate plate-shaped thrust bearing 161 may be inserted therebetween.

Therefore, when the upper and lower bearing covers 135 and 136 are coupled to the rotor 131 and the cylinder 132 and the fixing member 140 in the axial direction, the bottom surface of the cylinder engaging portion 135b of the upper bearing cover 135 becomes a cylinder. 132 is bolted to abut the upper surface and the upper surface of the rotor coupling portion 135c of the upper bearing cover 135 is bolted to abut the bottom surface of the rotor 132, the cover portion of the lower bearing cover 136 ( 136b) is bolted to abut the bottom surface of the cylinder 132. At this time, the upper shaft portion 135a is supported by the journal bearing on the upper portion of the fixed shaft 141 and the upper cover portions 135b and 135c are supported by the upper surface of the eccentric portion 142 so that the upper bearing cover 135 is fixed to the fixing member ( 140 is rotatably installed, and the lower shaft portion 136a is supported by the journal bearing under the fixed shaft 141, while the lower cover portion 136b is thrust supported on the bottom of the eccentric portion 142. 136 is rotatably installed relative to the fixing member 140. In addition, the lower shaft portion 136a of the lower bearing cover 136 is fitted to the bearing portion 160a of the lower bearing 160, and the lower bearing cover 136 is supported by the bearings in the journal surface or the thrust surface which abut each other. It is rotatably supported with respect to the lower bearing 160.

Figure 4 is a plan view showing the vane mounting structure in the first embodiment of the compressor according to the present invention.

Looking at the mounting structure of the vane 133 with reference to Figure 4, the vane evacuation protrusion (132A) protruding on one side of the outer peripheral surface of the cylinder 132 is provided, the vane evacuation protrusion (132A) on the inner / outer peripheral surface of the cylinder 132 A vane mounting hole 132H penetrated in the radial direction and axially penetrated therein is provided, and a vane spring supporter is provided on the outer circumferential surface of the cylinder 132 to block the vane mounting hole 132H and to support the vane spring 134. 137: shown in FIG. 3). Therefore, one end of the vane 133 is elastically supported by the vane spring 134 in the vane mounting hole 132H, while the other end of the vane 133 is supported on the outer circumferential surface of the eccentric portion 142.

The vane 133 mounted as described above divides the compression space provided between the cylinder 132 and the eccentric portion 142 into a suction pocket S and a compression pocket D. The horizontal suction flow path 142B of the eccentric portion 142 described above is positioned to communicate with the suction pocket S, and the discharge port and discharge valve 135A of the upper bearing cover 135 are positioned to communicate with the compression pocket D. However, as described above, in order to reduce the dead volume, the vanes 133 are preferably located close to each other.

Therefore, when the rotor 131 rotates by the rotor field with the stator 120 (shown in FIG. 1), the cylinder 132 connected by the rotor 131 and the upper bearing cover 135 also rotates integrally. The vanes 133 are elastically supported by the vane mounting holes 132H of the cylinder 132 and are supported on the outer circumferential surface of the eccentric portion 142. The cylinder 132 rotates about the fixed shaft 141, and the vanes ( 133 rotates along the outer circumferential surface of the eccentric portion 142 with respect to the eccentric portion 142. That is, the inner circumferential surface of the cylinder 132 has portions corresponding to each other on the outer circumferential surface of the eccentric portion 142. The portions corresponding to each other are inhaled while repeating the process of contacting each time the cylinder 132 rotates once and away from each other. As the pocket S gradually increases, the refrigerant or working fluid is sucked into the suction pocket S, and the compression pocket D gradually decreases while the refrigerant or working fluid therein is compressed, and then discharged.

5 is a plan view showing an operating cycle of the compression mechanism in the first embodiment of the compressor according to the present invention.

Looking at the process of suction, compression, and discharge of the compression mechanism, as shown in Figure 5, while the cylinder 132 and the vane 133 rotates relative to (a), (b), (c), (d) Shows one cycle. In more detail, when the cylinder 132 and the vane 133 are located at (a), the refrigerant or the working fluid is sucked into the suction pocket S, and the discharge is divided into the suction pocket S and the vane 133. Compression occurs in the compression pocket (D). Even when the cylinder 132 and the vane 133 arrive at (b) while rotating, the suction pocket S increases and the compression pocket D decreases, so that the refrigerant or the working fluid is sucked into the suction pocket S, Compression continues in the compression pocket (D). When the cylinder 132 and the vane 133 arrive at (c) while rotating, the suction is continuously sucked into the suction pocket S, and the refrigerant is cooled when the pressure of the refrigerant or the working fluid becomes higher than the set pressure in the compression pocket D. B The working fluid is discharged through the discharge port of the upper bearing cover 135 (shown in FIG. 2) and the discharge valve 135A (shown in FIG. 2). In (d), suction and discharge of the refrigerant or working fluid are almost finished. Of course, when the position is changed from (d) to (a), the vanes 133 pass through the horizontal suction passage 142B provided in the eccentric portion 142.

6 is a perspective view showing an example of the vane lubrication structure in the first embodiment of the compressor according to the present invention.

Looking at the vane lubrication structure in the first embodiment of the compressor according to the present invention with reference to Figures 4 and 6, the vane evacuation protrusion 132A protruding on the outer peripheral surface of the cylinder 132 to secure the installation space of the vane 133 Is provided, and the vane mounting hole 132H penetrated from the inner circumferential surface of the cylinder 132 to the outer circumferential surface of the vane evacuation protrusion 132A is provided, and the vane 133 is attached to the vane mounting hole 132H with the vane spring 134. The vane spring stopper 137 is provided to prevent the vane mounting holes 132H extending to the outer circumferential surface of the vane evacuation protrusion 132A to elastically support the vane spring stopper 137. An oil supply hole 137h communicating with an internal space of the (e) is provided. At this time, the oil level of the oil is stored in the airtight container 110 (shown in FIG. 1) through the oil supply hole 137h of the vane spring stopper 137. It is preferable to maintain higher than the oil supply hole (137h). Of course, even when the compressor is operated at high speed, the oil level of the oil should be kept at least higher than the lowest end of the oil supply hole 137h of the vane spring stopper 137. However, when oil is introduced into the vane mounting hole 132H through the oil supply hole 137h of the vane spring stopper 137, it is difficult to maintain the oil level of the oil above a certain height because it is mixed with the compressed refrigerant and escapes to the outside. . Therefore, it is preferable that an oil recovery structure is applied in order to maintain an appropriate amount of oil or more in the sealed container 110 (shown in FIG. 1).

Looking at the oil recovery structure of the above embodiment, when the compressed refrigerant exiting the discharge port and the discharge valve 135A of the upper bearing cover 135 hits the oil separation plate 180 (shown in FIG. 1) installed directly on the rotor 131. The oil is separated from the compressed refrigerant. As such, the refrigerant from which the oil is separated passes through the hole 180h (shown in FIG. 3) provided in the oil separation plate 180 (shown in FIG. 1), and the oil separated from the refrigerant is separated from the oil separation plate 180 (see FIG. 1). 1 above the rotor 131 or the upper bearing cover 135, and then to the lower portion of the sealed container 110 (shown in FIG. 1) along the oil return passage between the parts. In this case, the oil return flow passage may be composed of a gap between the stator 120 (shown in FIG. 1) and the rotor 131, or a jig may be mounted to bolt the cylinder 132 to the upper and lower bearing covers 135 and 136. It may be composed of a series of jig mounting holes (not shown) provided in the cylinder 131 and the upper and lower bearing covers 135 and 136 so as to communicate vertically.

In addition, as another example of the vane lubrication structure, the lower bearing cover 136 is installed so as not to cover a part of the bottom surface of the vane mounting hole 132H of the cylinder 132, and the oil inside the sealed container 110 (shown in FIG. 1). It is preferable that not only the oil level of the lower bearing cover 136 is maintained but also the lowest end of the vane mounting hole 132H is locked. At this time, since the vane mounting holes 132H are provided in the vane evacuation protrusion 132A protruding from the circular cylinder 132, even if the lower cover portion 136b of the lower bearing cover 136 is formed in a disc shape, the vane evacuation protrusion is formed. It can be installed so as not to cover a part of the vane mounting holes (132H) extending up to (132A). In addition, even if the lower cover portion 136b of the lower bearing cover 136 is formed in a disc shape, its outer peripheral portion is formed stepped so as not to cover a part of the vane mounting hole 132H extending to the vane evacuation protrusion 132A. Can be installed.

In addition, referring to another example of the vane lubrication structure, the upper bearing cover 135 is installed so as not to cover a part of the upper surface of the vane mounting hole 132H of the cylinder 132, and the inside of the sealed container 110 (shown in FIG. 1). The oil level is preferably maintained higher than the upper bearing cover 135 as well as the top of the vane fitting 132H is locked.

7 to 9 are side cross-sectional perspective and exploded perspective and side cross-sectional views showing a second embodiment of the compressor according to the present invention.

As shown in FIGS. 7 to 9, the second embodiment of the compressor according to the present invention includes a sealed container 210, a stator 220 fixed in the sealed container 210, and a stator ( The rotating member 230 is rotatably installed inside the stator 220 by the rotating electromagnetic field from the 220 and compresses the refrigerant, and the rotating member 230 is installed to hang on the outer circumferential surface, and at the same time, the upper and lower ends of the fixed shaft 241. A fixed member 240 fixed to the closed container 210 so as not to move, an upper bearing 250 for fixing an upper end of the fixed shaft 241 to the closed container 210 inside, and a lower end of the fixed shaft 241. And a lower bearing 260 fixed to the inside of the hermetic container 210 so as to be spaced apart from and at the same time rotatably supported on the upper surface of the rotating member 230. At this time, the electric mechanism for providing power through the electrical action includes a rotor 231 of the rotating member 230, including the stator 220, the compressor mechanism for compressing the refrigerant through the mechanical action rotating member 230 It includes a fixing member 240, including. Therefore, by installing the transmission mechanism and the compression mechanism in the radial direction, the overall compressor height can be lowered.

The airtight container 210 is formed of a body portion 211 and upper and lower shells 212 and 213 in the same manner as the airtight container 210 of the first embodiment, but the high pressure that the inside of the airtight container 210 is filled with a high pressure refrigerant It consists of That is, the fixed shaft 241 is directly exposed to the center of the upper shell 212 as an example of the suction tube in which the refrigerant is sucked, and the discharge tube 214 for discharging the high-pressure refrigerant at one side of the upper shell 212 is provided. A terminal 215 is also provided to supply power to the stator 220. At this time, the fixed shaft 241 does not need to protrude excessively to the outside of the sealed container 210, it is preferable to install a suitable fixed structure to the outside of the sealed container 210 to connect to the external refrigerant pipe.

Since the stator 220 is configured in the same manner as in the first embodiment, detailed description thereof will be omitted.

The rotary member 230 includes a cylindrical rotor 231 and 232, a roller 233, a vane 234, a bush 235, an upper bearing cover 236 and a muffler 237, and a lower bearing cover 238. ) The cylindrical rotors 231 and 232 are rotated integrally with the rotor 231 by being located inside the rotor 231 with a plurality of permanent magnets in the axial direction so as to rotate by the rotating electromagnetic field from the stator 220. While it is made of a cylinder 232 having a compression space therein, the rotor 231 and the cylinder 232 may be separately configured and molded, but integrally in the form of a powder sintered body or a laminate in which iron pieces are laminated. It may be configured. The roller 233 is cylindrically mounted on the outer circumferential surface of the eccentric portion 242 of the fixing member 240 to be described below, and for this purpose, a lubrication structure is applied between the roller 233 and the eccentric portion 242. It is preferable. At this time, between the roller 233 and the eccentric portion 242 is provided with suction guide flow paths 233A and 242C through which the refrigerant can be sucked, and the roller 233 has a suction port communicating with the suction guide flow paths 233A and 242C ( 233a). The vane 234 is integrally provided on the outer circumferential surface of the roller 233 so as to be located at one side of the suction port 233a of the roller 233, and is provided on the inner rotor surface of the cylindrical rotors 231 and 232 or the cylinder 232. It is installed to fit in the vane mounting holes 232H. The bush 235 is installed to support both end surfaces of the vanes 234 fitted into the vane mounting holes 232H of the cylindrical rotors 231 and 232. Of course, a lubrication structure is applied to allow the vanes 234 to move smoothly between the vane mounting holes 232H of the cylindrical rotors 231 and 232 and the bush 235.

The upper bearing cover 236 and the muffler 237 and the lower bearing cover 238 are coupled to the cylindrical rotors 231 and 232 in the axial direction, between the cylindrical rotors 231 and 232 and the rollers 233 and vanes 234. The compression space is formed and installed in contact with the journal bearing or the thrust bearing at a portion in contact with the fixing member 240. In addition, the upper bearing cover 236 is provided with a discharge port (not shown) through which the refrigerant compressed in the compression space can be discharged and a discharge valve 236A installed therein. It is preferably located adjacent to the vane 233. The muffler 337 is coupled to the upper surface of the upper bearing cover 236, and is provided with a discharge chamber that can reduce the opening and closing noise of the discharge valve 236A and the flow noise of the high-pressure refrigerant therebetween, the discharge chamber is The discharge holes (not shown) provided in the bearing cover 236 and the muffler 237 are communicated with each other. The upper bearing cover 236 and the muffler 237 are coupled to the upper surfaces of the cylindrical rotors 231 and 232, and the lower bearing cover 237 is coupled to the lower surfaces of the cylindrical rotors 231 and 232, and the cylindrical rotors 231 and 232. ) Is fastened at once by fastening members such as long bolts.

The fixed member 240 has a fixed shaft 241 provided in a cylindrical shape and a fixed shaft 241 in all radial directions of the fixed shaft 241 to have a cylindrical shape having a larger diameter than the cylinder of the fixed shaft 241. And an eccentric portion 242 eccentrically formed on the fixed shaft 241 at the same time. A lower portion of the fixed shaft 241 is formed with a first oil supply passage 241A through which oil stored in the sealed container 210 can be supplied, whereas a lower pressure refrigerant can be sucked into the upper portion of the fixed shaft 241. Since the vertical suction passage 241B is formed, and the first oil supply passage 241A and the vertical suction passage 241B are formed to be isolated, the oil may be prevented from escaping together with the refrigerant. The eccentric portion 242 is formed to extend in all radial directions of the fixed shaft 241, and extends to the outer circumferential surface in the radial direction of the eccentric portion 242 so as to communicate with the vertical suction passage 241B of the fixed shaft 241. The horizontal suction passage 242B is provided. Of course, although the roller 233 rotates along the outer circumferential surface of the eccentric portion 242, the refrigerant is provided because the ring-shaped suction guide flow paths 233A and 242C are provided between the inner circumferential surface of the roller 233 and the outer circumferential surface of the eccentric portion 242. Vertical suction passage 241B of the fixed shaft 241, horizontal suction passage 242B of the eccentric portion 242, suction guide passages 233A and 242C between the roller 233 and the eccentric portion 242, roller ( It may be introduced into the compression space along the suction port 233a of the 233. Since the upper and lower surfaces of the eccentric portion 242 come into contact with the upper and lower bearing covers 236 and 237 and serve as a trust surface, it is preferable that a supply passage for lubricating oil is formed on the upper and lower surfaces of the eccentric portion 242. Since the roller 233 abuts on the outer circumferential surface of the eccentric portion 242 so as to be rotatable, it is preferable that a supply passage for lubricating oil extending to the outer circumferential surface is formed inside the eccentric portion 242.

The upper and lower bearings 250 and 260 have the same structure as in the first embodiment, and the rotating member 230 is installed to be suspended to the fixing member 240, and then the upper portion of the fixing shaft 241 is the upper bearing 250. ) Is welded and fixed to the upper portion of the sealed container 210 in a state of being fitted, and welded to the lower portion of the sealed container 210 in a state in which the lower bearing cover 238 is rotatably supported by the lower bearing 260.

On the other hand, looking at the structure rotatably assembled to the fixing member 240, the rotating member 230, the upper and lower bearing cover (236,238) is rotatably installed on the fixing member 230 and the lower bearing (260). More specifically, the upper bearing cover 236 has an upper shaft portion 236a provided with a journal bearing on an inner circumferential surface surrounding the upper portion of the fixed shaft 241, and an upper cover provided with a thrust bearing on a bottom surface in contact with the upper surface of the eccentric portion 242. Part 236b, but the upper cover portion 236b is bolted to the cylindrical rotor (231,232) on the bottom. In addition, the lower bearing cover 238 has a lower shaft portion 238a provided with a journal bearing on an inner circumferential surface surrounding the lower portion of the fixed shaft 241, and a lower cover portion provided with a thrust bearing on an upper surface which is in contact with the bottom surface of the eccentric portion 242. (238b). In addition, the lower bearing 260 is a stepped cylindrical bearing portion 260a surrounding the lower shaft portion 238a and a mounting portion 260b extended in the radial direction of the bearing portion 260a to be welded and fixed inside the sealed container 210. ) At this time, the inner circumferential surface of the bearing portion 260a is provided with a journal bearing for journal-supporting the outer circumferential surface of the lower shaft portion 238a, and a thrust bearing for thrust supporting the lower end of the lower shaft portion 238a on the stepped bottom surface of the bearing portion 260a. Or a separate plate-shaped thrust bearing 261 may be inserted therebetween.

Accordingly, when the upper and lower bearing covers 236 and 238 are coupled to the cylindrical rotors 231 and 232 and the fixing member 240 in the axial direction, the bottom surface of the upper cover portion 236b of the upper bearing cover 236 becomes the cylindrical rotor ( 231,232 is bolted to abut the upper surface, the cover portion 238b of the lower bearing cover 238 is bolted to abut the bottom of the cylindrical rotor (231,232). At this time, since the upper shaft portion 236a is supported by the journal bearing on the upper portion of the fixed shaft 241 and the upper cover portion 236b is thrust supported on the upper surface of the eccentric portion 242, the upper bearing cover 236 is fixed member 240. Lower bearing cover 238 because the lower shaft portion 238a is journal bearing supported under the fixed shaft 241 and the lower cover portion 238b is thrust supported on the bottom of the eccentric portion 242. Is rotatably installed relative to the fixing member 240. In addition, the lower shaft portion 238a of the lower bearing cover 238 is fitted to the bearing portion 260a of the lower bearing 260, and the lower bearing cover 238 is supported by bearings on the journal surface or the thrust surface which abut each other. It is rotatably supported with respect to the lower bearing 260.

10 is a plan sectional view showing a vane mounting structure in a second embodiment of a compressor according to the present invention.

Looking at the mounting structure of the vane 234 with reference to Figure 10, the inner circumferential surface of the cylindrical rotors (231, 232) is provided with a vane mounting hole (232H) is formed in the radial direction and axially penetrated, the vane mounting hole ( After the pair of bushes 235 are fitted to the 232H, the vanes 234 integrally provided on the outer circumferential surface of the roller 233 are fitted between the bushes 235. At this time, a compression space is provided between the cylindrical rotors 231 and 232 and the roller 233, and the compression space is divided into the suction pocket S and the compression pocket D by the vanes 234. The suction port 233a of the roller 233 is located at one side of the vane 234 so as to be in communication with the suction pocket S, and the discharge port and the discharge valve 236A of the upper bearing cover 236 (shown in FIG. 8) described above. 8 is located on the other side of the vane 234 so as to communicate with the compression pocket (D), it is preferably located close to the vane 234 to reduce the dead volume. As such, the vane 234 integrally manufactured with the roller 233 in the compressor of the present invention is assembled to be slidably moved between the bushes 235 in the conventional rotary compressor. The friction loss caused by the sliding contact generated by the spring can be eliminated, and refrigerant leakage can be reduced between the suction pocket S and the compression pocket D. FIG.

Therefore, when the cylindrical rotors 231 and 232 receive the rotational force by the rotating magnetic field with the stator 220 (shown in Fig. 7), the cylindrical rotors 231 and 232 rotate. In the state where the vanes 234 are fitted into the vane mounting holes 232H of the cylindrical rotors 231 and 232, the rotational force of the cylindrical rotors 231 and 232 is transmitted to the roller 233. 234 reciprocates linearly between bushes 235. That is, the inner circumferential surfaces of the cylindrical rotors 231 and 232 have portions corresponding to each other on the outer circumferential surfaces of the rollers 233. The portions corresponding to each other are each of the cylindrical rotors 231 and 232 and the roller 233 rotates once. As the suction pocket (S) gradually grows while repeating contact with each other, the suction pocket (S) gradually grows, while the refrigerant or working fluid is sucked into the suction pocket (S), and the compression pocket (D) gradually decreases. It is compressed and then discharged.

11 is a plan view showing an operating cycle of the compression mechanism in the second embodiment of the compressor according to the present invention.

Looking at the process of suction, compression, and discharge of the compression mechanism, as shown in Figure 11, the cylindrical rotors (231, 232) and the roller 233 is rotated to (a), (b), (c), (d) This shows one cycle where the relative position changes. In more detail, when the cylindrical rotors 231 and 232 and the roller 233 are located at (a), the refrigerant or the working fluid is sucked into the suction pocket S through the suction port 233a of the roller 233, and the suction pocket Compression occurs in the discharged compression pocket D, which is divided into S and the vanes 234. Even when the cylindrical rotors 231 and 232 and the roller 233 arrive at (b) while rotating, the suction pocket S increases and the compression pocket D decreases, so that the refrigerant or the working fluid is sucked into the suction pocket S. In this case, compression continues to occur in the compression pocket (D). When the cylindrical rotors 231 and 232 and the roller 233 arrive at (c) while rotating, they are continuously sucked into the suction pocket S, and the pressure of the refrigerant or the working fluid in the compression pocket D becomes higher than the set pressure. The refrigerant or the working fluid is discharged through the discharge port of the upper bearing cover 236 (shown in FIG. 8) and the discharge valve 236A (shown in FIG. 8). In (d), suction and discharge of the refrigerant or working fluid are almost finished.

12 is a perspective view showing an example of the vane lubrication structure in the second embodiment of the compressor according to the present invention.

Looking at the vane lubrication structure in the second embodiment of the compressor according to the present invention with reference to Figures 10 and 12, the engaging projection 232a protruding to the outer peripheral surface of the cylinder 232 to form the inner peripheral surface of the rotor 231 is And a vane mounting hole 232H extending from the inner circumferential surface of the cylinder 232 to a part of the coupling protrusion 232a, and the vane 234 abuts between the bushes 235 on the vane mounting hole 232H. The lower bearing cover 238 is installed so as not to cover a part of the bottom surface of the vane mounting hole 232H of the cylinder 232. At this time, since the vane mounting holes 232H are provided in the engaging projection 232a protruding from the circular cylinder 232, the engaging projection even if the lower cover portion 238b of the lower bearing cover 238 is formed in a disc shape. It may be installed so as not to cover a part of the vane mounting holes (232H) extended to (232a). In addition, even if the lower cover portion 238b of the lower bearing cover 238 is formed in a disc shape, the outer circumferential portion thereof is formed stepped so as not to cover a part of the vane mounting holes 232H extending to the coupling protrusion 232a. Can be. As such, in order to allow oil to flow through the bottom surface of the vane mounting hole 232H, the oil level of the oil inside the sealed container 210 (as shown in FIG. 7) is not only maintained higher than that of the lower bearing cover 238, and the vane mounting hole is provided. It is preferable that the bottom end of 232H be kept locked. However, when the oil is introduced into the vane mounting holes 232H through the bottom of the vane mounting holes 232H, it is difficult to maintain the oil level of the oil above a certain height because it is mixed with the compressed refrigerant and exits to the outside. Therefore, it is preferable that an oil recovery structure is applied in order to maintain an appropriate amount of oil or more in the sealed container 210 (shown in FIG. 7). Looking at the oil recovery structure of the above embodiment, the oil separation installed in the discharge port of the upper bearing cover 236 and the discharge port of the muffler 237 (shown in Figure 9) is installed directly on the muffler 237 (shown in Figure 9). Upon hitting plate 280 (shown in FIG. 7), the oil is separated from the compressed refrigerant. As such, the refrigerant from which the oil is separated exits through a hole (not shown) provided in the oil separation plate 280 (shown in FIG. 7), and the oil separated from the refrigerant is an oil separation plate (280 shown in FIG. 7). From above onto the rotor 231 or upper bearing cover 236 and then to the bottom of the sealed container 210 (shown in FIG. 7) along the oil return path between the parts. At this time, the oil return flow passage may be composed of a gap between the stator 220 and the rotor 231, or a jig may be mounted to bolt the cylinder 232 to the upper and lower bearing covers 236 and 238. It may be composed of a series of jig mounting holes (not shown) provided in the cylinder 231 and the upper and lower bearing cover (236,238) so as to communicate vertically.

In addition, referring to another example of the vane lubrication structure, the upper bearing cover 236 is installed so as not to cover a part of the upper surface of the vane mounting hole 232H of the cylinder 232, and inside the sealed container 210 (shown in FIG. 7). The oil level is preferably kept higher than the upper bearing cover 236 as well as the top of the vane fitting 232H is locked.

In the above, the present invention has been described in detail by way of examples based on the embodiments of the present invention and the accompanying drawings. However, the scope of the present invention is not limited by the above embodiments and drawings, and the scope of the present invention will be limited only by the contents described in the claims below.

1 is a side sectional perspective view showing a first embodiment of a compressor according to the present invention;

2 is an exploded perspective view showing a first embodiment of a compressor according to the present invention;

3 is a side sectional view showing a first embodiment of a compressor according to the present invention;

Figure 4 is a plan view showing the vane mounting structure in the first embodiment of the compressor according to the present invention.

5 is a plan view showing an operation cycle of the compression mechanism in the first embodiment of the compressor according to the present invention.

6 is a perspective view showing an example of the vane lubrication structure in the first embodiment of the compressor according to the present invention.

Figure 7 is a side sectional perspective view showing a second embodiment of the compressor according to the present invention.

8 is an exploded perspective view showing a second embodiment of the compressor according to the present invention.

9 is a side sectional view showing a second embodiment of a compressor according to the present invention;

10 is a plan view showing a vane mounting structure in a second embodiment of a compressor according to the present invention;

11 is a plan view showing the operating cycle of the compression mechanism in the second embodiment of the compressor according to the present invention.

12 is a perspective view showing an example of the vane lubrication structure in a second embodiment of the compressor according to the present invention.

Claims (15)

A hermetically sealed container in which the refrigerant is sucked and discharged and the oil is stored; A stator fixed in a sealed container; A fixing member installed at an upper end of the fixed shaft so as not to move in the sealed container and extending in the sealed container at the same time; Located inside the stator, it can suck and compress the refrigerant into the compression space formed therein while rotating around the fixed axis by mutual electromagnetic force with the stator, and the compression space is compressed and discharged into the suction pocket and the refrigerant suction A rotating member including a vane reciprocating so as to be partitioned into a compression pocket, and a vane mounting hole accommodating the vanes; And an oil supply hole communicating a part of the vane mounting hole to the inner space of the sealed container so that the oil in the inner space is supplied to the vane mounting hole. The method of claim 1, The rotating member includes a rotor provided between the stator and the fixing member so as to rotate about the fixing member by mutual electromagnetic force with the stator, a cylinder laminated to the rotor, rotating together with the rotor, and having a compression space therein, an eccentric portion and A vane that is elastically supported by the cylinder to rotate with the cylinder and is in sliding contact with the outer surface of the eccentric portion so as to partition the compressed space between the cylinders into a suction pocket into which the refrigerant is sucked and a compression pocket into which the refrigerant is compressed and discharged. A vane mounting hole formed in a shape, a vane spring stopper for blocking the vane mounting hole so that the vane spring supporting the vane elastically, and an upper and lower portion of the compression space are formed to rotate around the fixing member together with the rotating member. Compressor comprising an upper and lower bearing cover. The method of claim 2, The oil supply hole is formed in the vane spring stopper to communicate with the vane mounting hole at a position lower than the oil level of the oil stored in the airtight container, so that the oil can be supplied to the vane mounting hole. The method of claim 1, The vane fitting is extended to the vane evacuation protrusion formed by protruding from the outer peripheral surface of the cylinder, A compressor, characterized in that the open space of the vane evacuation protrusion, which is not closed by at least one of the upper and lower bearing covers, functions as an oil supply hole to the vane mounting hole. The method of claim 4, wherein And the lower open space of the vane evacuation protrusion, which is not closed by the lower bearing cover, is an oil supply hole communicating with the oil stored in the sealed container. The method of claim 3, And the upper open space of the vane evacuation protrusion not closed by the upper bearing cover is an oil supply hole communicating with the oil collected on the upper bearing cover. The method of claim 1, The rotating member is a cylindrical rotor, which is rotatably supported by the fixed member so as to rotate about a fixed shaft by a rotating electromagnetic field from the stator, and receives a rotational force of the cylindrical rotor while rotating about the eccentric with the cylindrical rotor. Roller that forms a compression space between the rotor, vane which transmits the rotational force from the cylindrical rotor to the roller and divides the compression space into the suction pocket where the refrigerant is sucked in and the compression pocket where the refrigerant is compressed and discharged, and the cylinder from the outer peripheral surface of the roller. The vane mounting hole is formed integrally with the roller to protrude toward the rotor, and the upper and lower bearing cover which rotates about the fixed member together with the rotating member to form upper and lower portions of the compression space. Compressor made. The method of claim 7, wherein A compressor, characterized in that the open space of the vane fitting, which is not closed by at least one of the upper and lower bearing covers, functions as an oil supply hole to the vane fitting. The method of claim 8, Compressor, characterized in that the lower open space of the vane mounting opening is not closed by the lower bearing cover is an oil supply hole in communication with the oil stored in the sealed container. The method of claim 8, And the upper opening of the vane fitting not closed by the upper bearing cover is an oil supply hole communicating with oil collected on the upper bearing cover. The method according to any one of claims 1 to 10, The fixing member is formed so as to be spaced apart from the lower end of the first fixing member, the first fixing member including an eccentric portion formed so as to be eccentric to the fixed shaft and the fixed shaft is installed on the upper end and long extending into the sealed container so as not to move in the sealed container It is divided into a second fixing member which is installed so as not to move in the lower portion of the sealed container, The rotating member is rotated about the first fixing member, characterized in that the compressor is rotatably supported while applying a load on the second fixing member. The method of claim 11, The rotating member further includes a cylinder having a compression space therein, and upper and lower bearing covers which form upper and lower portions of the compression space and rotate about the fixed shaft together with the rotating member. The upper bearing cover includes an upper shaft portion surrounding the fixed shaft, and an upper cover portion coupled to the cylinder to form an upper portion of the compression space. And an inner surface of the upper shaft portion is rotatably journal-supported to an outer surface of the fixed shaft, and a bottom surface of the upper cover portion is rotatably supported by an upper surface of the eccentric portion. The method of claim 11, The rotating member further includes a cylinder having a compression space therein, and upper and lower bearing covers which form upper and lower portions of the compression space and rotate about the fixed shaft together with the rotating member. The lower bearing cover includes a lower shaft portion surrounding the fixed shaft and a lower cover portion coupled to the cylinder to form a lower portion of the compression space. And an inner surface of the lower shaft portion is rotatably journal-supported to an outer surface of the fixed shaft, and an upper surface of the lower cover portion is rotatably supported by the bottom of the eccentric portion. The method of claim 11, The rotating member further includes a cylinder having a compression space therein, and upper and lower bearing covers which form upper and lower portions of the compression space and rotate about the fixed shaft together with the rotating member. The lower shaft portion formed to surround the fixed shaft in the lower bearing cover is formed so as to extend than the lower end of the fixed shaft, the end of the lower shaft portion is characterized in that the rotatably supported while applying the load of the rotating member to the second fixing member . The method of claim 14, The second fixing member further includes a cylindrical bearing portion having a step therein, And a lower end portion of the lower shaft portion is thrust-supported at the step of the second fixing member, and an outer surface of the lower shaft portion is journal-supported on the inner surface of the cylindrical bearing portion.

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