KR20110015859A - Compressor - Google Patents

Abstract

PURPOSE: A compressor enhancing an oil retrieval rate is provided to retrieve oil from the compressed refrigerant and to improve the structural safety. CONSTITUTION: A compressor comprises a sealed container, a stator(120), a fixing member, a rotating member, an outlet, and an oil separating plate(180). Oil is saved in the sealed container. The stator is fixed within the sealed container. The fixing member is fixed to the sealed container and is expanded to the inside of the sealed container.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor for compressing a refrigerant while rotating in a state in which the rotating member is suspended on a fixed member and supported on a bearing, and in particular, it is possible not only to achieve structural stabilization but also to improve assemblability and to increase oil recovery rate. Relates to a compressor.

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.

It is also an object of the present invention to reduce the lateral vibration caused by eccentric rotation as well as to provide a compressor that is easy to assemble in actual production.

Another object of the present invention is to provide a compressor capable of separating oil mixed in a compressed refrigerant.

Another object of the present invention is to provide a compressor capable of recovering oil separated from a compressed refrigerant.

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; Fixed part which is installed at the top of the fixed shaft so as not to move in the sealed container at the same time long extending into the sealed container; A rotating member positioned inside the stator and capable of sucking and compressing a refrigerant into a compression space formed therein while rotating about a fixed shaft by mutual electromagnetic forces with the stator; A discharge port provided in the rotating member and discharging the compressed refrigerant from the compression space into the sealed container; And an oil separation plate separating the oil mixed in the refrigerant by its own weight while the refrigerant discharged from the discharge port collides with each other.

In addition, in the present invention, the fixing member further comprises an eccentric portion eccentric from the axial center of the fixed shaft, the rotating member is a rotor installed to rotate by mutual electromagnetic force with the stator, and is laminated on the lower portion of the rotor to rotate with the rotor and the compression space A cylinder provided therein, a vane elastically supported by the cylinder so as to divide the compression space between the eccentric portion and the cylinder into a suction pocket into which the refrigerant is sucked, and a compression pocket into which the refrigerant is compressed and discharged, and upper and lower portions of the compression space. It further comprises an upper and lower bearing cover to rotate about a fixed shaft with a rotating member, the discharge port is characterized in that provided in the upper bearing cover.

In the present invention, the oil separation plate is fixed to any one of the inner circumferential surface of the stator or the upper surface of the rotor to form a predetermined space in the rotor.

In addition, in the present invention, the fixing member further comprises an eccentric portion eccentric from the axial center of the fixed shaft, the rotating member is a cylindrical rotor installed to rotate about the fixed shaft by mutual electromagnetic force with the stator, and the rotational force of the cylindrical rotor The roller which forms a compression space between the cylindrical rotor while being rotated about the eccentric part with the cylindrical rotor, and the suction pocket and the refrigerant that transfer the rotational force from the cylindrical rotor to the roller and suck the refrigerant into the compression space A vane formed integrally on the outer circumferential surface of the roller so as to be partitioned into compression pockets compressed and discharged, upper and lower bearing covers which form upper and lower portions of the rotating member and the compression space to rotate about a fixed shaft together with the rotating member, and an upper bearing cover And a muffler coupled in the axial direction of the upper bearing cover so as to communicate with the discharge. Is characterized in that the provided at each of the upper bearing cover and the muffler.

In addition, in the present invention, the oil separation plate is characterized in that fixed to any one of the muffler, the upper bearing cover, the sealed container so as to close to the discharge port of the muffler.

In addition, in the present invention, the oil separation plate is characterized in that a plurality of holes through which the refrigerant separated oil is provided.

In addition, in the present invention, the cylinder and the upper and lower bearing cover is provided with a jig mounting hole in which the assembling jig is axially mounted to bolt the upper and lower bearing cover to the cylinder, and the oil separated by the oil separation plate. Silver is recovered to the bottom of the sealed container through the jig mounting port.

In addition, in the present invention, the cylinder and the upper and lower bearing cover is provided with a jig mounting hole in which the assembling jig is axially mounted to bolt the upper and lower bearing cover to the cylinder, and the oil separated by the oil separation plate. Silver is recovered to the bottom of the sealed container through the jig mounting port.

In addition, in the present invention, the oil recovery passage for guiding the oil separated by the oil separation plate to the bottom of the sealed container; characterized in that it further comprises.

Further, in the present invention, the oil recovery passage is characterized in that the gap between the stator and the rotating member.

In addition, in the present invention, the fixing member further comprises an eccentric portion eccentric from the axial center of the fixed shaft, the rotating member is a rotor installed to rotate by mutual electromagnetic force with the stator, and is laminated on the lower portion of the rotor to rotate with the rotor and the compression space A cylinder provided therein, a vane elastically supported by the cylinder so as to divide the compression space between the eccentric portion and the cylinder into a suction pocket into which the refrigerant is sucked, and a compression pocket into which the refrigerant is compressed and discharged, and upper and lower portions of the compression space. And an upper and lower bearing cover which is formed and rotates about the fixed shaft together with the rotating member, and the oil return flow passage further includes a cylinder and an upper part in which the assembly jig is axially mounted to bolt the upper and lower bearing covers to the cylinder. And it is characterized in that the jig mounting holes provided to communicate with the lower bearing cover.

In addition, in the present invention, the fixing member further comprises an eccentric portion eccentric from the axial center of the fixed shaft, the rotating member is a cylindrical rotor installed to rotate about the fixed shaft by mutual electromagnetic force with the stator, and the rotational force of the cylindrical rotor The roller which forms a compression space between the cylindrical rotor while being rotated about the eccentric part with the cylindrical rotor, and the suction pocket and the refrigerant that transfer the rotational force from the cylindrical rotor to the roller and suck the refrigerant into the compression space A vane formed integrally on the outer circumferential surface of the roller so as to be partitioned into compression pockets compressed and discharged, upper and lower bearing covers which form upper and lower portions of the rotating member and the compression space to rotate about a fixed shaft together with the rotating member, and an upper bearing cover Further comprising a muffler coupled in the axial direction of the upper bearing cover in communication with the A feeding is characterized in that the mounting fixture so that the job includes a jig for assembling the cylinder and communicating with the upper and lower bearing cover which is mounted in the axial direction in order to bolt the upper and lower bearing cover on the cylinder.

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, in the compressor according to the present invention, the oil is separated from the refrigerant while the compressed refrigerant mixed with the oil is discharged, and the oil is separated from the refrigerant, and only the oil separated refrigerant passes through the oil separation plate to the outside, so that the oil falls out of the compressor. The outgoing circulation rate can be lowered, and the lubrication by an appropriate amount or more of oil can be smoothly performed to secure lubrication performance and operation reliability.

In addition, the compressor according to the present invention is relatively recovered because the oil separated from the compressed refrigerant flows quickly through the jig mounting holes provided for fastening the cylinder and the upper and lower bearing covers in addition to the gap between the stator and the rotor. Even if only a small amount of oil is provided, or even at high speed, the compressor can maintain a proper amount of oil level in the compressor, and the lubrication by such oil is smoothly performed to secure lubrication performance and operation 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 includes a rotor 131 of the rotating member 130, including the stator 120, the compressor mechanism for compressing the refrigerant through the mechanical action is a rotating member ( And a fixing member 140 including 130. 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 141 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. And an eccentric portion 142 eccentrically formed on the fixed shaft 141 at the same time. 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, The body portion 111 of the sealed container 110 is fixed by shrinkage or three-point welding or the like. 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 rotatable 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. . 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 side sectional view showing a refrigerant flow structure in a first embodiment of a compressor according to the present invention.

1 and 6, a vertical suction passage 141B is provided to allow refrigerant to be sucked into a hollow space above the fixed shaft 141 fixed to the center of the sealed container 110. A discharge tube 115 may be provided on the sealed container 110 to discharge the compressed refrigerant filled in the sealed container 110.

For suction of the refrigerant, a vertical suction passage 141B is provided in the axial direction on the upper portion of the fixed shaft 141, and the horizontal suction passage passes through the eccentric portion 142 so as to communicate with the vertical suction passage 141B. 142B is provided, and the horizontal suction passage 142B is directly in communication with the compression space. Of course, the vertical suction passage 141B and the horizontal suction passage 142B, through which the refrigerant flows, are provided with a refrigerant supply passage 141A provided in the fixed shaft 141 and the eccentric portion 142 such that oil flows. Formed separately).

In order to discharge the refrigerant, a discharge port and a discharge valve 135A are provided in the upper bearing cover 135 so as to communicate with the compression space and the inner space of the sealed container 110, and the inner space and the sealed container 110 of the sealed container 110 are provided. The discharge pipe 110 is provided outside the upper surface. At this time, the discharge port and the discharge valve 135A of the upper bearing cover 135 is preferably located close to the vane 133 in order to reduce the dead volume, the upper bearing cover and the vane 133 is moved together because the upper bearing The discharge port and the discharge valve 135A of the cover 135 are rotated together while maintaining the same position as the vane 133.

In addition, the refrigerant exiting the discharge port and the discharge valve 135A of the upper bearing cover 135 will remain in the inner space of the rotor 131, in order to prevent oil from being mixed with the compressed refrigerant to escape the oil separation plate 180 ) Is installed at any one of the inner circumferential surface of the stator 120, the upper surface of the rotor 131, the upper bearing cover 135, and the fixed shaft 142 so that the rotor 131 is positioned directly above the rotor 131. At this time, the oil separation plate 180 is provided with a plurality of holes 180h through which the refrigerant from which oil is separated can escape into the inner space of the sealed container 110, and the holes 180h are spaced in a circumferential direction at a peripheral portion thereof. A plurality is provided with.

Therefore, when the low pressure refrigerant is sucked along the vertical suction passage 141B of the fixed shaft 141, the suction pocket S of the compression space (S: shown in FIG. 4) is provided through the horizontal suction passage 142B of the eccentric portion 142. Flows into. At this time, the eccentric portion 142 remains stationary, but the cylinder 132 and the upper and lower bearing covers 135 and 136 rotate about the fixed shaft 141, while the vane 133 is the eccentric portion 142. Since it rotates around the volume of the suction pocket (S: shown in Figure 4) and the compression pocket (D: shown in Figure 4) as described above, the refrigerant is compressed. Thereafter, when the refrigerant compressed in the compression pocket (D: shown in FIG. 4) becomes higher than the set pressure, the discharge valve 135A provided in the upper bearing cover 135 is opened, and the compressed refrigerant is the upper bearing cover 135. Through the outlet of the At this time, the opening and closing noise of the discharge valve 135A and the flow noise of the high-pressure refrigerant are reduced in the space between the rotor 131, the upper bearing cover 135, and the oil separation plate 180, and the compressed refrigerant is separated from the oil separation plate ( 180) and remove the oil. As such, only the refrigerant from which the oil is separated is filled in the sealed container 110 through the holes 180h of the oil separation plate 180, and exits to the outside through the discharge tube 115 of the sealed container 110. At this time, the reason why the oil is mixed in the compressed refrigerant will be described in more detail below.

7 is a side sectional view showing an oil circulation structure in the first embodiment of the compressor according to the present invention.

In the first embodiment of the compressor as described above, the rotating member 130 is installed to hang on the fixing member 140, and is supported by the lower bearing 160 to be rotatable, so that the rotating member 130 is fixed member 140 ) And the part where the rotating member 130 is supported by the lower bearing 160, that is, the lubrication surface must be lubricated. In addition, the rotating member 130 and the fixing member 140 and the lower bearing 160 Lubrication is required between the parts that abut each other.

The oil level of the oil stored in the sealed container 110 (shown in FIG. 1) is at least higher than the lower bearing 160 as shown in FIGS. 1 and 7, or lower than the lower end of the lower shaft portion 136a of the lower bearing cover 136. It is desirable to remain high. Therefore, as described above, since the lower shaft portion 136a of the lower bearing cover 136 is accommodated in the bearing portion 160a of the lower bearing 160, the surfaces in contact with each other, that is, the journal surface and the trust surface, respectively support bearings. Since the contact surface is immersed in oil, a separate lubricating oil path may not be provided.

However, it is preferable that the lubricating oil passage is provided at a portion where the rotating member 130 and the fixing member 140 contact each other, and the lubricating oil can be divided into a lower lubricating oil passage, an oil supply member, and an upper lubricating oil passage. The lower lubrication passage is configured to supply the oil stored in the lower portion of the sealed container 110 to abutting portions of the lower bearing cover 136, the fixed shaft 141, and the eccentric portion 142, and the oil supply member 170 rotates. It is configured to pump the oil as it rotates with the member 130, the upper lubricating flow path is oil pumped by the oil supply member 170, the upper bearing cover 136 and the fixed shaft 141 and the eccentric portion 142 It is configured to supply to abutting parts of each other.

The lower lubricating oil passage has a first oil supply passage 141A, which is a hollow space perpendicular to the lower portion of the fixed shaft 141, and an oil supply hole penetrated in the radial direction below the fixed shaft 141 so as to communicate with the oil supply passage 141A. (Not shown) and the first oil supply groove formed on the outer circumferential surface of the fixed shaft 141 directly below the eccentric portion 142 and the eccentric portion 142 which are in contact with the lower bearing cover 136 so as to communicate with the oil supply hole. , b). In addition, in order to supply oil to the first oil supply grooves a and b even if the oil does not pass through the first oil supply passage 141A and the oil supply hole, the inner peripheral surface of the lower shaft portion 136a of the lower bearing cover 136 is provided. Vertical or straight grooves (not shown) may be formed to communicate with the first oil supply grooves a and b.

The oil supply member 170 is installed in the hollow shaft portion 171 of the cylindrical shaft fitted to the lower shaft portion 136a of the lower bearing cover 136, and is installed inside the hollow shaft portion 171 and the hollow shaft portion 171 by a rotational force. It includes a propeller 172 so that the oil is supplied through the flow path. Therefore, the oil supply member 170 is rotated in the state submerged in the oil, such as the lower bearing cover 136, the oil is raised through the oil supply member 170.

The upper lubrication structure includes two or more extending to the upper surface of the eccentric portion 142 so as to communicate with the first oil supply passage 141A of the fixed shaft 141 and the first oil supply passage 141A of the fixed shaft 141. Upper and eccentric portions of the eccentric portion 142 contacting the upper bearing cover 135 so as to communicate with the second oil supply passage 142A of the eccentric portion 142 and the second oil supply passage 142A of the eccentric portion 142. (142) a second oil supply groove (c, d) formed on the outer circumferential surface of the fixed shaft 141 immediately above, the second oil supply passage (142A) provided in the eccentric portion (142) is the eccentric portion (142) It is preferable to be provided so as not to overlap with the horizontal suction passage (142B: shown in Figure 3) provided in. In addition, the oil stored in the second oil supply grooves (c, d) to be lubricated as it rises along the surface in contact with the upper shaft portion (135a) and the upper portion of the fixed shaft (142) of the upper bearing cover 135 In order to communicate with the second oil supply grooves c and d, vertical or straight grooves (not shown) may be formed on the inner circumferential surface of the upper shaft portion 135a of the upper bearing cover 135 as shown in FIG. 8. Can be.

Therefore, since the oil stored under the sealed container 110 is formed at a higher oil surface than the oil supply hole, including the lower lower shaft portion 136a of the lower bearing cover 136, the oil is supplied with the first oil of the fixed shaft 141. It flows into the first oil supply grooves a and b through the flow path 141A, the oil supply hole of the fixed shaft 141, and the groove of the lower bearing cover 136. At this time, as the lower shaft portion 136a of the lower bearing cover 136 is immersed in oil, lubrication is performed between the lower bearing 160 and the lower bearing cover 136 is the first oil supply groove (a, b). ) And the groove 136g are lubricated between the fixed shaft 141 and the eccentric portion 142 and rotatably installed. In addition, the oil is pumped by the oil supply member 170 as the rotating member 130 rotates, the oil is the first oil supply passage 141A of the fixed shaft 141, the second of the eccentric portion 142 Through the oil supply passage 142A, it is introduced into the second oil supply grooves c and d, and further rises through the groove of the upper bearing cover 135. At this time, the upper bearing cover 136 is lubricated between the fixed shaft 141 and the eccentric portion 142 by the oil collected in the second oil supply grooves (c, d) and the groove (135g) to be rotatable at the same time. Is installed.

In addition, the oil is introduced into the vane mounting holes 132H (shown in FIG. 4) to lubricate the vanes 133, and the vane mounting holes (132H (shown in FIG. 4)) as shown in FIGS. 3 and 7. A hole (not shown) is provided in the vane spring supporter 137 for blocking, and an oil surface is formed higher than that of the vane spring supporter 137. Therefore, oil is introduced into the vane mounting hole 132H (shown in FIG. 4) through the hole of the vane spring supporter 137, and the oil is lubricated between the vane 133 and the vane mounting hole 132H (shown in FIG. 4). As the oil enters the compression space, the oil is compressed and discharged together with the refrigerant.

However, the oil mixed in the compressed refrigerant is discharged from the discharge port of the upper bearing cover 135 and the discharge valve 135A, and then only oil is separated from the refrigerant while hitting the oil separation plate 180. Thereafter, the refrigerant flows out through the discharge tube 115 (shown in FIG. 1) of the sealed container 110 (shown in FIG. 1) through the holes 180h of the oil separation plate 180 as shown in FIG. 6. On the other hand, the oil is recovered to the lower portion of the sealed container 110 (shown in FIG. 1) while falling while expanding radially while hitting the oil separation plate 180 as shown in FIG. 7. At this time, the oil is recovered through the gap (H) between the stator 120 and the rotor 131, which is a kind of oil return flow path, or to fasten the bolt (B) to the cylinder 132 and the upper and lower bearing covers 135 and 136. The jig can be quickly retrieved through a series of jig mounts 132H, 135H, 136H that can be mounted. Therefore, the oil mixed in the compressed refrigerant is separated by the oil separation plate 180 and is quickly sealed through the oil recovery passages H, 132H, 135H, and 136H provided between the parts. It is recovered to the bottom, and is circulated again inside the compressor through the oil lubrication structure.

8 to 10 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 in the first embodiment, the second embodiment of the compressor according to the present invention, as shown in FIGS. 8 to 10, 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 sealed 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. The 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 configured separately, but may be combined, but integrally formed in the form of a powder sintered body or a laminate in which iron pieces are laminated. May be 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 for reducing the opening and closing noise of the discharge valve 236A and the flow noise of the high-pressure refrigerant, the discharge chamber is the upper bearing The discharge hole (not shown) provided in the cover 236 and the muffler 237 are respectively communicated with. 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 233 Along the suction port 233a of the) may be introduced into the compression space. 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.

11 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 11, 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 on 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. 9) described above. 9 is located on the other side of the vane 234 so as to communicate with the compression pocket (D), it is preferable to be 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. 8), the cylindrical rotors 231 and 232 rotate. While the vane 234 is 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, and the vanes 234 according to the rotation of both vanes 234. ) Reciprocates linearly between the 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.

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

Referring to the process of suction, compression, and discharge of the compression mechanism, as shown in FIG. 12, the cylindrical rotors 231 and 232 and the roller 233 rotate to (a), (b), (c) and (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. 9) and the discharge valve 236A (shown in FIG. 9). In (d), suction and discharge of the refrigerant or working fluid are almost finished.

Figure 13 is a side sectional view showing a refrigerant flow structure in the second embodiment of the compressor according to the present invention.

8 and 13, a vertical suction passage 241B is provided to allow refrigerant to be sucked into a hollow space above the fixed shaft 241 fixed to the sealed container 210. The discharge pipe 214 through which the refrigerant can be discharged is provided on the 210.

For suction of the refrigerant, a vertical suction passage 241B is provided in the axial direction on the upper portion of the fixed shaft 241, and the horizontal suction passage passes through the eccentric portion 242 so as to communicate with the vertical suction passage 241B. (242B) is provided, the suction suction guide flow path (242C, 233A) in the form of a ring is provided between the circumference of the eccentric portion (242) and the inner peripheral surface of the roller 233 to communicate the horizontal suction passage (242B) and the compression space at the same time A suction port 233a (shown in FIG. 11) penetrated through the roller 233 is provided to communicate with the guide passages 242C and 233A. Of course, the vertical suction passage 241B, the horizontal suction passage 242B, and the suction guide passages 242C and 233A, through which the refrigerant flows, are provided with an oil supply passage provided on the fixed shaft 241 and the eccentric portion 242 so that oil flows. It is preferably formed separately from 241A (not shown). In addition, the suction port 233a (shown in FIG. 11) of the roller 233 is preferably formed to be close to the vane 234 so that suction may continue even when the roller 233 is rotated, and the roller 233 and the vane Since the 234 moves together, the suction port 233a (shown in FIG. 11) of the roller 233 rotates together while maintaining the same position as the vane 234.

In order to discharge the refrigerant, a discharge port and a discharge valve 236A are provided in the upper bearing cover 236 so as to communicate with the compression space and the inner space of the sealed container 210, and the muffler coupled in the axial direction to the upper bearing cover 236. The discharge port 237h is provided at the 237, and the discharge tube 214 is provided at an outer space of the sealed container 210 and an upper surface of the sealed container 210. At this time, the discharge port and the discharge valve 236A of the upper bearing cover 236 is close to the vane 234 so as to be partitioned by the suction port 233a (shown in FIG. 11) and the vane 234 of the roller 233. Preferably, the upper bearing cover 236 has the roller 233 and the vane 234 moving together, so that the discharge port and the discharge valve 236A of the upper bearing cover 236 have the suction hole ( 233a: shown in FIG. 11) and the vanes 234 are rotated while maintaining the same position relative to.

In addition, the sealed container 210, the stator 220, the rotor 231, the muffler 237 so that the oil separation plate 280 is located directly above the muffler 231 in order to prevent oil from being mixed with the compressed refrigerant. , Is installed in any one of the fixed shaft (242). In this case, the oil separation plate 280 is provided with a plurality of holes 280h through which the refrigerant from which oil is separated may escape into the inner space of the sealed container 210, and the holes 280h are spaced in the circumferential direction at predetermined intervals. A plurality is provided with.

Therefore, when the low pressure refrigerant is sucked along the vertical suction passage 241B of the fixed shaft 241, the suction guide between the horizontal suction passage 242B of the eccentric portion 242, the eccentric portion 242, and the roller 233 is provided. It flows into the suction pocket (S: shown in FIG. 11) of a compression space through the flow paths 242C and 233A, and the suction port 233a of the roller 233 (shown in FIG. 11). At this time, the eccentric portion 242 remains stationary, but the cylindrical rotors 231 and 232 and the upper and lower bearing covers 236 and 238 rotate about the fixed shaft 241 and the vane integral rollers 233 and 234 are deflected. Since it rotates around the core 242, the volume of the suction pocket S (shown in FIG. 11) and the compression pocket D (shown in FIG. 11) gradually changes as described above, and thus the refrigerant is compressed. Thereafter, when the refrigerant compressed in the compression pocket (D: shown in FIG. 11) becomes higher than the set pressure, the discharge valve 236A provided in the upper bearing cover 236 is opened, and the compressed refrigerant is the upper bearing cover 236. Through the outlet of the At this time, the opening and closing noise of the discharge valve 236A and the flow noise of the high-pressure refrigerant are reduced in the space between the upper bearing cover 236 and the muffler 237, and the compressed refrigerant exits the discharge port 237h of the muffler 237. After exiting, the oil is separated from the refrigerant while hitting the oil separation plate 280. As such, only the refrigerant from which the oil is separated is filled in the sealed container 210 through the holes 280h of the oil separation plate 280, and exits to the outside through the discharge tube 214 of the sealed container 210.

14 is a side sectional view showing an oil circulation structure in a second embodiment of a compressor according to the present invention.

Similarly to the first embodiment, the second embodiment of the compressor as described above, the rotating member 230 is installed so as to hang on the fixing member 240, and is supported rotatably on the lower bearing 260, the rotating member 230 ) Is suspended to the fixing member 240, the portion that the rotating member 230 is supported on the lower bearing 260, that is, the lubrication must be made to the surface, in addition to the rotating member 230 and the fixing member 240 Lubrication is required between the abutting parts of the bottom bearing 260.

However, the lubricating oil passage is preferably provided at a portion where the rotating member 230 and the fixing member 240 contact each other, and the lubricating oil may be divided into a lower lubricating oil passage, an oil supply member, and an upper lubricating oil passage.

The lower lubricating oil passage has a first oil supply passage 241A, which is a hollow space perpendicular to the lower portion of the fixed shaft 241, and an oil supply hole penetrated in the radial direction below the fixed shaft 241 so as to communicate with the oil supply passage 241A. (Not shown) and the first oil supply groove (a) formed on the bottom surface of the eccentric portion 242 contacting the lower bearing cover 238 and the outer peripheral surface of the fixed shaft 241 immediately below the eccentric portion 242 so as to communicate with the oil supply hole. , b). Of course, the oil surface is preferably formed so that the lower bearing cover 238 is locked. In addition, in order to supply oil to the first oil supply grooves a and b even if the oil does not pass through the first oil supply passage 241A and the oil supply hole, the inner circumferential surface of the lower shaft portion 238a of the lower bearing cover 238 is provided. Vertical or straight grooves (not shown) may be formed to communicate with the first oil supply grooves a and b.

The oil supply member 270 is installed inside the hollow shaft portion 271 of the cylindrical shaft 271 fitted to the lower shaft portion 238a of the lower bearing cover 238, and the hollow shaft portion 271 and the hollow shaft portion 271 by a rotational force. It includes a propeller 272 to supply the oil through the flow path. Therefore, the oil supply member 270 rotates in the state submerged in the oil like the lower bearing cover 236, and the oil is raised through the oil supply member 270.

The upper lubrication structure includes at least two extending to the upper surface of the eccentric portion 242 so as to communicate with the first oil supply passage 241A of the fixed shaft 241 and the first oil supply passage 241A of the fixed shaft 241. Upper and eccentric portions of the eccentric portion 242 contacting the upper bearing cover 236 so as to communicate with the second oil supply passage 242A of the eccentric portion 242 and the second oil supply passage 242A of the eccentric portion 242. A second oil supply groove (c, d) formed on the outer circumferential surface of the fixed shaft 241 immediately above, the second oil supply passage 242A provided in the eccentric portion 242 is the eccentric portion 242 It is preferable to be provided so as not to overlap with the horizontal suction passage (242B) provided in. In addition, the oil stored in the second oil supply grooves (c, d) to be lubricated as the oil is raised along the surface in contact with the upper shaft portion 236a and the upper portion of the fixed shaft 242 of the upper bearing cover 236 To this end, vertical or straight grooves (not shown) may be formed on the inner circumferential surface of the upper shaft portion 236a of the upper bearing cover 236 so as to communicate with the second oil supply grooves c and d.

Therefore, the oil stored under the sealed container 210 is first oil supplied through the first oil supply passage 241A of the fixed shaft 241, the oil supply hole of the fixed shaft 241, and the groove of the lower bearing cover 238. It flows into the supply grooves a and b. Accordingly, the lower bearing cover 238 is lubricated by the oil collected in the first oil supply grooves a and b and the groove, and is rotatably installed with respect to the fixed shaft 241 and the eccentric portion 242. Subsequently, when the oil on the first oil supply passage 241A of the fixed shaft 241 is pumped by the oil supply member 270 as the rotating member 230 rotates, the oil may be the first of the fixed shaft 241. The oil supply passage 241A and the second oil supply passage 242A of the eccentric portion 242 flow into the second oil supply grooves c and d as well as the grooves of the upper bearing cover 236. . Accordingly, the upper bearing cover 236 is lubricated by the oil collected in the second oil supply grooves c and d and the groove, and is rotatably installed with respect to the fixed shaft 241 and the eccentric portion 242.

In addition, oil is introduced into the vane mounting holes 232H (shown in FIG. 11) to lubricate the vanes 233, and the lower bearing cover 238 is shown in the cylinder 232 as shown in FIGS. 10 and 14. Although coupled, the lower bearing cover 238 is installed so as not to cover all of the vane mounting holes 232H (shown in FIG. 11) of the cylinder 232, and the oil level is kept higher than the lower bearing cover 238. For example, in order to expose the vane mounting holes 232H (shown in FIG. 11) of the cylinder 232 from the lower bearing cover 238, the lower portion that abuts the vane mounting holes 232H (shown in FIG. 11) of the cylinder 232. The lower cover part 238b of the bearing cover 238 may be partially formed, or a separate hole may be formed. Therefore, the oil is introduced into the vane mounting hole 232H (shown in FIG. 11), and the oil is lubricated between the vane 233 and the vane mounting hole (232H: shown in FIG. 11), and the oil is introduced into the compression space. It is compressed and discharged together with the refrigerant.

However, the oil mixed in the compressed refrigerant is discharged from the discharge port of the upper bearing cover 236 and the discharge valve 236A, and then some oil is separated from the refrigerant while hitting the muffler 237, and the refrigerant in which the oil is partially separated is a muffler After being discharged from the discharge port 237h of 237, the oil is further separated from the refrigerant while hitting the oil separation plate 280. As such, the refrigerant from which the oil is separated passes through the holes 280h of the oil separation plate 280 to the outside through the discharge tube 214 (shown in FIG. 8) of the sealed container 210 (shown in FIG. 8). On the other hand, the oil is recovered to the lower portion of the sealed container 210 (shown in FIG. 8) while expanding in the radial direction while hitting the muffler 237 and the oil separator 280. At this time, the oil separated from the refrigerant by the muffler 237 is a series of jig mounting holes 232H, 236H to which the jig can be mounted to fasten the bolt (B) to the cylinder 232 and the upper and lower bearing covers (236,238). , 238H is quickly recovered, and the oil separated from the refrigerant by the oil separation plate 280 may be recovered through the gap H between the stator 220 and the rotor 231, which is a kind of oil recovery flow path. . Therefore, the oil mixed in the compressed refrigerant is separated by the muffler 237 and the oil separation plate 280, and is quickly sealed through the oil recovery passages H, 232H, 236H, and 238H provided between the parts. 210 is recovered to the lower portion, and is circulated again inside the compressor through the oil lubrication structure.

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 and 7 are side cross-sectional views showing the refrigerant flow structure and the oil circulation structure in the first embodiment of the compressor according to the present invention.

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

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

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

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

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

13 and 14 are side cross-sectional views showing a refrigerant flow structure and an oil circulation structure in a second embodiment of the compressor according to the present invention.

Claims (12)

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; A rotating member positioned inside the stator and capable of sucking and compressing a refrigerant into a compression space formed therein while rotating about a fixed shaft by mutual electromagnetic forces with the stator; A discharge port provided in the rotating member and discharging the compressed refrigerant from the compression space into the sealed container; And, And an oil separation plate separating the oil mixed in the refrigerant by its own weight while the refrigerant discharged from the discharge port collides with each other. The method of claim 1, The fixing member further includes an eccentric portion eccentric from the axial center of the fixed shaft, The rotating member is a rotor installed to rotate by mutual electromagnetic force with the stator, a cylinder which is stacked below the rotor, rotates with the rotor, and has a compression space therein, and a suction space where refrigerant is sucked into the compression space between the eccentric portion and the cylinder. And a vane elastically supported in the cylinder so as to partition the pocket and the compression pocket into which the refrigerant is compressed and discharged, 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. Compressor characterized in that the discharge port is provided in the upper bearing cover. The method of claim 2, The oil separator is fixed to any one of the inner peripheral surface of the stator or the upper surface of the rotor to form a predetermined space inside the rotor. The method of claim 1, The fixing member further includes an eccentric portion eccentric from the axial center of the fixed shaft, The rotary member is a compression space between the cylindrical rotor installed to rotate about the fixed shaft by mutual electromagnetic force with the stator and the cylindrical rotor while being rotated about the eccentric with the cylindrical rotor by receiving the rotational force of the cylindrical rotor. A vane integrally formed on the outer circumferential surface of the roller to form a roller, and to transmit the rotational force from the cylindrical rotor to the roller, and to divide the compression space into a suction pocket into which the refrigerant is sucked and a compression pocket into which the refrigerant is compressed and discharged; A top and bottom bearing cover which forms a top and a bottom of the space and rotates about the fixed shaft together with the rotating member, and a muffler coupled in the axial direction of the top bearing cover to communicate with the top bearing cover,  The discharge port is a compressor, characterized in that provided in the upper bearing cover and the muffler, respectively. The method of claim 4, wherein The oil separation plate is a compressor, characterized in that fixed to any one of the muffler, the upper bearing cover, the sealed container so as to be close to the discharge port of the muffler. 6. The method according to any one of claims 1 to 5, The oil separation plate is a compressor, characterized in that a plurality of holes are provided for passing through the refrigerant separated oil. The method according to claim 2 or 3, The cylinder and the upper and lower bearing covers are provided with jig mounting holes in which the assembling jig is axially mounted to bolt the upper and lower bearing covers to the cylinder, Compressor, characterized in that the oil separated by the oil separation plate is recovered to the bottom of the sealed container through the jig mounting opening. The method according to claim 4 or 5, The cylinder and the upper and lower bearing covers are provided with jig mounting holes in which the assembling jig is axially mounted to bolt the upper and lower bearing covers to the cylinder. Compressor, characterized in that the oil separated by the oil separation plate is recovered to the bottom of the sealed container through the jig mounting opening. 6. The method according to any one of claims 1 to 5, Compressor further comprises an oil recovery passage for guiding the oil separated by the oil separation plate to the lower container. 10. The method of claim 9, The oil return flow path is a compressor, characterized in that the gap between the stator and the rotating member. 10. The method of claim 9, The fixing member further includes an eccentric portion eccentric from the axial center of the fixed shaft, The rotating member is a rotor installed to rotate by mutual electromagnetic force with the stator, a cylinder which is stacked below the rotor, rotates with the rotor, and has a compression space therein, and a suction space where refrigerant is sucked into the compression space between the eccentric portion and the cylinder. And a vane elastically supported in the cylinder so as to partition the pocket and the compression pocket into which the refrigerant is compressed and discharged, 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 oil return passage is a jig mounting hole provided to communicate with the cylinder and the upper and lower bearing cover for mounting the assembly jig in the axial direction for bolting the upper and lower bearing cover to the cylinder. 10. The method of claim 9, The fixing member further includes an eccentric portion eccentric from the axial center of the fixed shaft, The rotary member is a compression space between the cylindrical rotor installed to rotate about the fixed shaft by mutual electromagnetic force with the stator and the cylindrical rotor while being rotated about the eccentric with the cylindrical rotor by receiving the rotational force of the cylindrical rotor. A vane integrally formed on the outer circumferential surface of the roller to form a roller, and to transmit the rotational force from the cylindrical rotor to the roller, and to divide the compression space into a suction pocket into which the refrigerant is sucked and a compression pocket into which the refrigerant is compressed and discharged; A top and bottom bearing cover which forms a top and a bottom of the space and rotates about the fixed shaft together with the rotating member, and a muffler coupled in the axial direction of the top bearing cover to communicate with the top bearing cover, The oil return passage is a jig mounting hole provided to communicate with the cylinder and the upper and lower bearing cover for mounting the assembly jig in the axial direction for bolting the upper and lower bearing cover to the cylinder.

Images