KR20110015853A - Compressor - Google Patents

Abstract

PURPOSE: A compressor is provided to reduce lateral vibration due to eccentric rotation by preventing eccentric rotation. CONSTITUTION: The sealed container stores oil. The stator is fixed within the sealed container. The fixing member comprises a fixed axis(141) and an eccentric portion(142). The upper and lower ends of the fixed axis are fixed to the sealed container. The eccentric portion is eccentric to the fixed axis. The rotating member comprises a cylinder type rotor(131), a roller(133), and a vane. The rotor is supplied to the fixing member to be rotate. The roller forms the compression space with the rotor. The lower lubricating flow path supplies the oil stored in the sealed container between the eccentric portion and the roller.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor for compressing a refrigerant while rotating in a state in which a rotating member is suspended from a stationary member. In particular, the present invention relates not only to structural stabilization, but also to assemblability, and to improve lubrication performance to ensure operational reliability. It is about 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. 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 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, the present invention is not only to reduce the lateral vibration due to the eccentric rotation, but also to increase the efficiency, it is an object of the present invention to provide a compressor that is easy to manufacture and assembly.

It is also an object of the present invention to provide a compressor in which oil stored in a sealed container can be supplied to a lubrication flow path between a fixed member and a rotating member.

Compressor according to the present invention for solving the above problems is a sealed container in which oil is stored; A stator fixed in a sealed container; A fixing member including an eccentric portion formed so as to be eccentric to the fixed shaft, the fixed shaft having upper and lower ends installed so as not to move in the sealed container; The cylindrical rotor, which is rotatably supported by the fixed member to be rotated about the fixed shaft by the rotating electromagnetic field from the stator, receives the rotational force of the cylindrical rotor, and rotates about the eccentric with the cylindrical rotor while rotating with the cylindrical rotor. A rotating member comprising a roller for forming a compression space in the roller, and a vane for transmitting a rotational force from the cylindrical rotor to the roller and partitioning 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; And a lower lubrication flow path provided between the fixed shaft and the eccentric portion and the roller so that the oil stored in the sealed container is supplied between the eccentric portion and the roller.

Further, in the present invention, at least a part of the fixed shaft further comprises a refrigerant passage formed in the hollow shaft through which the refrigerant can flow, characterized in that the lower lubrication passage is configured to be isolated from the refrigerant passage.

In addition, in the present invention, the lower lubricating oil passage is an oil supply passage which is a hollow portion extending long to a predetermined height from the bottom of the fixed shaft to communicate with the oil stored in the sealed container, and penetrates in the radial direction of the eccentric portion so as to communicate with the oil supply passage. And a first oil supply groove formed between the outer circumferential surface of the eccentric portion and the inner circumferential surface of the roller so as to communicate with the first oil supply hole.

In addition, in the present invention, the first oil supply groove is characterized in that the groove portion of the ring shape provided on the outer peripheral surface of the eccentric portion.

In addition, in the present invention, the first oil supply hole is characterized in that located lower than the oil level filled in the sealed container.

Further, in the present invention, the rotating member, the upper and lower bearings to form the upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the holding member and to form a compression space between the cylindrical rotor and the roller. It further comprises a cover, characterized in that the groove is provided along the inner circumferential surface of the lower bearing cover to supply oil even when the inner circumferential surface of the lower bearing cover is in contact with the lower outer circumferential surface of the fixed shaft.

Further, in the present invention, the lower lubrication flow path is a second oil supply hole penetrated in the radial direction of the fixed shaft so as to communicate with the oil supply passage, and the eccentric portion bottom and the eccentric portion directly contacting the lower bearing cover so as to communicate with the second oil supply hole. It characterized in that it comprises a second oil storage groove formed on the outer peripheral surface of the fixed shaft.

Further, in the present invention, the vane is integrally formed on the roller so as to protrude toward the cylindrical rotor from the outer circumferential surface of the roller, and the vane fitting is formed on the cylindrical rotor to receive the protruding vane, and at least a part of the lowermost end of the vane fitting is It is characterized in that the open to communicate with the oil stored in the sealed container.

Further, in the present invention, the rotating member, the upper and lower bearings to form the upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the holding member and to form a compression space between the cylindrical rotor and the roller. It further comprises a cover, characterized in that the lower bearing cover has a step so that at least a portion of the lower end of the vane fitting is opened to communicate with the oil stored in the sealed container.

Further, in the present invention, the rotating member, the upper and lower bearings to form the upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the holding member and to form a compression space between the cylindrical rotor and the roller. And an upper lubrication passage provided between the fixed shaft, the eccentric portion, and the upper bearing cover to separate the compressed oil such as the refrigerant in the compression space and to be supplied between the eccentric portion and the upper bearing cover. do.

In addition, the present invention further comprises a refrigerant discharge passage provided on the upper bearing cover and the fixed shaft to discharge the refrigerant compressed in the compression space, the upper lubrication passage lower than the refrigerant discharge passage to separate the oil from the refrigerant Characterized in that located.

In addition, in the present invention, the upper lubrication passage is an oil separation hole penetrating the shaft portion of the upper bearing cover surrounding the fixed shaft upper portion, and an upper surface of the eccentric portion in contact with the upper bearing cover so as to communicate with the oil separation hole and a fixed shaft immediately above the eccentric portion. It characterized in that it comprises a third oil storage groove formed on the outer peripheral surface.

In addition, in the present invention, the third oil storage groove is characterized in that the groove portion formed in a ring shape on the upper peripheral surface of the fixed shaft, and the groove portion formed in a ring shape on the upper surface of the eccentric portion.

Compressor according to the present invention configured as described above is assembled to suspend the rotating member to the holding member, and then the upper and lower ends are fixed to the sealed container so that the fixed shaft of the fixing member does not move, so that the parts can be easily assembled to center the sealed container. There is an advantage that can increase the structural safety and assembly.

In addition, the compressor according to the present invention, even if the eccentric portion is eccentric from the axial center of the fixed shaft and protrudes in all the radial directions of the fixed shaft to remain stationary, while the cylindrical rotor rotates about the fixed shaft and the roller rotates about the eccentric portion Therefore, since the cylindrical rotor and the roller rotate about each axis, eccentric rotation does not occur. As a result, the balance weight is adopted to reduce the lateral vibration caused by the eccentric rotation and to reduce the vibration caused by the eccentric rotation. Since it can be omitted, the efficiency can be increased, and the actual production assembly is easy.

In addition, the compressor according to the present invention is lubricated between the fixed shaft and the lower bearing cover, the eccentric portion and the roller, the eccentric portion and the lower bearing cover while supplying the oil stored in the sealed container through the communication passage, and then the compression space with the refrigerant In order to lubricate between the fixed shaft and the upper bearing cover, the eccentric portion and the upper bearing cover while being compressed and discharged from the pump, it is possible to omit a member for pumping oil separately and to reduce the friction loss between the components, thereby reducing the compression efficiency. In addition to increasing the power consumption, there is an advantage to increase the operation reliability.

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

1 to 3 is a side cross-sectional perspective view, an exploded perspective view and a side cross-sectional view showing an example of a compressor according to the present invention.

One example of the compressor according to the present invention is a stator by the sealed container 110, the stator 120 fixed in the sealed container 110, and a rotating electromagnetic field from the stator 120 as shown in FIGS. (120) Rotating member 130 is rotatably installed in the inside and the rotating member 130 and the rotating member 130 is installed so as to hang on the outer circumferential surface at the same time the upper and lower ends of the fixed shaft 141 does not move in the sealed container (110). It includes a fixing member 140 fixed so as not to. 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 installing the transmission mechanism and the compression mechanism in 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. A predetermined position of the upper shell 112 is provided with a suction tube 115 through which the refrigerant can be sucked, and a fixed tube 141 is directly provided as an example of a discharge tube (not shown) through which the refrigerant is discharged at the center of the upper shell 112. Is provided so as to be exposed, it 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, the suction tube and the discharge tube may be changed accordingly. In the embodiment of the present invention is configured as a low pressure, the fixed shaft 141, which is a discharge 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 made of a core and a coil concentrated on the core, and is fixed to the inside of the body portion 111 of the hermetic container 110 by shrinking. 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 the cylindrical rotors 131 and 132, the roller 133, the vanes 134, the bush 135, the upper bearing cover 136 and the muffler 137, and the lower bearing cover 138. ) The cylindrical rotors 131 and 132 are provided with a plurality of permanent magnets in the axial direction so as to be rotated by the rotating electromagnetic field from the stator 120, and are located inside the rotor 131 to rotate integrally with the rotor 131. While it is made of a cylinder 132 having a compression space therein, the rotor 131 and the cylinder 132 may be separately configured and molded, but integrally formed in the form of a powder sintered body or a laminate in which iron pieces are laminated. May be The roller 133 is cylindrically mounted on the outer circumferential surface of the eccentric portion 142 of the fixing member 140 to be described below, and for this purpose, a lubrication structure is applied between the roller 133 and the eccentric portion 142. It is preferable. The vane 134 is integrally provided on the outer circumferential surface of the roller 133 so as to be radially expanded, and is installed to fit into the vane mounting holes 132H provided on the cylindrical rotors 131 and 132 or the inner circumferential surface of the cylinder 132. The bush 135 is installed to support both end surfaces of the vanes 134 fitted into the vane mounting holes 132H of the cylindrical rotors 131 and 132. Of course, a lubrication structure is applied to allow the vane 134 to move smoothly between the vane mounting holes 132H and the bush 135 of the cylindrical rotors 131 and 132.

The upper bearing cover 136 and the muffler 137 and the lower bearing cover 138 are coupled to the cylindrical rotors 131 and 132 in the axial direction, between the cylindrical rotors 131 and 132 and the rollers 133 and vanes 134. 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 140. The upper surface of the upper bearing cover 136 is formed so that the suction chamber 136a and the discharge chamber 136b are partitioned in the space between the muffler 137 and the suction chamber 136a is the upper bearing cover 136 and the muffler ( The discharge port 136b communicates with an intake port (137a) provided at each of the upper and lower bearing covers 136a, and the shaft portion protrudes upward from the center of the upper bearing cover 136. In communication with the discharge guide passage (not shown) provided in. Of course, the suction port and the discharge port provided in the upper bearing cover 137 may be provided with a suction valve or a discharge valve, the suction and discharge ports provided in the upper bearing cover 137 may be divided by vanes 134. It is preferable to be provided at both sides of 134. The upper bearing cover 136 and the muffler 137 are coupled to the upper surfaces of the cylindrical rotors 131 and 132, and the lower bearing cover 137 is coupled to the lower surfaces of the cylindrical rotors 131 and 132, and to the cylindrical rotors 131 and 132. It is fastened at the same time by a fastening member such as a kind of long bolt.

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. An oil supply passage 141A is formed below the fixed shaft 141 to supply oil stored in the airtight container 110, while a high pressure refrigerant is discharged to the upper portion of the fixed shaft 141. As the flow path 141B is formed, and the oil supply passage 141A and the refrigerant discharge passage 141B are formed to be isolated, oil can 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, because the upper and lower surfaces of the eccentric portion 142 abuts the upper and lower bearing cover (136,138) acting as a trust surface The upper and lower surfaces of the eccentric portion 142 is preferably provided with a lubricating oil supply passage, and the roller 133 is installed on the outer circumferential surface of the eccentric portion 142 so that the roller 133 can be rotatably contacted therein. It is preferable that a supply flow path of the lubricating oil extended to the outer circumferential surface is formed.

In addition, upper and lower bearings 150 and 160 are provided to fix the fixed shaft 141 to the sealed container 110. The upper bearing 150 is fixed to the upper shell 112 of the airtight container 110 by fitting the upper portion of the fixed shaft 141, and the lower bearing 160, the lower portion of the fixed shaft 141 After being fitted, it is fixed to the body portion 111 side of the sealed container 110 by shrinkage or three-point welding or the like. The upper bearing 150 is formed radially smaller than the lower bearing 160 to prevent interference with the suction pipe 115 or the terminal 116 provided in the upper shell 112. These upper and lower bearings 150 and 160 are manufactured by press working, but roller 133 and vanes 134, bush 135, upper and lower bearing covers 136 and 138, fixed shaft 141 and eccentric 142 ) Are all cast by cast iron and then manufactured by grinding and further machining.

4 is a plan view showing the vane mounting structure of the compressor according to the present invention, Figure 5 is a plan view showing the operation cycle of the compression mechanism in the compressor according to the present invention.

Looking at the mounting structure of the vane 134 with reference to Figure 4, the inner circumferential surface of the cylindrical rotor (131, 132) is formed in the radially long and is provided with a vane mounting hole 132H penetrated in the axial direction, the vane mounting hole ( After the pair of bushes 135 are inserted into the 132H, the vanes 134 integrally provided on the outer circumferential surface of the roller 133 are fitted between the bushes 135. In this case, a compression space is provided between the cylindrical rotors 131 and 132 and the roller 133, and the compression space is divided into the suction pocket S and the compression pocket D by the vanes 134. The suction port and the suction chamber 136a (shown in FIG. 2) of the upper bearing cover 136 (shown in FIG. 2) described above are located in communication with the suction pocket S, and the upper bearing cover 136 (shown in FIG. 2) The discharge port and the discharge chamber 136b (shown in FIG. 2) are positioned to communicate with the compression pocket D, but are preferably located close to the vane 134 to reduce the dead volume. As such, the vane 134 integrally manufactured with the roller 133 in the compressor of the present invention is assembled to be slidably movable between the bushes 135. 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 131 and 132 receive a rotational force by the rotating magnetic field with the stator 120 (shown in Fig. 1), the cylindrical rotors 131 and 132 rotate. While the vane 134 is fitted to the vane mounting holes 132H of the cylindrical rotors 131 and 132, the rotational force of the cylindrical rotors 131 and 132 is transmitted to the roller 133. 134 reciprocates linearly between bushes 135. That is, the inner circumferential surfaces of the cylindrical rotors 131 and 132 have portions corresponding to each other on the outer circumferential surfaces of the rollers 133. The portions corresponding to each other are each of the cylindrical rotors 131 and 132 and the roller 133 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.

Referring to the process of suction, compression, and discharge of the compression mechanism, as shown in FIG. 5, the cylindrical rotors 131, 132 and the roller 133 rotate to (a), (b), (c), and (d). This shows one cycle where the relative position changes. In more detail, when the cylindrical rotors 131 and 132 and the roller 133 are positioned at (a), the refrigerant or the working fluid is sucked into the suction pocket S, and the suction rotor S and the vane 134 are partitioned. Compression occurs in the compressed pocket D discharged. Even when the cylindrical rotor 131 and 132 and the roller 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. In this case, compression continues to occur in the compression pocket (D). When the cylindrical rotors 131 and 132 and the roller 133 reach (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 and the discharge valve of the upper bearing cover 136 (shown in FIG. 2). In (d), suction and discharge of the refrigerant or working fluid are almost finished.

1 to 5, the compressor configured as described above is rotated in a state in which the rotating member 130 is installed to hang on the fixing member 140, so that the rotating member 130 is suspended to the fixing member 140. That is, lubrication must be performed on the thrust face, and in addition to this, lubrication is required between the parts that abut each other among the rotating member 130 and the fixing member 140.

6 is a side cross-sectional view showing an example of the upper and lower lubricating oil of the compressor according to the present invention, Figure 7 is a perspective view showing an example of a fixed shaft lubrication structure of the compressor according to the present invention.

As shown in FIGS. 6 to 7, the lower lubrication channel has a lower bearing cover 138, a fixed shaft 141, and an eccentric portion 142 through a flow path through which oil stored in the sealed container 110 (shown in FIG. 1) is communicated. And the upper lubricating flow path, the upper bearing cover 136, the fixed shaft 141, and the eccentric part 142 through a flow path through which oil is discharged together with a high-pressure refrigerant. And to feed into portions abutting each other.

More specifically, the lower lubrication flow passage 141A is a hollow space extending vertically from the bottom of the fixed shaft 141 to the eccentric portion 142 and the eccentric portion 142 so as to communicate with the oil supply passage 141A. A first oil supply groove (a) formed between the outer circumferential surface of the eccentric portion 142 and the inner circumferential surface of the roller 133 to communicate with the first oil supply hole 142a penetrated in the radial direction of the first oil supply hole 142a. The second oil supply hole 141a penetrated in the radial direction below the fixed shaft 141 to communicate with the oil supply passage 141A, and the lower bearing cover 138 to communicate with the second oil supply hole 141a. ) And second oil supply grooves b and c formed on an outer circumferential surface of the fixed shaft 141 directly below the eccentric portion 142 and directly below the eccentric portion 142. At this time, the first oil supply groove (a) may be formed in any of the portions in contact with each other of the roller 133 and the eccentric portion 142, but the eccentric portion 142 that is relatively thick and easy to machine. It is preferable to be formed on the outer circumferential surface, and the second oil supply grooves b and c may also be formed in any of abutting portions of the lower bearing cover 138, the fixed shaft 141, and the eccentric portion 142. In addition, it is preferable that not only the thickness is thick but also formed in a ring-shaped groove having a side cross-section 'a' on the lower outer circumferential surface of the fixed shaft 141 and the bottom of the eccentric portion 142 that are easy to machine. In addition, a member capable of pumping oil may be employed, but even if there is no such oil pumping member, the oil level of the oil stored in the sealed container 110 may be supplied with the first oil so that the oil may be supplied along the lower lubrication passage. It is preferable to remain higher than the hole 142a. In addition, a helical groove (not shown) capable of supplying oil to the second oil supply grooves b and c may be provided on the inner circumferential surface of the lower bearing cover 138 surrounding the lower portion of the fixed shaft 141.

The upper lubricating flow path has an oil separation hole 136e penetrating through the shaft portion of the upper bearing cover 136 surrounding the upper part of the fixed shaft 141, and an eccentric part which is in contact with the upper bearing cover 136 so as to communicate with the oil separation hole 136e. (142) a third oil storage groove (d, e) formed on the outer circumferential surface of the fixed shaft 141 immediately above the upper surface and the eccentric portion (142). At this time, since the oil separation hole 136e is formed in the shaft portion of the upper bearing cover 136 by a drilling process, it cannot but be inclined toward the center, and the third oil supply grooves d and e may be formed in the upper bearing cover ( 136 and the fixed shaft 141 and the eccentric portion 142 may be formed anywhere in contact with each other, but the outer peripheral surface and the eccentric portion 142 upper peripheral surface 142 is relatively thick and easy to machine The upper surface is preferably formed of a ring-shaped groove having a side cross-section 'b'. In addition, the upper lubrication passage is preferably located lower than the refrigerant discharge passage 141B to separate the oil from the high pressure refrigerant. As such, the upper lubrication passage guides the high-pressure refrigerant containing oil to the discharge chamber 136b of the upper bearing cover 136 and the refrigerant discharge passage 142B of the fixed shaft 142. It may be.

Therefore, the oil stored in the lower portion of the sealed container 110 (shown in FIG. 1) is the first and second oil supply grooves a and b through the oil supply passage 141A and the first and second oil supply holes 142a and 141a. c) oil introduced into the first oil supply groove (a) lubricates between the roller 133 and the eccentric portion 142 to allow the roller 133 to rotate on the outer circumferential surface of the eccentric portion 142, and 2 The oil gathered in the oil supply grooves b and c lubricates between the lower bearing cover 138 and the fixed shaft 141 and the eccentric portion 142 so that the lower bearing contacts the fixed shaft 141 and the eccentric portion 142. The cover 138 is rotatable.

As such, since the oil level of the oil stored in the sealed container 110 is higher than the first oil supply hole 142a, the oil is compressed in the compression space together with the refrigerant, and then the upper bearing cover 136 Is discharged to the discharge port 136d and the discharge chamber 136b. When the high-pressure refrigerant containing oil flows into the third oil supply grooves d and e through the oil separation hole 136e, the oil is separated from the refrigerant and stays in the third oil supply grooves d and e. The refrigerant separated from the oil passes through the discharge guide passage 141b penetrated radially to the upper circumferential surface of the upper portion of the fixed shaft 141 and the refrigerant discharge passage 141B penetrated in the axial direction to the upper portion of the fixed shaft 141. Exit the sealed container 110 (shown in Figure 1). At this time, the oil collected in the third oil supply groove (d, e) is lubricated between the upper bearing cover 136 and the fixed shaft 141 and the eccentric portion 142 and the fixed shaft 141 and the eccentric portion 142 and The abutted upper bearing cover 136 is rotatable.

8 is a perspective view showing an example of the vane lubrication structure of the compressor according to the present invention.

The upper and lower bearing covers 136 and 138 are bolted to the rotor 131 (shown in FIG. 2) or the cylinder 132 in the axial direction as shown in FIG. 8. As described above, when the cylindrical rotor composed of the rotor 131 (shown in FIG. 2) and the cylinder 132 is adopted, the upper and lower bearing covers 136 and 138 are all bolted to the cylindrical rotor at the same time. When a cylindrical rotor consisting of the rotor 131 (shown in FIG. 2) and the cylinder 132 are employed separately, the upper and lower bearing covers 136, 138 are separately mounted to the rotor 131 (shown in FIG. 2) and the cylinder 132. Each bolt B may be fastened, or the bolt B may be fastened only to the cylinder 132. In the embodiment of the present invention, a cylindrical rotor in which the rotor 131 (shown in FIG. 2) and the cylinder 132 are separately applied, and the upper bearing cover 136 and the lower bearing cover 138 are respectively applied to the cylinder 132. Bolts are fastened. At this time, the lower bearing cover 138 is installed to cover the bottom surface of the cylinder 132, but the lower bearing cover 138 protrudes to the outer circumferential surface of the cylinder 132 in order to be combined with the rotor 131 (shown in Figure 2) It is preferable that the coupling protrusion 132a and the vane mounting holes 132H provided therein are not covered. For example, a portion of the lower bearing cover 138 corresponding to at least a portion of the vane mounting hole 132H may be configured to be stepped, deleted, or provided with an additional oil supply hole. Of course, the oil stored in the airtight container 110 (shown in FIG. 1) is maintained higher than the lower bearing cover 138 so that the lower end of the vane mounting hole 132H can be locked. Thus, when oil flows into the vane mounting holes 132H of the cylinder 132 not covered by the lower bearing cover 138, the vanes 134 smoothly between the vane mounting holes 132H and the bushes 135. Make a reciprocating linear motion at.

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 cross-sectional perspective view showing an example of a compressor according to the present invention.

2 is an exploded perspective view showing an example of a compressor according to the present invention.

Figure 3 is a side sectional view showing an example of a compressor according to the present invention.

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

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

Figure 6 is a side cross-sectional view showing an example of the upper and lower lubricating oil of the compressor according to the present invention.

7 is a perspective view showing an example of a fixed shaft lubrication structure of the compressor according to the present invention.

8 is a perspective view showing an example of the vane lubrication structure of the compressor according to the present invention.

<Explanation of symbols on main parts of the drawings>

110: sealed container 120: stator

130: rotating member 131: rotor

132: cylinder 133: roller

134: vane 135: bush

136: upper bearing cover 137: muffler

138: lower bearing cover 140: fixing member

141: fixed shaft 142: eccentric portion

Claims (13)

A sealed container in which oil is stored; A stator fixed in a sealed container; A fixing member including an eccentric portion formed so as to be eccentric to the fixed shaft, the fixed shaft having upper and lower ends installed so as not to move in the sealed container; The cylindrical rotor, which is rotatably supported by the fixed member to be rotated about the fixed shaft by the rotating electromagnetic field from the stator, receives the rotational force of the cylindrical rotor, and rotates about the eccentric with the cylindrical rotor while being rotated about the cylindrical rotor. A roller for forming a compression space, the rotating member comprising a vane for transmitting rotational force from the cylindrical rotor to the roller and partitioning 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; And, And a lower lubrication flow path provided between the fixed shaft, the eccentric portion, and the roller so that the oil stored in the sealed container is supplied between the eccentric portion and the roller. The method of claim 1, At least a part of the fixed shaft further includes a refrigerant passage formed in the hollow shaft through which the refrigerant can flow, The lower lubrication passage is configured to be isolated from the refrigerant passage. The method of claim 2, The lower lubricating oil passage is an oil supply passage, which is a hollow portion extending from the bottom of the fixed shaft to a predetermined height to communicate with the oil stored in the sealed container, and a first oil supply hole penetrated in the radial direction of the eccentric portion so as to communicate with the oil supply passage. And a first oil supply groove formed between the eccentric outer peripheral surface and the roller inner peripheral surface to communicate with the first oil supply hole. The method of claim 3, Compressor characterized in that the first oil supply groove is a ring-shaped groove provided on the outer peripheral surface of the eccentric portion. The method of claim 3, Compressor characterized in that the first oil supply hole is located lower than the oil level filled in the sealed container. 6. The method according to any one of claims 1 to 5, The rotating member further includes upper and lower bearing covers forming upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the fixed member and to form a compression space between the cylindrical rotor and the rollers, And a groove is provided along the inner circumferential surface of the lower bearing cover to supply oil even when the inner circumferential surface of the lower bearing cover contacts the lower outer circumferential surface of the fixed shaft. The method of claim 6, The lower lubricating oil passage has a second oil supply hole penetrated in the radial direction of the fixed shaft so as to communicate with the oil supply passage, and a bottom surface of the eccentric portion which is in contact with the lower bearing cover so as to communicate with the second oil supply hole, and a fixed shaft outer surface just below the eccentric portion. And a second oil storage groove formed. 6. The method according to any one of claims 1 to 5, The vane is integrally formed on the roller to protrude from the outer circumferential surface of the roller toward the cylindrical rotor, and the vane mounting hole is formed on the cylindrical rotor to receive the protruding vane. At least a portion of the lowermost end of the vane fitting is opened to communicate with the oil stored in the hermetic container. The method of claim 8, The rotating member further includes upper and lower bearing covers forming upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the fixed member and to form a compression space between the cylindrical rotor and the rollers, And the lower bearing cover has a step so that at least a portion of the lower end of the vane fitting is opened to communicate with the oil stored in the hermetic container. 6. The method according to any one of claims 1 to 5, The rotating member further includes upper and lower bearing covers forming upper and lower portions of the cylindrical rotor to rotatably support the cylindrical rotor to the fixed member and to form a compression space between the cylindrical rotor and the rollers, And an upper lubrication passage provided between the fixed shaft and the eccentric portion and the upper bearing cover to separate the compressed oil such as the refrigerant in the compression space and to be supplied between the eccentric portion and the upper bearing cover. The method of claim 10, Further comprising a refrigerant discharge passage provided in the upper bearing cover and the fixed shaft to discharge the compressed refrigerant in the compression space, And the upper lubrication passage is located lower than the refrigerant discharge passage to separate oil from the refrigerant. The method of claim 11, The upper lubrication flow path is an oil separation hole penetrating the shaft portion of the upper bearing cover surrounding the upper part of the fixed shaft, and a third oil formed on the upper surface of the eccentric portion in contact with the upper bearing cover and the outer peripheral surface of the fixed shaft just above the eccentric portion so as to communicate with the oil separation hole. Compressor comprising a storage groove. The method of claim 12, The third oil storage groove is a compressor, characterized in that the groove portion formed in a ring shape on the upper outer peripheral surface of the fixed shaft, and the groove portion formed in a ring shape on the upper surface of the eccentric portion.

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