KR101105967B1 - Compact compressor - Google Patents

Abstract

The present invention relates to a compressor, and more particularly, to a compressor in which a compression space is formed inside a rotating member to achieve maximum efficiency.

The compact compressor of the present invention is a sealed container in which the refrigerant is sucked and discharged, a shaft member is fixed in the sealed container, a stator wound in a concentrated winding zone, an axis extending long into the sealed container, and an eccentric portion formed to be eccentric to the shaft, And a motor unit comprising a rotor rotating about an axis by a rotating electromagnetic field from the stator, a cylinder located inside the rotor and integrally rotating with the rotor, and having a compression space therein, and receiving the rotational force of the rotor together with the rotor. Rotating but rotating around the eccentric portion comprises a compression unit consisting of a roller to form a compression space between the rotor, characterized in that the height (L1) of the stator is higher than the height (L2) of the rotor.

Description

Compact Compressor {COMPACT COMPRESSOR}

The present invention relates to a compact compressor, and more particularly, to a compact compressor in which a compression space is formed inside the rotating member to achieve maximum efficiency.

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.

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.

However, in these conventional compressors, details of structural features of the motor mounted inside the compressor for maximizing the efficiency of the compressor are not described. That is, the compressor is formed inside the motor, the width of the stator and the rotor portion is narrowed to increase the magnetic saturation, the higher current is required to generate the same torque, which adversely affects the efficiency of the motor There is this.

An object of the present invention is to provide a compact compressor that optimizes the efficiency of the compression unit and the efficiency of the motor unit in a compressor in which a compression space is formed inside the rotating member.

It is also an object of the present invention to provide a compact compressor that achieves maximum efficiency at the same material cost.

It is also an object of the present invention to provide a compact compressor in which the magnetic characteristics are excellent in structural features of the compressor.

It is also an object of the present invention to provide a compact compressor which makes up for the loss of magnetic flux of a motor mounted inside a compressor, thereby improving characteristics such as torque and cogging torque.

The compact compressor of the present invention is a sealed container in which the refrigerant is sucked and discharged, a shaft member is fixed in the sealed container, a stator wound in a concentrated winding zone, an axis extending long into the sealed container, and an eccentric portion formed to be eccentric to the shaft, And a motor unit comprising a rotor rotating about an axis by a rotating electromagnetic field from the stator, a cylinder located inside the rotor and integrally rotating with the rotor, and having a compression space therein, and receiving the rotational force of the rotor together with the rotor. Rotating but rotating around the eccentric portion comprises a compression unit consisting of a roller to form a compression space between the rotor, characterized in that the height (L1) of the stator is higher than the height (L2) of the rotor.

Further, in the present invention, the height L1 of the stator and the height L2 of the rotor are characterized by having a relationship of 1.5 <L1 / L2 <1.9.

Further, in the present invention, the height (L2) of the rotor and the height (L3) of the cylinder is characterized by having a relationship of 0.90 <L2 / L3 <1.10.

Further, in the present invention, the first volume is defined as the volume of the stator, the second volume is defined as the volume of the first volume / compression space, and is characterized in that 35,000 <second volume <50,000.

In addition, in the present invention, the separation interval between the rotor and the stator is characterized in that it is changed periodically.

In the present invention, the outer circumferential surface of the rotor is characterized in that the first curved portion, and the second curved portion closer to the center of the rotor than the first curved portion is formed radially continuous.

In addition, in the present invention, the insertion space into which the permanent magnet is inserted into the rotor is formed to be spaced apart from each other by a connecting portion, and the connecting portion is formed closer to the second curved portion than the first curved portion.

Further, in the present invention, the region formed by the center of the first curved portion and the rotor is characterized in that the magnetic is greater than the region formed by the center of the second curved portion and the rotor.

In addition, in the present invention, the insertion space into which the permanent magnet is inserted into the rotor is formed to be spaced apart from each other, each insertion space is spaced apart from each other, a pair of permanent magnets are inserted and mounted, a pair of permanent magnets in the stator direction It is characterized by being mounted while forming an angle of less than 180 ° with each other.

In addition, in the present invention, the insertion space into which the permanent magnet is inserted into the rotor is formed to be spaced apart from each other, each insertion space is spaced apart from each other, a pair of permanent magnet is inserted and mounted, both ends of the insertion space of the rotor and the permanent magnet Characterized in that the gap is formed to space the gap.

Further, in the present invention, the void portion is characterized in that it comprises an extension space extending by a predetermined length to the central axis of the insertion space along the circumferential direction.

In the present invention, it is characterized in that the projection is formed between the extension space and the permanent magnet.

In addition, in the present invention, the stator is characterized by consisting of a straight tooth portion, the coil is wound, and the pole formed at the end of the tooth portion.

In addition, in the present invention, the stator is composed of a tooth portion to which the coil is wound, and the pole portion formed at the end of the tooth portion, and the surface of the pole portion facing the rotor comprises a curved portion and a pair of flat portions formed on both sides of the curved portion. It is done.

The present invention has the effect of improving the torque in the concentrated winding system in the compressor in which the compression space is formed inside the rotating member.

In addition, the present invention has the effect of optimizing the efficiency of the compression unit and the efficiency of the motor in the compressor in which the compression space is formed inside the rotating member.

In addition, the present invention has the effect of achieving maximum efficiency at the same material cost.

In addition, the present invention has the effect of achieving a maximum efficiency by keeping the magnetic saturation uniform.

In addition, the present invention has the effect of making the magnetic characteristics excellent in the structural characteristics of the compressor.

In addition, the present invention has the effect of recovering the magnetic flux loss of the motor mounted inside the compressor, thereby improving the characteristics of torque, cogging torque and the like.

Moreover, this invention has the effect of improving cogging torque by the shape of the pole part of a stator.

In addition, the present invention has the effect of improving the compression efficiency in the compression space formed inside the rotor by optimizing the arrangement angle of the permanent magnet, the number of slots, by adjusting the ratio between the magnetic region and the non-magnetic region.

In the following, the invention is described in detail by way of examples and 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 tube 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 becomes relatively large so that the core of the BLDC motor has twelve slots or 15 along the circumference. It is configured to have a slot. 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 or 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, and the vanes 134 according to the rotation of both vanes 134. ) Is a reciprocating linear motion between the bush (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.

6 is a perspective view showing an example of the vane integrated roller of the compressor according to the present invention.

The vane-integrated rollers 133 and 134 are formed of a cylindrical roller 133 and vanes 134 extending radially on the outer circumferential surface of the roller 133, as shown in FIG. It is manufactured by further machining. As described above, the inner diameter of the roller 133 is about the outer diameter of the eccentric portion 142 (shown in FIG. 2) so that the roller 133 is rotatably mounted to the circumferential surface of the eccentric portion 142 (shown in FIG. 2). The roller 133 and the eccentric portion 142 are formed to have a tolerance of about 20 to 30 μm, and the lubricating oil supply passage is provided on the outer circumferential surface of the eccentric portion 142 (shown in FIG. 2) or the inner circumferential surface of the roller 133. : Almost no loss due to sliding contact between the two parts is shown. Of course, since the roller 133 and the vane 134 are integrally formed, the vane is elastically supported by the cylinder in the conventional rotary compressor and the sliding loss can be eliminated as compared to the sliding contact with the roller. It is possible to prevent the refrigerant of the suction pocket S (shown in FIG. 4) and the compression pocket D (shown in FIG. 4) from mixing between the roller 133 and the vane 134.

7A to 7C are perspective views illustrating various embodiments of the cylindrical rotor of the compressor according to the present invention.

In the first embodiment of the cylindrical rotors 131 and 132, the rotor 131 and the cylinder 132 are separately configured to be made of different materials as shown in FIG. 7A, and the rotor 131 and the cylinder 132 are provided. The outer circumferential surface of the cylinder 132 is joined to the inner circumferential surface of the rotor 131 so that the rotation is possible integrally. The rotor 131 is formed such that iron pieces are stacked in the axial direction, and permanent magnets (not shown) are inserted into a plurality of holes formed to face the stator 120 (shown in FIG. 2) in such a stack. The cylinder 132 is formed to form a compression space between the roller 133 (shown in FIG. 2). In order for the rotor 131 and the cylinder 132 to be combined, a plurality of coupling grooves 131a are provided on the inner circumferential surface of the rotor 131, and the cylinder 132 to be combined with the coupling grooves 131a of the rotor 131. The outer circumferential surface of the) is provided with a plurality of protruding coupling protrusions (132a). Of course, the cylinder 132 is formed in a cylindrical shape with a constant thickness in the radial direction, the portion in which the coupling protrusions 132a are formed is formed in a thicker thickness in the radial direction. Therefore, the vane mounting holes 132H provided on the inner circumferential surface of the cylinder 132 are preferably formed at positions corresponding to one of the coupling protrusions 132a of the cylinder 132 to facilitate space utilization. On the other hand, since the rotor 131 and the cylinder 132 are configured separately, the upper bearing cover 136 and the muffler 137 are bolted to one of the rotor 131 and the cylinder 132, the lower bearing cover 138 Is bolted to the other one can be more stably fixed. Accordingly, the rotor 131 and the cylinder 132 have a circumference for fastening the upper bearing cover 136 (shown in FIG. 2) and the muffler 137 (shown in FIG. 2) and the lower bearing cover 138 (shown in FIG. 2). It is preferable that a plurality of bolt holes 131h and 132h are provided at predetermined intervals in the direction. Of course, since the rotor 131 and the cylinder 132 are configured to rotate separately, the upper bearing cover 136 (shown in FIG. 2), the muffler 137 (shown in FIG. 2), and the lower bearing cover 138 are both Only the cylinder 132 may be bolted.

In the first embodiment of the cylindrical rotor, the coupling grooves 131a of the rotor 131 are provided so as to be located in opposite directions to each other, and the coupling protrusions 132a of the cylinder 132 are similarly opposite to each other. Two are provided so as to be positioned, and vane mounting holes 132H are provided at positions corresponding to one of them. In addition, in order for the upper bearing cover 136 and the muffler 137 and the lower bearing cover 138 to be separately fastened to the rotor 131 and the cylinder 132, the rotor 131 and the cylinder 132 are respectively circumferentially directed. Four bolt holes 131h and 132h are provided at regular intervals.

The second embodiment of the cylindrical rotor is integrally formed by powder sintering as shown in FIG. 7B, and permanent magnets are inserted into a plurality of holes formed to face the stator 120 (shown in FIG. 2) in the powder sintered body. It is formed to be. Of course, the outer circumferential surface portion provided with permanent magnets may be viewed as a rotor portion, and the inner circumferential surface portion provided inside the rotor portion as a cylinder portion. In addition, the inner circumferential surface of the cylindrical rotor 231 is provided with a vane mounting hole 231H, and the cylindrical rotor 231 has an upper bearing cover 136 (shown in FIG. 2) and a muffler 137 (shown in FIG. 2); A plurality of bolt holes 231h are provided at regular intervals in the circumferential direction so that the lower bearing cover 138 (shown in FIG. 2) may be bolted. Of course, since the cylindrical rotor 231 is manufactured by powder sintering, holes, vane mounting holes 231H, and bolt holes 231h on which permanent magnets are mounted are manufactured to be formed during powder sintering.

In the third embodiment of the cylindrical rotor, as shown in FIG. 7C, the iron pieces are stacked in the axial direction, and in such a stack, permanent magnets are inserted into a plurality of holes formed to face the stator 120 (shown in FIG. 2). Is formed. Of course, the outer circumferential surface portion provided with permanent magnets may be viewed as a rotor portion, and the inner circumferential surface portion provided inside the rotor portion as a cylinder portion. In addition, the inner circumferential surface of the cylindrical rotor 331 is provided with a vane mounting hole 331H, and the cylindrical rotor 331 has an upper bearing cover 136 (shown in FIG. 2) and a muffler 137 (shown in FIG. 2); A plurality of bolt holes 331h are provided at regular intervals in the circumferential direction so that the lower bearing cover 138 (shown in FIG. 2) may be bolted. Of course, since the cylindrical rotor 331 is manufactured by lamination of iron pieces, holes, vane mounting holes 331H, and bolt holes 331h to which permanent magnets are mounted are provided in the respective iron pieces, and these iron pieces are axially oriented. As the stacks are stacked, a series of holes, vane mounting holes 331H, and bolt holes 331h penetrated in the axial direction are formed.

8a to 8c are partial cross-sectional views of a motor mounted on a compressor according to the invention. The motor consists of a stator 120 and a rotor 400 (or a cylindrical rotor). However, since the above-described cylinder and the like may be applied to the inside of the rotor 400, illustration is omitted.

The stator 120 is formed at a predetermined interval inside the base portion 120a and the base portion 120b, and is formed at the ends of the plurality of teeth portions 121 and the teeth portion 121 in which the coils are wound. It consists of a pole 122 (or polche) to fix the position of. The coil wound on the stator 120 is preferably wound in a concentrated winding method.

The stator 120 is composed of 12 slots, the teeth portion 121 has a straight shape, the winding is made in this straight portion. The outer circumferential surface 120c of the stator 120 is fixedly mounted to the inner surface of the sealed container 110, and a groove 120d is formed in the outer circumferential surface 120c to allow gas or oil to flow.

The rotor 400 may correspond to the above-described rotor, and as shown in FIGS. 8A to 8C, a coupling groove 400a into which a coupling protrusion (not shown) of a cylinder (not shown) may be inserted and fixed. The main body includes an outer circumferential surface 400b facing the stator 120 and the interval with the stator 120 is changed periodically, and an inner circumferential surface 400c in contact with the cylinder. The main body is provided with a plurality of insertion spaces 410 and bolt holes 431H formed to insert a pair of permanent magnets 480.

As shown in FIG. 8A, the coupling groove 400a is positioned correspondingly between the pair of permanent magnets 480 mounted to be spaced apart from each other, in order to equalize the magnetic flow in the rotor 400, or It is preferably formed so as to correspond to the middle of the insertion space (410).

As shown in FIG. 8B, the insertion space 410 is positioned at regular intervals between the straight line D2 and the outer diameter D1 of the rotor 400 from the center of the rotor 400. Made of poles.

In addition, the interval between the outer circumferential surface 400b of the rotor 400 and the inner circumferential surface (or the pole portion 122) of the stator 120 is periodically spaced apart by G1 and G2. That is, the outer peripheral surface 400b is formed closer to the inner peripheral surface of the stator 120 than the outer peripheral surface 400d. These intervals G1 and G2 correspond to different values from each other, and by this different separation interval, the cogging torque can be significantly reduced.

As shown in FIGS. 8B and 8C, a pair of permanent magnets 480 are inserted and mounted in the insertion space 410 spaced apart by a gap G, and for this mounting, the inner surface 410a of the insertion space is mounted on the insertion space 410a. A plurality of fixing protrusions 412 and 414 are formed. The outer side surface 410b of the insertion space 410 and the inner side surface 410a corresponding thereto are formed corresponding to the shape of the permanent magnet 480. The neighboring insertion spaces 410 are uniformly spaced apart by the thickness of the connection portion 430. An end portion of the insertion space 410 facing the connection portion 430 is formed with a constant space A1 (that is, a void portion) in which the permanent magnet 480 is not mounted, and the void portion A1 has an inner surface 410a. It consists of an extension portion 410c extending from, and a straight portion 416 connected to the curved portion 410c and extending to the outer surface 410b. A pair of neighboring extensions 410c corresponds to the side of the connection 430. The gap A1 is formed at both ends of the insertion space 410 to space the rotor 400 and the permanent magnet 480 at regular intervals.

In addition, the bolt holes 431H are formed between the pair of permanent magnets 480 inserted into the same insertion space 410, or correspond to the middle of the insertion space 410.

As shown in FIG. 8B, the angle θt of the pole portion 122 with respect to the center of the stator 120 (or the rotor 400) is a pair of permanent magnets inserted and mounted in the same insertion space 410. 480 is formed smaller than the angle θm formed with respect to the center of the stator 120 (or the rotor 400). In addition, the angle θe formed by the neighboring permanent magnets 480, which are respectively inserted into the other insertion space 410 with respect to the center of the stator 120 (or the rotor 400), corresponds to the nonmagnetic region as a whole. The angle θm corresponds to the magnetic region as a whole, and the angle θm is larger than the angle θe so that a strong magnetism is formed. In addition, the angle θ t is larger than the angle θ e so that the area of the pole portion 122 of the stator 120 corresponding to the nonmagnetic region is made small.

9A-9D are partial cross-sectional views of various embodiments of a motor applicable to a compressor according to the present invention.

The stator 220 included in the motor of FIG. 9A includes a curved tooth part 221 and a pole part 222 formed at an end of the tooth part 221, and the stator 320 included in the motor of FIG. 9B. Has a straight tooth portion 321 and a pole portion 322 formed at an end of the tooth portion 321.

9A to 9D, the pair of permanent magnets inserted into and mounted in the same insertion space are disposed such that angles formed with each other toward the stator form an angle of 180 ° or less. In particular, the angle θ3 of the permanent magnet 480 mounted in the insertion space 510 of FIG. 9A forms an angle smaller than the angle θ5 of the permanent magnet 480 of FIG. 9B. Accordingly, the angle θ4 of the permanent magnet 480 with respect to the center of the stator 220 is smaller than the angle θ6 of the permanent magnet 480 with respect to the center of the stator 320. That is, the magnetic region becomes wider than that of FIG. 9A in FIG. 9B, and the number of slots also increases. The motors of FIGS. 9A to 9D are shown in Table 1, and FIGS. 9C and 9D are examples applied to the same stator 220 of FIG. 9A. 9C and 9D, the same angle between the stator 320 and the permanent magnet as in FIG. 9B may be applied.

Figure 9a Figure 9c Figure 9d Figure 9b Poles 8 Number of slots 12 15 Outer diameter of stator 121.7 mm Outer diameter of rotor 86.0mm Stack length 30.0mm

In addition, the outer circumferential surfaces of the rotors 700 and 800 of FIGS. 9A and 9B have a circular shape, but FIGS. 9C and 9D have curved portions having different curvatures connected to each other in a radial shape.

The outer circumferential surface of the rotor 900 of FIG. 9C has a first curve portion 900a and a second curve portion 900b closer to the center of the rotor 900 than the first curve portion 900a are sequentially and continuously connected. In radial form. In particular, the second curved portion 900b has a pointed shape where two curved surfaces meet at its center. For example, the first curved portion 900a and the second curved portion 900b may have a form of 1 / cos.

In addition, the outer circumferential surface of the rotor 1000 of FIG. 9D has the first curved portion 1000a and the second curved portion 1000b closer to the center of the rotor 1000 than the first curved portion 1000a are sequentially and continuously. Connected radially. In particular, the second curved portion 1000b has a smooth curved shape.

The region including the first curved portions 900a and 1000a corresponds to the magnetic region, and the region including the second curved portions 900b and 1000b corresponds to the nonmagnetic region.

Table 2 shows the performance evaluation indices of FIGS. 9A to 9D.

Figure 9a Figure 9b Figure 9c Figure 9d Average torque (Nm) 1.75 1.73 1.77 1.74 Cogging Torque (Peak-Peak) (Nm) 0.55 5.9 × 10 ^-3 0.37 0.22 Pulse rate of torque (%) 42.2 2.29 28.7 18.0

Comparing the performance of Figs. 9A and 9B, the cogging torque is significantly reduced, and the pulsation rate of the torque is also significantly reduced. This performance difference is determined by the influence of the number of slots, the influence of the straight tooth portion, or the influence of the angle of the permanent magnets.

Comparing the performance of Figs. 9A, 9B, and 9C, it is confirmed that the cogging torque is significantly reduced according to the shape of the outer circumferential surface, and the pulsation rate is reduced. That is, the periodic gap change between the rotor and the stator affects.

Comparing the performance of Figures 9b and 9c, the cogging torque is reduced in the smooth curved form than the shape of the outer peripheral surface, the pulsation rate of the torque is also reduced.

Table 3 shows the performances of examples of applying the rotor of FIGS. 9C and 9D to the stator 320 of FIG. 9B.

Figure 9b Another example of the rotor of FIG. 9C Another example of the rotor of FIG. 9D Average torque (Nm) 1.73 1.72 1.70 Cogging Torque (Peak-Peak) (Nm)
5.9 × 10 ^-3 1.8 × 10 ^-3 8.3 × 10 ^-4 Pulse rate of torque (%) 2.29 1.17 0.59

As described in Table 3, it can be seen that other examples of FIG. 9C show better performance than those of FIG. 9B, and that other examples of FIG. 9D show better performance than other examples of FIG. 9C. That is, it is confirmed that the shape of the outer circumferential surface, the number of slots, or the angle formed by the straight tooth portion or the permanent magnets rise from each other in terms of performance.

10 is a schematic cross-sectional view of the rotor and the stator. FIG. 10 is a schematic cross-sectional view of the rotor 131 and the stator 120 in the compressor of FIG. 1. In the motor unit including the rotor 131 and the stator 120, in the compressor including a compression unit for compressing the refrigerant in the rotor 131 inner diameter of the motor unit, the structural design of the motor unit is not only the performance efficiency of the motor unit itself, It also has a dominant influence on the performance efficiency of the entire compressor.

It is preferable that the motor part of the compressor of the present invention has a multipole structure.

In addition, conventionally, the height of the rotor and the stator has a height of 1: 1 based on the core including the iron core.

In the motor unit according to the present invention, as shown in FIG. 10, the stator 120 includes a core portion and a coil 120a to the upper and lower end-turns (winding end or end winding). It has a height L1, which is a length, and the rotor 131 has a height L2. The end-turn, which is essentially provided in the manufacture of the stator 120, corresponds to a portion that does not contribute to the generation of torque of the motor part, and as the volume thereof is reduced, the material cost is reduced and copper loss is also reduced. Accordingly, the height L1 of the stator 120 is preferably configured to be at least larger than the height L2 of the rotor 131.

11 is a performance graph according to the ratio of the height L1 of the stator to the height L2 of the rotor. 11 shows that the lower the ratio of L1 / L2, the more the cost reduction effect is increased based on the same material cost, but the manufacturing efficiency becomes difficult, but the motor efficiency is increased. On the other hand, the higher the ratio of L1 / L2, the lower the motor performance efficiency, the lower the efficiency of the same material cost standard, but is easier to implement in manufacturing. Considering this point, it is preferable that the ratio of L1 / L2 corresponds to 1.5 <L1 / L2 <1.9.

12 is a performance graph according to the ratio of the height L2 of the rotor and the height L3 of the cylinder.

First, the volume of the stator 120 is defined as the first volume V1, and the second volume V2 is defined as the volume of the first volume V1 / cylinder 132. The volume of the cylinder 132 refers to the volume of the compression space, and means only the volume of the space into which the refrigerant is introduced and compressed.

In the present invention, in the case of 35,000 <second volume V2 <50,000, the matter of the ratio between the height L2 of the rotor 131 and the height L3 of the cylinder 132 is shown in FIG.

In the graph between the performance efficiency of the compressor and the ratio of L2 / L3, when L2 / L3 is 1.0 or substantially 1.0, it is confirmed that the performance efficiency of the compressor is the maximum. Accordingly, it is preferable to form the ratio L2 / L3 so that 0.90 <L2 / L3 <1.10 is maintained.

13 is another embodiment of a rotor. The rotor 1000 includes a pair of permanent magnets 480 spaced apart from each other in the insertion space 1110. Adjacent insertion spaces 1110 are positioned with the connecting portion 1130 interposed therebetween, and adjacent to the connecting portion 1130, a void portion A1 is formed, and the void portion A1 is an insertion space along the circumferential direction. An extension space A2 extending by a predetermined length is formed on the central axis of 1110. By this extension space A2, the torque per current is increased. In addition, the connection 1130 reduces the torque ripple of the motor. A protrusion 1111 is formed between the extension space A2 and the permanent magnet 480 to support the permanent magnet 480 and form a shape of the extension space A2.

The angle formed by the insertion space 1110 including the gap A1 of FIG. 13 with respect to the center of the rotor 1100 is the ends of the pair of permanent magnets 480 and the rotor 1100 in the same insertion space 1110. ) Is formed larger than the angle formed by the center.

14 is another embodiment of a stator. The stator 320a includes a straight tooth portion 321a and a pole portion 322a formed at an end of the tooth portion 321a. In particular, the pole portion 322a is composed of a curved portion Fr and a pair of flat portions Fp formed on both sides of the curved portion Fr at its center toward the rotor. With the shape of this pole 322a, the cogging torque of the motor is significantly improved. 14 may be applied to the other motors described above.

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.

6 is a perspective view showing an example of the vane integrated roller of the compressor according to the present invention.

7a to 7c are perspective views showing various embodiments of the cylindrical rotor of the compressor according to the present invention.

8a to 8c are partial cross-sectional views of a motor mounted to the compressor according to the invention.

9A-9D are partial cross-sectional views of various embodiments of a motor applicable to a compressor according to the present invention.

10 is a schematic cross-sectional view of the rotor and the stator.

11 is a performance graph according to the ratio of the height L1 of the stator to the height L2 of the rotor.

12 is a performance graph according to the ratio of the height L2 of the rotor and the height L3 of the cylinder.

13 is another embodiment of a rotor.

14 is another embodiment of a stator.

Claims (14)

An airtight container through which the refrigerant is sucked and discharged; A rotor fixed in a sealed container, the shaft member including a stator wound in a concentrated zone, an axis extending long into the sealed container, an eccentric portion formed to be eccentric to the shaft, and a rotor rotating about the axis by a rotating electromagnetic field from the stator. A motor unit consisting of; And It is located inside the rotor and rotates integrally with the rotor, the cylinder having a compression space therein, and the roller receives the rotational force of the rotor to rotate with the rotor while rotating around the eccentric to form a compression space between the rotor Including a compression unit, Compact compressor, characterized in that the height (L1) of the stator is higher than the height (L2) of the rotor. The height L1 of the stator and the height L2 of the rotor Compact compressor, characterized in that the relationship 1.5 <L1 / L2 <1.9. The height L2 of the rotor and the height L3 of the cylinder Compact compressor having a relationship of 0.90 <L2 / L3 <1.10. The method according to any one of claims 1 to 3, Wherein the first volume is defined as the volume of the stator, and the second volume is defined as the volume of the first volume / compression space, wherein 35,000 <second volume <50,000. The compact compressor according to any one of claims 1 to 3, wherein the separation interval between the rotor and the stator is changed periodically. 4. The compact type according to any one of claims 1 to 3, wherein the outer circumferential surface of the rotor has a first curved portion and a second curved portion closer to the center of the rotor than the first curved portion is formed radially and continuously. compressor. The compact compressor according to claim 6, wherein the insertion spaces into which the permanent magnet is inserted into the rotor are spaced apart from each other by the connecting portion, and the connecting portion is formed closer to the second curved portion than the first curved portion. . 8. The compact compressor according to claim 7, wherein the region formed by the center of the first curved portion and the rotor is larger than the region formed by the center of the second curved portion and the rotor. According to any one of claims 1 to 3, the insertion space into which the permanent magnet is inserted into the rotor is formed to be spaced apart from each other, and each insertion space is spaced from each other is a pair of permanent magnet is inserted and mounted, A pair of permanent magnets, characterized in that the compact compressor is mounted at an angle of less than 180 ° to each other in the stator direction. According to any one of claims 1 to 3, the insertion space into which the permanent magnet is inserted into the rotor is formed to be spaced apart from each other, and each insertion space is spaced apart from each other and a pair of permanent magnet is inserted and mounted, the insertion Compact compressors, characterized in that the gap portion is formed at both ends of the space separating the rotor and the permanent magnet. 11. The compact compressor as claimed in claim 10, wherein the air gap includes an extension space extending by a predetermined length along the circumferential direction of the insertion space. The compact compressor according to claim 11, wherein a protrusion is formed between the extension space and the permanent magnet. 6. The compact compressor according to claim 5, wherein the stator includes a straight tooth portion around which a coil is wound and a pole formed at an end of the tooth portion. 6. The stator includes a tooth portion around which a coil is wound, and a pole portion formed at an end of the tooth portion, and a surface of the pole portion facing the rotor comprises a curved portion and a pair of flat portions formed on both sides of the curved portion. Compact compressor.

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