KR20220011542A - Rotary compressor - Google Patents

Abstract

A rotary compressor according to an embodiment comprises: an electric unit provided to be spaced apart from the inner circumferential surface of a shell; a rotary shaft which rotates while being coupled to the electric unit; a cylinder which is provided on an upper side of the electric unit to be spaced apart from the inner circumferential surface of the shell, and which is formed in an annular shape; a roller coupled to the rotary shaft and provided in the cylinder; a vane which is provided between the cylinder and the roller and forms a compression chamber in the cylinder; a support which elastically supports the electric unit onto the shell; a suction muffler having an inlet communicating with the inner space of the shell and an outlet communicating with a suction side of the compression chamber; and a discharge muffler having an inlet communicating with a discharge side of the compression chamber and an outlet communicating with a refrigerant discharge pipe which penetrates through the shell. Therefore, the rotary compressor of a low-pressure type, an upper compression type, and a spring-support type can be provided.

Description

Rotary Compressor

The present invention relates to a rotary compressor.

A compressor is a device that compresses a refrigerant by transferring the power generated from the electric part to the compression part. The electric part and the compression part may be installed inside the same shell or may be installed in different shells and connected using a separate power transmission mechanism. The former is called a hermetic compressor, and the latter is called an open compressor.

The hermetic compressor is divided into a low-pressure compressor and a high-pressure compressor according to the refrigerant filled in the inner space of the shell. The low-pressure compressor is a method in which the low-temperature and low-pressure refrigerant circulated in the refrigeration cycle is filled in the inner space of the shell, and in the high-pressure compressor, the high-temperature and high-pressure refrigerant discharged from the compression unit is filled in the inner space of the shell.

The low-pressure compressor cools the motor constituting the electric part as the inner space of the shell is filled with a low-temperature refrigerant, so that the motor efficiency can be improved. On the other hand, in the high-pressure compressor, the refrigerant discharged from the compression unit circulates in the inner space of the shell, so that the oil separation effect can be improved.

In addition, the hermetic compressor may be divided into a spring support method and a shell support method according to a method of supporting the compressor body including the electric part and the compression part. In the former case, as the compressor body is supported by the spring, the vibration of the compressor body is attenuated by the spring, so that the shell vibration is low, whereas in the latter, the vibration of the compressor body is low as the compressor body is fixed to the shell.

Patent Document 1 (Japanese Patent Laid-Open No. 2004-232524) discloses a hermetic compressor of a low pressure type and a shell support type. Patent Document 1 has a double shell structure, and the compressor body is fixed to the inner shell by a shell support method, and the inner shell is supported by the outer shell by a spring support method. The inner space of the inner shell is filled with the discharged refrigerant and is in a high pressure state, and this refrigerant is directly discharged without passing through the inner space of the outer shell. Accordingly, the inner space of the outer shell is maintained in a low pressure state.

In Patent Document 1 as described above, the inner shell surrounding the electric part is cooled by the refrigerant filled in the inner space of the outer shell, so that the motor efficiency can be improved. In addition, since the inner shell to which the compressor body is fixed is supported by a spring on the outer shell, the vibration of the compressor body can be improved to some extent and the shell vibration can be lowered at the same time.

However, in the conventional hermetic compressor as described above, the volume and weight of the compressor may increase, and the number of parts may increase, thereby increasing the manufacturing cost.

In addition, the conventional hermetic compressor has a limitation in attenuating compressor noise in a low frequency band because a device for attenuating noise generated during suction is not separately installed while being of a low pressure type.

In addition, in the conventional hermetic compressor, the size of the compressor may be enlarged when the suction muffler is installed in the inner space of the shell because the gap between the shell and the compressor body is narrow.

In addition, when the conventional hermetic compressor is formed in the upper compression method, it is difficult to recover oil, so it is difficult to provide an oil supply structure.

In addition, the conventional hermetic compressor has a so-called lower compression type and low pressure structure in which the compression part is located below the transmission part, so there is not enough space to install the roof pipe for a long time, and the roof pipe is submerged in oil and the temperature of the oil rises. As the oil viscosity decreases, friction loss in the compressor body may occur.

In addition, in the conventional hermetic compressor, as the inner space of the shell forms the low pressure portion, there is a fear that the refrigerant may leak from the compression chamber constituting the high pressure portion to the inner space of the shell. In particular, in the case of a rotary compressor, since the main bearing plate and the sub-bearing plate are combined on both sides of the cylinder, the refrigerant in the compression chamber leaks into the inner space of the shell due to a machining error or assembly error between the cylinder and both bearing plates and is compressed. losses could have occurred.

Japanese Patent Application Laid-Open No. 2004-232524 (published date: August 19, 2004)

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary compressor having a spring support structure that elastically supports the compressor body with respect to the shell while being of a low pressure type.

Furthermore, it is another object of the present invention to provide a rotary compressor capable of securing an installation space for a suction muffler to effectively attenuate suction noise of refrigerant sucked through the inner space of the shell.

Furthermore, another object of the present invention is to provide a rotary compressor in which a suction muffler can be stably installed in the inner space of the shell in the case of a low pressure type, a spring supported type, and an upper compression type.

Furthermore, it is another object of the present invention to provide a rotary compressor of a low pressure type and a spring support type, which can prevent the discharge flow path from being submerged in oil in advance, thereby suppressing the oil from being heated by the discharge gas.

Furthermore, it is another object of the present invention to provide a rotary compressor of a low pressure type, a spring support type, and an upper compression type in which the compression unit is located above the transmission unit, while allowing oil to be smoothly supplied to the compression unit.

Furthermore, it is another object of the present invention to provide a low-pressure rotary compressor capable of suppressing leakage of refrigerant between a cylinder and both bearing plates constituting a compression part.

The shell is formed in one layer to form an appearance; a compressor body provided spaced apart from the inner circumferential surface of the shell, comprising a transmission unit and a compression unit positioned above the transmission unit, and the compression unit formed in a rotary compression method; and a support part for elastically supporting the compressor body on the shell; a rotary compressor including a can be provided. Through this, the compressor body having the rotary compression unit can be supported in a spring-supported manner with respect to the single-shell shell.

In addition, in order to achieve the object of the present invention, the shell; It is provided spaced apart from the inner circumferential surface of the shell, and includes a transmission unit and a compression unit positioned above the transmission unit, the compression unit comprising: a compressor body made of a rotary compression method; a suction muffler having an inlet communicating with the inner space of the shell and having an outlet connected to a suction port of the compression unit; and a discharge muffler having an inlet connected to a discharge port of the compression unit, an outlet connected to a refrigerant discharge pipe passing through the shell, and a discharge muffler installed at an upper end of the compressor body. Through this, the rotary type compressor body can achieve a low pressure type and an upper compression type.

In addition, in order to achieve the object of the present invention, the shell is formed in one layer to form an appearance; a compressor body provided spaced apart from the inner circumferential surface of the shell, comprising a transmission unit and a compression unit positioned above the transmission unit, and the compression unit formed in a rotary compression method; a support part for elastically supporting the compressor body to the shell; a suction muffler having an inlet communicating with the inner space of the shell and having an outlet connected to a suction port of the compression unit; and a discharge muffler having an inlet connected to a discharge port of the compression unit, and an outlet connected to a refrigerant discharge pipe passing through the shell. Through this, the compressor body having the rotary compression unit is supported with respect to the shell in a spring-supported manner, and a low pressure type in which the inner space of the shell is filled with suction refrigerant can be achieved.

Here, the suction muffler may be installed to be located on the side of the compressor body. Through this, it is possible to reduce the size of the compressor while installing the suction muffler in the inner space of the shell.

In addition, the compression part may include an annular cylinder, a muffler mounting groove is formed on an outer circumferential surface of the cylinder, and an outlet of the suction muffler may be inserted into the muffler mounting groove to be supported in the circumferential direction. Through this, the suction muffler can be installed stably.

In addition, a boss portion extending to be inserted into a suction port provided in the cylinder or a support protrusion supported on an outer surface of the cylinder may be formed at the outlet portion of the suction muffler. Through this, it is possible to easily assemble the suction muffler by maintaining the alignment state of the suction muffler when assembling the suction muffler.

In addition, in order to achieve the object of the present invention, the shell forming the appearance; an electric part provided to be spaced apart from the inner circumferential surface of the shell; a rotating shaft coupled to the electric motor to rotate; a cylinder spaced apart from the inner circumferential surface of the shell and provided on the upper side of the electric part, the cylinder being formed in an annular shape; a roller coupled to the rotation shaft and provided inside the cylinder; a vane provided between the cylinder and the roller to form a compression chamber inside the cylinder; a support part for elastically supporting the electric part on the shell; and a suction muffler having an inlet communicating with the inner space of the shell and an outlet communicating with a suction side of the compression chamber; and a discharge muffler having an inlet connected to a discharge side of the compression chamber and an outlet communicating with a refrigerant discharge pipe passing through the shell. Through this, the compressor body having the upper compression type compression unit is supported with respect to the shell in a spring support method, and a low pressure type in which the inner space of the shell is filled with suction refrigerant can be achieved.

Here, the main bearing plate provided on the upper side of the electric part; and a sub-bearing plate coupled to the cylinder from an upper side of the main bearing plate with the cylinder interposed therebetween, wherein the suction muffler is located below the sub-bearing plate, the outer peripheral surface of the electric part and the It may be provided between the inner peripheral surfaces of the facing shell. Through this, it is possible to maintain the size of the compressor while installing the suction muffler in the inner space of the cell.

In addition, a radially penetrating suction port is formed in the cylinder, and a muffler mounting groove is formed on the outer peripheral surface of the cylinder to be radially depressed to communicate with the suction port, and the outlet of the suction muffler is inserted into the muffler mounting groove can be combined. Through this, it is possible to stably fix the suction muffler while maintaining the size of the compressor.

In addition, a muffler fixing part fixed to the cylinder may extend from the outlet part of the suction muffler. Through this, the suction muffler can be easily aligned and can be stably fixed.

In addition, the muffler fixing part may extend from both side surfaces of the outlet part of the suction muffler to correspond to the outer peripheral surface of the cylinder. Through this, the suction muffler can be stably fixed from both sides.

Here, the muffler fixing part may extend from the upper surface of the outlet part of the suction muffler to correspond to the upper surface of the cylinder. Through this, the suction muffler can also be supported in the axial direction.

Here, the suction muffler may be fixed to the cylinder by a muffler fixing member that surrounds the outlet of the suction muffler and is fastened to the cylinder. Through this, the structure of the suction muffler can be simplified while firmly fixing the suction muffler.

In addition, a muffler support protrusion supported in an axial direction on an upper circumferential surface of the muffler mounting groove may extend from the outlet of the suction muffler. Through this, it is possible to support the suction muffler in the axial direction while using the muffler fixing member.

In addition, the muffler fixing member may support the outlet of the suction muffler in the axial direction from the lower side of the muffler support protrusion. Through this, it is possible to more stably support the suction muffler while using the muffler fixing member.

Here, in the muffler mounting groove, the radial outer surface is opened, both circumferential side surfaces and the radial inner surface are closed to form a first muffler support surface and a second muffler support surface, and the suction port is the muffler mounting groove A second muffler support surface constituting a radially inner surface of may be radially penetrated. Through this, the suction muffler can be supported in the circumferential direction.

In addition, at the outlet of the suction muffler, an outlet extension inserted into the suction port may extend toward the suction port. Through this, it is possible to facilitate the assembly of the suction muffler and effectively suppress refrigerant leakage or oil inflow.

A muffler sealing member may be provided between the outlet of the suction muffler and the second muffler support surface facing the same. Through this, it is possible to suppress oil from flowing into the suction port.

Here, the suction muffler may include: a suction muffler body having a suction space therein; a suction muffler inlet for connecting the suction space of the suction muffler body to the inner space of the shell; a suction muffler outlet portion coupled to the cylinder to connect the suction space of the suction muffler body to the compression chamber; and a suction muffler connection part connecting between the suction muffler body part and the suction muffler outlet part, wherein the suction muffler connection part may be inclined toward the cylinder. Through this, it is possible to suppress an increase in the size of the compressor body and at the same time lower the flow resistance of the sucked refrigerant.

Here, the cylinder may be provided with a vane slot into which the vane is slidably inserted, and an oil passage hole communicating with the vane slot may be formed in the sub-bearing plate. Through this, the oil can be smoothly supplied to the sliding part while the rotary compression type compression part is located above the electric part.

A discharge port is formed in the sub-bearing plate, and a discharge muffler having a discharge space to accommodate the discharge port is provided on the upper surface of the sub-bearing plate, and the upper surface of the discharge muffler collects oil discharged through the rotation shaft An oil guide may be provided to guide the oil passage hole.

Here, one end of the vane may be rotatably hinged to the outer peripheral surface of the roller.

The compressor according to this embodiment, by elastically supporting the rotary type compressor body on the shell forming the exterior, blocks the vibration transmitted from the compressor body from being transmitted to the shell, thereby reducing the vibration noise of the compressor, and through this, the rotary compressor The volume and weight of the product can be reduced, and the number of parts can be reduced, thereby lowering the manufacturing cost.

In addition, the rotary compressor according to this embodiment is a spring supported type, an upper compression type, and a low pressure type, so that the electric part is rapidly cooled by the cold refrigerant sucked into the inner space of the shell, thereby improving motor efficiency and compressor performance. can be

In addition, by configuring the rotary compressor, which is a spring-supported method, in an upper compression method in which the compression part is located on the upper side of the electric part, a space for installing the suction muffler is secured to effectively offset the suction noise generated when the refrigerant is sucked. have. Through this, the electric part is rapidly cooled by the cold refrigerant sucked into the inner space of the shell, so that the motor efficiency and compressor performance can be improved.

In addition, by forming a muffler mounting groove in the cylinder and inserting and coupling the suction muffler, the suction muffler can be stably fixed in the circumferential direction while configuring the compressor body including the suction muffler in a spring-supported manner.

In addition, by extending the muffler fixing part to the suction muffler or fixing the suction muffler to the cylinder using a separate muffler fixing member, the stress of the muffler fixing part or the muffler fixing member fixing the suction muffler is reduced and the suction muffler is further improved. It can be fixed stably.

In addition, as the outlet extension extending from the outlet of the suction muffler is inserted into the suction port, the assembling position of the suction muffler can be easily aligned when assembling the suction muffler, thereby facilitating the assembly operation of the suction muffler.

In addition, since the sealing member is provided between the outlet and the suction port of the suction muffler, it is possible to suppress the oil inside the shell from flowing into the suction port, thereby reducing suction loss and increasing the compression efficiency.

In addition, the rotary compressor according to the present embodiment may be installed so that the loop pipe constituting the discharge flow path is separated without being submerged in the oil filled in the inner space of the shell by configuring it as a spring support method and an upper compression method. Through this, it is possible to prevent the oil inside the shell from being heated by the high-temperature refrigerant discharged through the roof pipe in advance, thereby suppressing the decrease in the viscosity of the oil, thereby reducing the friction loss on each bearing surface of the compressor body. .

In addition, it is possible to smoothly supply the oil stored in the shell to the compression unit by using the oil guide and the oil passage while configuring the rotary compressor of the spring-supported and upper compression type. Through this, oil is smoothly supplied to the bearing surfaces of the compressor body, and frictional losses due to insufficient oil on each bearing surface can be reduced.

1 is an exploded perspective view showing the compressor body of the rotary compressor according to the present embodiment;
2 is a perspective view showing the compressor body assembled in FIG. 1;
3 is a cross-sectional view showing the inside of the rotary compressor according to FIG. 2;
4 is a plan view showing the inside of the compression unit in FIG. 1;
5 is a perspective view showing the compressor body in FIG. 1;
6 is an exploded perspective view showing the compressor body by removing the suction muffler in FIG. 5;
7 is a perspective view showing an embodiment of the suction muffler in FIG. 1;
8 is a perspective view showing a state in which the suction muffler according to FIG. 7 is assembled;
9 is a sectional view of "IV-IV" in FIG. 8;
10 is a perspective view showing another embodiment of the suction muffler outlet in the suction muffler of FIG. 6;
11 is a cross-sectional view showing a state in which the suction muffler of FIG. 10 is assembled;
12 is an exploded perspective view showing another embodiment of the suction muffler in FIG. 1;
13 is a perspective view showing a state in which the suction muffler of FIG. 12 is assembled;
14 is an exploded perspective view showing another embodiment of the suction muffler in FIG. 1;
Fig. 15 is a perspective view showing the state in which the suction muffler of Fig. 14 is assembled;

Hereinafter, a hermetic compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. In the present specification, the same or similar reference numbers are assigned to the same and similar components even in different embodiments, and the description is replaced with the first description.

Hereinafter, a rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. In the present specification, the same or similar reference numerals are assigned to the same and similar components even in different embodiments, and the description is replaced with the first description.

In addition, the rotary compressor may be divided into a contact rotary compressor and a hinged vane rotary compressor depending on whether rollers and vanes are coupled. The contact rotary compressor is a method in which the vanes are in sliding contact with the rollers, and the hinged vane rotary compressor is a method in which the vanes are hinged to the rollers.

In addition, the rotary compressor may be divided into a rotary compressor and a vane rotary compressor according to the support position of the vane. A rotary compressor is a conventional structure in which a vane is slidably inserted into a cylinder and supported, and a vane rotary compressor is a method in which a vane is slidably inserted into a roller.

In addition, the rotary compressor may be divided into an eccentric rotary compressor and a concentric rotary compressor according to the presence or absence of eccentricity of the rollers. The eccentric rotary compressor is a method in which a roller is coupled to an eccentric portion of a rotating shaft, and a concentric rotary compressor is a method in which a roller is formed coaxially of a rotating shaft.

Although this embodiment describes a rotary compressor to which the hinge vane method is applied, the present invention is not limited thereto, and all known rotary compressors may be applied. However, hereinafter, a hinge vane type rotary compressor will be described as a representative example. Accordingly, unless otherwise specified in the description below, the rotary compressor may be understood as abbreviated as a hinge vane rotary compressor.

1 is an exploded perspective view showing the compressor body of the rotary compressor according to this embodiment, FIG. 2 is a perspective view showing the compressor body assembled in FIG. 1, and FIG. 3 is a cross-sectional view showing the inside of the rotary compressor according to FIG. , FIG. 4 is a plan view showing the compression unit in FIG. 3 , and FIG. 4 is a plan view illustrating the inside of the compression unit in FIG. 1 .

1 to 4 , the rotary compressor according to the present embodiment includes a shell 110 forming an external appearance, a compressor body C provided in an inner space 110a of the shell 110, and a compressor body C ) to the shell 110, the support 150, the suction/discharge unit 160 for guiding the refrigerant to the compressor body (C) and discharging the compressed refrigerant, and the oil contained in the oil reservoir of the shell 110 to the compressor body (C) includes a refueling unit 170 for supplying. The compressor body (C) transmits the driving force from the electric part 120 providing the driving force, the rotating shaft 130 and the electric part 120 coupled in the electric part 120 to transmit the rotational force to the compression part 140 to be described later. and a compression unit 140 for receiving and compressing the refrigerant.

The shell 110 has the inner space 110a sealed, so that the compressor body C, the support part 150, the suction/discharge part 160 and the oil supply part 170 are accommodated. The shell 110 is made of an aluminum alloy (hereinafter, abbreviated as aluminum) which is light and has a high thermal conductivity, and includes a base shell 111 and a cover shell 112 .

The base shell 111 is formed in a substantially hemispherical shape. A suction pipe 115 , a discharge pipe 116 , and a process pipe 117 are respectively penetrated and coupled to the base shell 111 . The suction pipe 115 , the discharge pipe 116 , and the process pipe 117 may be coupled to the base shell 111 by an insert die casting method, respectively.

The cover shell 112 is formed in a substantially hemispherical shape like the base shell 111 . The cover shell 112 is coupled to the base shell 111 from the upper side of the base shell 111 to form the inner space 110a of the shell 110 .

In addition, the cover shell 112 may be coupled to the base shell 111 by welding, but when the base shell 111 and the cover shell 112 are formed of an aluminum material that is difficult to weld, they may be bolted together.

Next, the electric part will be described.

The electric part 120 according to the present embodiment includes a stator 121 and a rotor 122 .

The stator 121 is spaced apart from the inner circumferential surface of the shell 110 and is elastically supported against the inner space 110a of the shell 110 , that is, the bottom surface of the base shell 111 , and the rotor 122 is the stator 121 . ) is rotatably installed inside the

The stator 121 according to the present embodiment includes a stator core 1211 and a stator coil 1212 .

The stator core 1211 is made of a metal material such as an electrical steel sheet, and when a voltage is applied from the outside to the electric part 120, the stator coil 1212 and the rotor 122, which will be described later, interact with each other through electromagnetic force. carry out

In addition, the stator core 1211 is formed in a substantially rectangular cylindrical shape. For example, the inner circumferential surface of the stator core 1211 may be formed in a circular shape, and the outer circumferential surface may be formed in a rectangular shape. Bolt holes (not shown) are formed through each of the four corners of the stator core 1211, and fixed self-fastening bolts (not shown) pass through each bolt hole, respectively, and are fastened to the main bearing plate 141 to be described later. Accordingly, the stator core 1211 is fixed to the lower surface of the main bearing plate 141 by the fixing self-fastening bolts.

In addition, in a state where the stator core 1211 is spaced apart from the inner circumferential surface of the shell 110 in the axial and radial directions, the lower end of the stator core 1211 is attached to a support spring 152 to be described later with respect to the bottom surface of the shell 110 . supported by Accordingly, vibration generated during operation may be suppressed from being directly transmitted to the shell 110 .

The stator coil 1212 is wound inside the stator core 1211 . As described above, when a voltage is applied from the outside, the stator coil 1212 generates an electromagnetic force to perform electromagnetic interaction with the stator core 1211 and the rotor 122 . Through this, the electric unit 120 generates a driving force for the reciprocating motion of the compression unit 140 .

An insulator 1213 is disposed between the stator core 1211 and the stator coil 1212 . Accordingly, direct contact between the stator core 1211 and the stator coil 1212 is suppressed, so that electromagnetic interaction can be smoothly performed.

The rotor 122 according to this embodiment includes a rotor core 1221 and a magnet 1222 .

The rotor core 1221, like the stator core 1211, is made of a metal material such as an electrical steel sheet, and has a substantially cylindrical shape. A rotation shaft 130 to be described later may be press-fitted to the center of the rotor core 1221 .

The magnet 1222 is made of a permanent magnet, and may be inserted and coupled at equal intervals along the circumferential direction of the rotor core 1221 . The rotor 122 rotates through electromagnetic interaction with the stator core 1211 and the stator coil 1212 when a voltage is applied. Accordingly, while the rotation shaft 130 rotates together with the rotor 122 , the rotational force of the electric unit 120 is transmitted to the compression unit 140 .

Next, the axis of rotation will be described.

The rotating shaft 130 according to the present embodiment includes a rotor coupling portion 131 , a main bearing surface portion 132 , an eccentric portion 133 , and a sub bearing surface portion 134 .

The rotor coupling portion 131 is a portion press-fitted to the rotor core 1221 , and forms a lower half of the rotation shaft 130 . A lower end of the rotor coupling unit 131 may extend longer than a lower end of the rotor 122 , and an oil feeder 138 to be described later may be installed at the lower end of the rotor coupling unit 131 .

The main bearing surface part 132 is formed in the middle of the rotation shaft 130 , that is, between the rotor coupling part 131 and the eccentric part 133 . The main bearing surface part 132 is formed on the same axis as the rotor coupling part 131 and is rotatably inserted into the main bearing part 1413 of the main bearing plate 141 which will be described later.

The eccentric portion 133 is formed between the upper end of the main bearing surface portion 133 and the lower end of the sub bearing surface portion 134 . The eccentric portion 133 is formed eccentrically with respect to the center of the rotor coupling portion 131 , that is, the center of the rotation shaft 130 , and a roller 1441 to be described later is rotatably inserted therein. Accordingly, when the rotating shaft 130 rotates, the roller 1441 compresses the refrigerant while rotating in the inside of the compression chamber (V).

The sub bearing surface portion 134 extends in the axial direction from the upper end of the eccentric portion 133 . The sub bearing surface portion 134 is formed on the same axis as the main bearing surface portion 132 and is rotatably inserted into the sub bearing portion 1422 of the sub bearing plate 142 to be described later.

On the other hand, an oil pumping hole 135 penetrating between both ends of the rotation shaft 130 in the axial direction is formed inside the rotation shaft 130 , and a first oil supply hole is formed at a predetermined interval along the axial direction of the rotation shaft 130 . (1361), the second oil supply hole 1362, the third oil supply hole 1363 is formed through the outer peripheral surface of the rotating shaft (130). For example, the first oil supply hole 1361 penetrates through the outer peripheral surface of the main bearing surface portion 132, the second oil supply hole 1362 penetrates through the outer peripheral surface of the eccentric part 133, and the third oil supply hole 1363 Silver may penetrate through the outer peripheral surface of the sub-bearing surface portion 134 .

In addition, an oil feeder 138 for pumping oil in the shell 110 to the oil pumping hole 135 may be installed at the lower end of the oil pumping hole 135 . The oil feeder 138 may be variously applied, such as a trochoid gear pump, a spiral shaft, or a propeller oil feeder.

Accordingly, the oil inside the shell 110 is pumped by the oil feeder 138 and moves toward the upper end of the rotation shaft 130 through the oil pumping hole 135, and a part of this oil is the oil pumping hole 135. In the middle of the lubrication is supplied to each bearing surface through the first oil supply hole 1361, the second oil supply hole 1362, and the third oil supply hole 1363.

Next, the compression unit will be described.

5 is a perspective view showing the compressor body in FIG. 1 , and FIG. 6 is an exploded perspective view showing the compressor body by removing the suction muffler.

5 and 6 , the compression unit 140 according to the present embodiment includes a main bearing plate (hereinafter, referred to as a main bearing) 141 , a sub-bearing plate (hereinafter referred to as a sub-bearing) 142 , and a cylinder 143 . , including a vane roller 144 . The main bearing 141 and the sub bearing 142 are provided on both sides of the axial direction with the cylinder 143 interposed therebetween to form a compression chamber V inside the cylinder 143 .

In addition, the main bearing 141 and the sub bearing 142 radially support the rotation shaft 130 penetrating the cylinder 143 . The vane roller 144 is coupled to the eccentric portion 133 of the rotating shaft 130 to compress the refrigerant while rotating in the cylinder 143 .

The main bearing 141 may have a main plate portion 1411 formed in a disk shape, and a stator fixing protrusion 1412 may be formed at an edge of the main plate portion 1411 . The stator fixing protrusions 1412 may be formed to protrude downwardly from the four corners of the main plate 1411 toward the transmission 120 .

In addition, the stator fixing protrusion 1412 is fastened to the stator 121 by a fixing self-fastening bolt (unsigned), and may be elastically supported by the base shell 111 together with the stator 121 of the transmission unit 120 .

A main bearing part 1413 is formed to protrude upward toward the transmission part in the center of the main plate part 1411 , and a main bearing hole 1413a is formed through the main bearing part 1413 so that the rotating shaft 130 is inserted and supported. can be

In the sub bearing 142 , the sub plate portion 1421 is formed in a disk shape and may be bolted to the main bearing 141 together with the cylinder 143 . Of course, when the cylinder 143 is fixed to the shell 110 , the main bearing 141 may be bolted to the cylinder 143 together with the sub bearing 142 , respectively, and the sub bearing 142 is the shell 110 . ), the cylinder 143 and the main bearing 141 may be fastened to the sub bearing 142 with bolts.

In the center of the sub-plate part 1421, a sub-bearing part 1422 is formed to protrude downward toward the bottom surface of the shell 110, and a sub-bearing hole 1422a is provided in the sub-bearing part 1422 and a main bearing hole 1413a. It is formed by penetrating on the same axis as the The lower end of the rotation shaft 130 is supported in the sub bearing hole 1422a.

Referring back to FIG. 4 , the cylinder 143 is formed in an annular shape. The inner circumferential surface of the cylinder 143 is formed in a perfect circle shape having the same inner diameter. The inner diameter of the cylinder 143 is formed larger than the outer diameter of the roller (1441). Accordingly, a compression chamber V is formed between the inner peripheral surface of the cylinder 143 and the outer peripheral surface of the roller 1441 .

For example, the inner peripheral surface of the cylinder 143 is the outer wall surface of the compression chamber (V), the outer peripheral surface of the roller 1441 is the inner wall surface of the compression chamber (V), the vane 1445 is the compression chamber (V) side Each wall can be formed. Therefore, as the roller 1441 rotates, the outer wall surface of the compression chamber V forms a fixed wall, while the inner wall surface and the side wall surface of the compression chamber V form a variable wall whose position is variable. have.

A suction port 1431 is formed in the cylinder 143, a vane slot 1432 is formed on one side in the circumferential direction of the suction port 1431, and a discharge guide groove is formed on the opposite side of the suction port 1431 with the vane slot 1432 interposed therebetween. (1433) is formed.

The suction port 1431 may be formed to radially penetrate the inner circumferential surface from the outer circumferential surface of the cylinder 143 . The suction port 1431 may be formed to have a single inner diameter. However, when the outlet extension portion 1613a is formed at the outlet end of the suction muffler 161 to be described later, the extension portion insertion groove 1431a is stepped on the outer peripheral side of the suction port 1431 so that the outlet extension portion 1613a is inserted. may be formed. Accordingly, even when the outlet extension portion 1613a provided at the outlet end of the suction muffler 161 is inserted into the suction port 1431 , it is possible to suppress a decrease in the inner diameter of the suction port 1431 to secure the refrigerant suction amount.

In addition, a muffler mounting groove 1435 into which a suction muffler outlet 1613 to be described later is inserted and coupled may be formed on the outer periphery of the suction port 1431 . The muffler mounting groove 1435 may be formed by being depressed in the radial direction from the outer circumferential surface of the cylinder 143 .

For example, the muffler mounting groove 1435 may be formed in a substantially hexahedral shape to correspond to the suction muffler outlet 1613 . Specifically, the muffler mounting groove 1435 has both sides in the circumferential direction and a radially inner surface facing the inlet 1431 are each formed in a closed shape, and both axial side surfaces and radially outer surfaces are each formed in an open shape. can

Here, the blocked side surfaces of the muffler mounting groove 1435 form a support surface for supporting the side surfaces of the suction muffler outlet 1613 facing it. For example, both sides of the muffler mounting groove 1435 in the circumferential direction form a first muffler support surface 1435a, and the inner surface of the muffler mounting groove 1435 forms a second muffler support surface 1435b. .

Accordingly, the suction muffler outlet 1613 to be described later may be inserted and coupled from the outer circumferential side of the muffler mounting groove 1435 to the inner circumferential side. And, as both sides of the muffler mounting groove 1435 in the upper and lower axial directions are opened, the cross-sectional area of the suction muffler outlet 1613 is made as large as possible, so that the flow path area of the suction muffler outlet 1613 is secured as much as possible. can The muffler mounting groove 1435 will be described again later with the suction muffler 161 .

The vane slot 1432 is elongated in the direction toward the outer circumferential surface on the inner circumferential surface of the cylinder 143 . The inner circumferential side of the vane slot 1432 is opened, and the outer circumferential side is formed to be blocked or blocked by the inner circumferential surface of the shell 110 .

The vane slot 1432 is formed to have a width approximately similar to the thickness or width of the vane 1445 so that the vane 1445 of the vane roller 144, which will be described later, slides. Accordingly, both sides of the vane 1445 are supported by both inner wall surfaces of the vane slot 1432 and slide approximately in a straight line.

The discharge guide groove 1433 is formed by chamfering the inner edge of the cylinder 143 in a hemispherical shape. The discharge guide groove 1433 serves to guide the refrigerant compressed in the compression chamber V of the cylinder 143 to the discharge port 1423 of the sub bearing 142 . Accordingly, the discharge guide groove 1433 is formed at a position overlapping the discharge port 1423 when projected in the axial direction so as to communicate with the discharge port 1423 .

However, since the discharge guide groove 1433 generates a dead volume, it is preferable not to form the discharge guide groove 1433 as much as possible. .

Meanwhile, compression chamber sealing grooves (unsigned) are formed on both upper and lower sides of the cylinder 143 , and the compression chamber sealing member 146 made of an O-ring or gasket may be inserted into the compression chamber sealing groove.

For example, the compression chamber sealing member 146 may be formed in an annular shape and installed along the periphery of the compression chamber (V). Specifically, the compression chamber sealing member 146 surrounds the outer peripheral side of the vane slot 1432 and the outer peripheral side of the discharge guide groove 1433, and seals between the inner peripheral side of the muffler mounting groove 1435 and the compression chamber (V). It can be installed through the face.

Accordingly, the compression chamber sealing member 146, including the vane slot 1432 and the discharge guide groove 1433, encloses and seals the compression chamber V, and at the same time seals between the compression chamber V and the muffler mounting groove 1435. It is separated and sealed. Through this, it is possible to suppress leakage of the high-pressure refrigerant compressed in the compression chamber V into the internal space 110a of the shell 110 constituting the relatively low-pressure part.

The compression chamber sealing member 146 may be installed on both sides of the cylinder 143 in the axial direction, but in some cases, it is installed on the main bearing 141 or the sub bearing 142 facing both sides of the cylinder 143 . it might be

Meanwhile, the vane roller 144 includes a roller 1441 and a vane 1445 as described above. The roller 1441 and the vane 1445 may be formed as a single body, or may be combined to perform a relative motion. Hereinafter, the present embodiment will be mainly described with respect to an example in which the roller and the vane are rotatably coupled.

Referring back to FIG. 4 , the roller 1441 is formed in a cylindrical shape. The roller 1441 may be formed in a perfect circle shape having the same center as the inner circumferential surface and the outer circumferential surface, or may be formed in a perfect circle shape in which the inner circumferential surface and the outer circumferential surface of the roller 1441 have different centers.

In addition, the axial height of the roller 1441 is formed to be substantially equal to the height of the inner peripheral surface of the cylinder (143). However, since the roller 1441 must slide with respect to the main bearing 141 and the sub bearing 142 , the axial height of the roller 1441 may be formed to be slightly smaller than the height of the inner circumferential surface of the cylinder 143 .

In addition, the inner peripheral height and the outer peripheral height of the roller 1441 is formed to be substantially the same. Accordingly, both axial end surfaces connecting between the inner peripheral surface and the outer peripheral surface of the roller 1441 form a sealing surface, respectively. These sealing surfaces are formed at right angles to the inner circumferential surface or the outer circumferential surface of the roller 1441, respectively. However, the edge between the inner circumferential surface of the roller 1441 and each sealing surface or the edge between the outer circumferential surface of the roller 1441 and each sealing surface may be formed to be slightly inclined or curved.

In addition, the roller 1441 is rotatably inserted and coupled to the eccentric portion 133 of the rotating shaft 130, and the vane 1445 is slidably coupled to the vane slot 1432 of the cylinder 143 to the roller 1441. is hinged to the outer circumferential surface of the Accordingly, when the rotating shaft 130 rotates, the roller 1441 makes a reciprocating motion within the cylinder 143 by the eccentric portion 133 and the vane reciprocates in a state coupled to the roller 1441 .

Also, the rollers 1441 may be aligned to be co-center with respect to the cylinder 143, but may be aligned slightly eccentrically in some cases.

In addition, the roller 1441 is formed in an annular shape so that its inner peripheral surface has an inner diameter that can be in sliding contact with the outer peripheral surface of the eccentric portion 133 of the rotation shaft 130 . The radial width (thickness) of the roller 1441 is formed to a thickness sufficient to secure a sealing distance from the hinge groove 1411 to be described later.

In addition, the thickness of the roller 1441 may be uniformly formed along the circumferential direction, or may be formed differently in some cases. For example, the inner peripheral surface of the roller 1441 may be formed in an elliptical shape.

However, in order to minimize the load during rotation of the rotary shaft 130, the inner and outer peripheral surfaces of the roller 1441 are formed in a round shape having the same center, and the radial thickness of the roller 1441 is formed uniformly along the circumferential direction. it may be desirable

In addition, one hinge groove 1411 is formed on the outer peripheral surface of the roller 1441 so that a vane hinge portion 1445b of a vane 1445 to be described later is inserted and rotated. The hinge groove 1411 is formed in an arc shape with an open outer circumferential surface.

The inner diameter of the hinge groove 1411 is formed to be larger than the outer diameter of the vane hinge portion 1445b, and is formed to a size sufficient to slide without falling out while the vane hinge portion 1445b is inserted.

Meanwhile, referring back to FIG. 4 , the vane 1445 includes a vane body portion 1445a and a vane hinge unit 1445b.

The vane body portion 1445a is a portion constituting the vane body, and is formed in a flat plate shape having a predetermined length and thickness. For example, the vane body portion 1445a is formed in a rectangular hexahedral shape as a whole. In addition, the vane body portion 1445a is formed with a length such that the vane 1445 remains in the vane slot 1432 even in a state in which the roller 1441 has completely moved to the opposite side of the vane slot 1432 .

The vane hinge portion 1445b is formed to extend to the front end of the vane body portion 1445a facing the roller 1441 . The vane hinge portion 1445b is inserted into the hinge groove 1411 and formed to have a rotatable cross-sectional area. The vane hinge portion 1445b may be formed in a semi-circular shape or a substantially circular cross-sectional shape excluding the connecting portion to correspond to the hinge groove 1411 .

Next, the support part will be described.

Referring back to FIG. 3 , the support part 150 according to the present embodiment includes a spring cap 151 and a support spring 152 . The support part 150 supports between the lower surface of the electric part and the bottom surface of the base shell 111 facing it, and generally supports the four corners of the electric part 120 with respect to the shell 110 . Accordingly, the support unit 150 forms a support unit as a pair of the spring cap 151 and the support spring 152 so that each support unit supports the four corners of the compressor body C. Hereinafter, a pair of support units will be described as a representative example.

The spring cap 151 according to this embodiment is fixed to the first spring cap 1511 fixed to the bottom surface of the base shell 111 and the lower surface of the electric part 120 (precisely, the lower surface of the stator core). It may be formed of a second spring cap 1512 .

The first spring cap 1511 and the second spring cap 1512 may be disposed on a coaxial line in the axial direction, or may be disposed on different axial lines in some cases. When the first spring cap 1511 and the second spring cap 1512 are disposed on different axial lines, it is advantageous that the second spring cap 1512 is disposed outside the first spring cap 1511 . .

Each of the first spring cap 1511 and the second spring cap 1512 may be formed of a rubber material, or may be formed by being wrapped around an outer circumferential surface of a metal material with a rubber or plastic material in consideration of installation rigidity and cushioning.

For example, the first spring cap 1511 is inserted into the cap fixing groove (not shown) in the metal base shell 111 to be firmly fixed, so it may be formed of a metal material. However, since the second spring cap 1512 is inserted into and fixed to the bolt head (not shown) of the fixing self-fastening bolt (not shown) protruding in the axial direction from the lower surface of the stator core 1211, it may be formed of a rubber or plastic material. can

The support spring 152 may be formed of a compression coil spring. One end of the support spring 152 may be inserted into and fixed to the first spring cap 1511 , and the other end of the support spring 152 may be inserted and fixed into the second spring cap 1512 . Accordingly, the stator core 1211 may be elastically supported by the shell by the support spring 152 .

Next, the suction/discharge part will be described.

Referring back to FIG. 1 , the suction/discharge unit 160 according to the present embodiment includes a suction muffler 161 and a discharge muffler 162 . The suction muffler 161 may be coupled to the outer peripheral surface of the cylinder 143 , and the discharge muffler 162 may be coupled to the upper surface of the sub bearing 142 . Accordingly, the suction muffler 161 is located below the sub bearing 142 , and the discharge muffler 162 is located above the sub bearing 142 .

In addition, the inlet of the suction muffler 161 is spaced apart from the inner circumferential surface of the shell 110 and communicates with the inner space 110a of the shell 110, and the outlet of the suction muffler 161 communicates with the suction port 1431 and is compressed ( V) can be directly connected to the room. Accordingly, the refrigerant sucked from the suction pipe 120 flows into the suction muffler 161 through the inner space 110a of the shell 110, and the refrigerant flows into the compression chamber V through the suction muffler 161. is inhaled

In addition, the inlet of the discharge muffler 162 is coupled to the sub bearing 142 to directly communicate with the discharge port 1423 , and the outlet of the discharge muffler 162 is connected to the loop pipe 118 to the refrigerant discharge pipe 116 . can be directly connected. Accordingly, the roof pipe 118 connects between the discharge muffler and the refrigerant discharge pipe at a position higher than the oil level of the oil filled in the inner space 110a of the shell 110, and thereby is discharged from the compression chamber (V). The refrigerant is discharged to the outside of the compressor through the discharge muffler 162 , the loop pipe 118 , and the refrigerant discharge pipe 116 without heating the oil in the inner space 110a of the shell 110 .

A detailed look at the suction muffler and the discharge muffler is as follows. The suction muffler will be described first.

7 is a perspective view showing an embodiment of the suction muffler in FIG. 1 , FIG. 8 is a perspective view showing the suction muffler according to FIG. 7 is assembled, and FIG. 9 is a sectional view “IV-IV” in FIG.

5 and 6 again, the suction muffler 161 according to the present embodiment may include a suction muffler body 1611, a suction muffler inlet 1612, and a suction muffler outlet 1613. can The suction muffler 161 may have a suction space 1611a to be described later formed therein by assembling a plurality of members. In this embodiment, the suction muffler 161 may be formed by assembling the lower muffler and the upper muffler.

A suction space 1611a having a predetermined volume is formed inside the suction muffler body 1611 . The suction muffler body 1611 may be formed as a single member, or may be formed by assembling a plurality of members. However, since the suction muffler body 1611 needs to have a suction space 1611a therein, it may be formed by assembling a plurality of members.

The inside of the suction space 1611a may be formed as a single space, but may be formed to have a plurality of spaces or flow paths in order to increase the noise attenuation effect. For this, it may be formed according to the internal shape of a conventional muffler.

The suction muffler inlet 1612 may communicate with the lower half of the suction space 1611a. In addition, as the suction muffler 161 is disposed adjacent to the outer circumferential surface of the compressor body C including the electric part, the suction muffler inlet 1612 may be preferably formed on the outer surface of the suction muffler body 1611. have.

The suction muffler inlet 1612 may be preferably formed eccentrically to one side in the circumferential direction to secure the length of the suction passage. Accordingly, the suction muffler outlet 1613 to be described later may be eccentrically formed on the opposite side of the suction muffler inlet 1612 in the circumferential direction.

The suction muffler outlet 1613 may communicate with the upper half of the suction space 1611a. The suction muffler outlet 1613 may be formed consecutively to the suction muffler body 1611 . However, the outlet portion 1613 of the suction muffler is coupled to the outer circumferential surface of the cylinder 143 , and the main bearing plate 141 is positioned below the cylinder 143 . Then, when the suction muffler outlet 1613 is formed successively to the suction muffler body 1611 , the suction muffler body 1611 should be installed at a radially widened position avoiding interference with the main bearing plate 141 . Then, the lateral diameter of the compressor may increase, making it difficult to downsize the compressor.

Accordingly, the suction muffler body part 1611 and the suction muffler outlet part 1613 may be connected by the suction muffler connection part 1614 . The suction muffler connecting portion 1614 may be formed to be long like a neck portion of a kind of muffler.

The suction muffler connection part 1614 may be inclined by a predetermined angle α in a direction from the suction muffler body part 1611 toward the cylinder 143 . Accordingly, the flow resistance of the refrigerant from the suction muffler body 1611 to the suction muffler outlet 1613 is reduced, so that the refrigerant can be smoothly sucked into the suction port 1431 of the cylinder 143 (refer to FIG. 9 ). )

Meanwhile, the suction muffler outlet 1613 may be formed to correspond to the cross-sectional shape of the muffler mounting groove 1435 of the cylinder 143 . For example, the suction muffler outlet 1613 may have a substantially rectangular cross-sectional shape when projected in a radial direction. Accordingly, both sides of the suction muffler outlet portion 1613 in the circumferential direction may be respectively closely adhered to and supported in the circumferential direction of the muffler mounting groove 1435 in the circumferential direction.

In addition, the muffler fixing part 1615 may be formed to extend in the circumferential direction on both sides of the suction muffler outlet part 1613 in the circumferential direction. The circumferential length of the muffler fixing part 1615 may be longer than the circumferential length of the muffler mounting groove 1435 . Accordingly, the muffler fixing part 1615 may be fixed to the cylinder 143 outside the muffler mounting groove 1435 .

For example, the circumferential length (hereinafter, the first length) L1 from the center O of the suction port 1431 to the fixing point (ie, the fastening hole) of the muffler fixing part 1615 is the suction port 1431 . From the center O to the first muffler support surface 1435a of the muffler mounting groove 1435, the circumferential length (hereinafter, the second length) L2 may be formed to be equal to or longer than the length L2.

Specifically, the first length L1 may be longer than the second length L2. Accordingly, the vibration transmitted by the suction muffler 161 during the operation of the compressor is buffered and absorbed to a certain extent by the muffler fixing unit 1615, and the stress in the muffler fixing unit 1615 is reduced to prevent the suction muffler 1616. It can be fixed more stably.

In addition, the muffler fixing part 1615 may be formed in a curved shape having the same curvature as that of the outer circumferential surface of the cylinder 143 . Accordingly, the muffler fixing part 1615 may be fixed in close contact with the outer peripheral surface of the cylinder 143 .

In addition, a fastening hole 1616a is formed in the muffler fixing part 1615 , and a fastening groove 143a may be formed on the outer peripheral surface of the cylinder 143 facing the fastening hole 1616a. Accordingly, the muffler fixing part 1615 is fastened by the muffler fastening bolt 1616 that penetrates the fastening hole 1616a and is fastened to the fastening groove 143a, and then the suction muffler 161 is stably attached to the cylinder 143. It can be fastened with

Also, a muffler sealing member 1617 may be provided between the end surface 1613b of the suction muffler outlet 1613 and the inner surface of the muffler mounting groove 1435 of the cylinder 143 facing the same in the radial direction. The muffler sealing member 1617 is formed of an O-ring or a flat gasket, and when an outlet extension 1613a to be described later is formed on the suction muffler outlet 1613, the outlet extension 1613a is wrapped around the suction muffler outlet portion ( 1613) may be in close contact between the end surface 1613b and the inner surface of the muffler mounting groove 1435.

Accordingly, a portion of the oil in the shell 110 inner space 110a (for example, oil flowing into the oil passage hole 1721 of the oil supply unit 170 to be described later) is partially transferred to the suction muffler 161 and the cylinder 143 . ) through the gap between the intake port 1431 can be suppressed.

On the other hand, the outlet extension portion 1613a of the suction muffler outlet portion 1613 may be formed to extend toward the cylinder (143). The outlet extension portion 1613a is formed to extend in a cylindrical shape from the end surface 1613b of the suction muffler outlet portion 1613, and is inserted into the extension portion insertion groove 1431a of the suction port 1431 described above to be radially supported. can Accordingly, when the suction muffler 161 is inserted into the muffler mounting groove 1435 to be coupled, the assembly position of the suction muffler 161 is easily aligned and the refrigerant between the suction muffler 161 and the suction port 1431 . It can effectively block leakage or oil inflow.

Meanwhile, although not shown in the drawings, it is possible to fix the front end surface of the suction muffler outlet 1613 in close contact with the outer circumferential surface of the cylinder 143 without forming a muffler mounting groove in the cylinder 143 .

In addition, in the above-described embodiment, the muffler fixing part 1615 is integrally formed with the suction muffler 161, but in some cases, a separate muffler fastened to the cylinder 143 without integrally forming the muffler fixing part. The suction muffler 161 may be fixed to the cylinder 143 using a fixing member. This will be explained again later.

Next, the discharge muffler will be described.

2 and 3 again, the discharge muffler 162 according to the present embodiment includes a discharge muffler body 1621 having a discharge space 1621a to accommodate the discharge port 1423, and a discharge muffler body ( It extends from 1621 and includes a discharge muffler fixing part 1622 fixed to the upper surface of the sub bearing 142 .

The discharge muffler body part 1621 is composed of a side wall surface and an upper wall surface forming the discharge space 1621a, and the side wall surface forming the discharge space 1621a is connected to the roof pipe 118 to form the discharge space 1621a. A refrigerant discharge hole 1621b for guiding the discharged refrigerant to the discharge pipe 116 may be formed. Accordingly, the refrigerant discharged to the discharge space 1621a is discharged to the loop pipe 118 through the refrigerant discharge hole 1621b while the discharge noise is canceled in the discharge space 1621a, and the refrigerant is discharged through the discharge pipe 116 through the condenser.

Also, a bearing part through hole 1621c through which the sub bearing part 1422 passes may be formed in the center of the upper wall surface of the discharge muffler body part 1621 . The bearing part through-hole 1621c may be formed by simply passing through the upper wall surface of the discharge muffler body part 1621 . However, since the sub-bearing part 1422 is inserted through the bearing part through-hole 1621c, a sealing member (unsigned) can be installed between the sub-bearing part 1422 and the inner side of the discharge space 1621a. It may be formed into a cylindrical shape by bending.

In addition, as the rotation shaft 130 is inserted into the sub-bearing part 1422 to pass through, the upper end of the rotation shaft 130 is exposed to the outside of the discharge muffler 162 . Accordingly, the upper end of the rotation shaft 130 on which the oil pumping hole 135 is formed is exposed to the outside of the discharge muffler 162 , and the oil sucked through the oil pumping hole 135 is discharged to the outside of the discharge muffler 162 . will become This oil is supplied to the rear side of the vane slot 1432 by an oil guide 171 to be described later. This will be explained again in the refueling department.

Next, the oil supply part will be described.

2 to 4 , the oil supply unit 170 according to the present embodiment includes an oil guide 171 and an oil passage unit 172 . The oil guide serves to collect oil scattered from the upper end of the rotation shaft 130 , and the oil passage 172 is connected to the oil guide 171 to guide the oil to the corresponding position. Accordingly, based on the flow order of the oil, the oil guide 171 is provided on the downstream side of the rotation shaft 130 , and the oil passage part 172 is provided to be located on the downstream side rather than the oil guide 171 .

The oil guide 171 may be provided outside the upper wall surface of the discharge muffler 162 . The oil guide 171 may be integrally formed with the discharge muffler 162 , and may be welded or fastened according to a material. The oil guide 171 may be formed of a metal or a material such as plastic.

In addition, the lower surface of the oil guide 171 in contact with the discharge muffler 162 may be opened, and the side and upper surfaces of the oil guide 171 may be formed in a closed shape to collect oil scattered from the upper end of the rotation shaft 130 . Accordingly, a portion of the side surface and the upper surface of the oil guide 171 may form an oil accommodating space 1711 together with the upper surface of the discharge muffler 163 . However, the side of the side that faces the oil passage portion 172 among the side surfaces constituting the oil receiving space 1711 may be opened to form a guide outlet 1712 .

An oil guide protrusion 1713 may be formed on the outer peripheral surface of the guide outlet 1712 . The oil guide protrusion 1713 may be provided between the oil guide 171 and the oil passage portion 172 . Accordingly, the oil collected in the oil guide 171 can smoothly move to the oil guide hole 172 by the oil guide protrusion 1713 .

The oil guide protrusion 1713 may include a first guide protrusion 1713a and a second guide protrusion 1713b.

The first guide protrusion 1713a may be continuously formed along the upper surface and the side surface of the discharge muffler 162 . The first guide protrusion 1713a may be integrally formed with the oil guide 171 or may be integrally formed with the outer surface of the discharge muffler 142 . In addition, the first guide protrusion 1713a may be post-assembled to the oil guide 171 or the discharge muffler 142 .

The second guide protrusion 1713b may be formed on the upper surface of the sub bearing 142 in succession to the first guide protrusion 1713a. For example, the second guide protrusion 1713b may be formed to surround a portion of the circumference of the oil passage hole 1721 to be described later. Accordingly, the oil guided by the oil guide protrusion 1713 can move to the oil passage hole 1721 without flowing out to another place.

The oil passage portion 172 is formed through the sub bearing 142 and the cylinder 143 so as to supply the oil guided by the oil guide 171 toward the compression portion 140 , precisely to the rear of the vane slot 1432 . can be For example, the oil passage part 172 may include an oil passage hole 1721 formed in the sub bearing 142 .

The inlet end of the oil passage hole 1721 is exposed to the inner space 110a of the shell 110 and communicates with the oil guide 171 , and the outlet end of the oil passage hole 1721 communicates with the vane slot 1432 . . However, when an oil storage groove 1722 to be described later is formed on the outer periphery of the vane slot 1432 , the outlet end of the oil passage hole 1721 communicates with the vane slot 1432 through the oil storage groove 1722 . can

Accordingly, the oil receiving space 1711 of the oil guide 171 communicates with the vane slot 1432 through the oil passage hole 1721, and the oil collected by the oil guide 171 is the oil passage hole 1721. It may be supplied to the vane slot 1432 through.

The circumferential width of the oil passage hole 1721 may be wider than the circumferential width of the vane slot 1432 . Accordingly, the oil collected by the oil guide 171 and moving to the lower space of the shell 110 may be accommodated by the oil passage hole 1721 .

Meanwhile, an oil storage groove 1722 recessed by a predetermined width and depth may be formed on the outer periphery of the vane slot 1432 . The cross-sectional area of the oil storage groove 1722 may be formed to be substantially the same as the cross-sectional area of the oil passage hole 1721 . Accordingly, the oil moving to the oil passage hole 1721 is accommodated in the oil storage groove 1722 , so that a certain amount of oil can always be stored in the rear of the vane slot 1432 . Through this, oil can be quickly supplied between the vane 1445 and the vane slot 1432 even when the compressor is restarted.

On the other hand, although not shown in the drawings, a non-return valve (not shown) may be further installed in the middle of the oil passage part to selectively open and close the oil passage part to block the reverse flow of refrigerant or oil from the oil storage groove to the oil passage hole. have.

This prevents the refrigerant being compressed in the compression chamber from leaking into the inner space of the shell through the oil passage during operation of the compressor. can be supplied quickly.

The rotary compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the electric part 120, the rotor 122 rotates. When the rotor 122 rotates, the rotation shaft 130 coupled to the rotor 122 rotates while transmitting the rotational force to the vane roller 144 coupled to the eccentric portion 133 of the rotation shaft 130 . .

Then, the roller 141 of the vane roller 144 rotates, and the vane 1445 is inserted into the cylinder 143 and reciprocating while sucking the refrigerant into the compression chamber V of the cylinder 143 and compressing it. do. The compressed refrigerant is continuously compressed by the rollers 141 and the vanes 1445 of the vane roller 144 to open the discharge valve 145 provided in the main bearing 141 and the discharge muffler ( 162), the discharged refrigerant is discharged to the condenser constituting the refrigeration cycle through the loop pipe 118 and the discharge pipe 116, repeating a series of processes.

At this time, the oil stored in the inner space 110a of the shell 110 is pumped by the oil feeder 138 provided at the lower end of the rotating shaft 130 and sucked through the oil pumping hole 135, and the sucked oil A portion is supplied to each bearing surface through the first oil supply hole 1361 , the second oil supply hole 1362 , and the third oil supply hole 1363 to lubricate it.

And the oil sucked up to the upper end of the rotation shaft 130 is scattered in the oil receiving space 1711 formed by the upper surface of the discharge muffler 162 and the oil guide 171 . This oil is collected by the oil guide 171 and flows down the upper surface of the discharge muffler 162 and the upper surface of the sub bearing 142 through the guide outlet 1712 . This oil is guided to the vane slot 1432 through the oil passage hole 1721 and the oil storage groove 1722 of the sub bearing 142, and the oil accumulated in the vane slot 1432 causes the vane 1445 to reciprocate. When doing so, it lubricates between the vane 1445 and the vane slot 1432 or lubricates the bearing surface of the roller 1451 while moving toward the compression chamber (V).

On the other hand, as described above, as the oil storage groove 1722 is formed on the outer periphery of the vane slot 1432, a certain amount of oil is stored, and the oil in the oil storage groove 1722 is stored in the vane slot 1432 during the operation of the compressor. ), while storing a certain amount of oil even when the compressor is stopped, oil can be quickly supplied to the vane slot 1432 when the compressor is restarted. Through this, it is possible to reduce friction loss due to insufficient oil in the compression unit 140 including the vanes 1445 and the vane slots 1432 during restart.

In this way, it is possible to configure a rotary compressor of a spring-supported type in which the compressor body including the electric part and the compression part is spaced apart from the shell by using a single shell. Accordingly, it is possible to reduce the vibration noise of the compressor by preventing the vibration transmitted from the compressor body from being transmitted to the shell. Through this, the volume and weight of the rotary compressor can be reduced, and the number of parts can be reduced, thereby lowering the manufacturing cost.

In addition, it is possible to stably connect the suction muffler to the compression unit by configuring the rotary compressor as a spring-supported method as an upper compression method in which the compression unit is located above the transmission unit. Accordingly, an upper compression type low pressure rotary compressor in which the inner space of the shell forms a low pressure unit may be configured. Through this, the electric part is rapidly cooled by the cold refrigerant sucked into the inner space of the shell, so that the motor efficiency and compressor performance can be improved.

In addition, by configuring the rotary compressor of the spring support type and upper compression type, it is possible to install the loop pipe constituting the discharge flow path to be separated without being submerged in the oil filled in the inner space of the shell. Accordingly, it is possible to prevent in advance that the oil inside the shell is heated by the high-temperature refrigerant discharged through the loop pipe, thereby suppressing a decrease in the viscosity of the oil, and thus friction loss on each bearing surface of the compressor body. can reduce

In addition, it is possible to smoothly supply the oil stored in the shell to the compression unit by using the oil guide and the oil passage while configuring the rotary compressor of the spring-supported and upper compression type. Through this, oil is smoothly supplied to the bearing surfaces of the compressor body, and frictional losses due to insufficient oil on each bearing surface can be reduced.

On the other hand, another embodiment of the suction muffler is as follows.

That is, in the above-described embodiment, the outlet extension is formed at the outlet of the suction muffler and inserted into the inlet. However, in some cases, the outlet extension may not be formed at the outlet of the suction muffler. In this case, the position may be aligned during assembly by the muffler fixing part extending from the suction muffler.

10 is a perspective view showing another embodiment of the suction muffler outlet in the suction muffler of FIG. 6 , and FIG. 11 is a cross-sectional view showing the suction muffler of FIG. 10 assembled.

10 and 11, in the suction muffler 161 according to the present embodiment, the end face 1613b of the suction muffler outlet 1613 is formed flat, and the end face of the suction muffler outlet 1613 ( 1613b) may be in close contact with the second muffler support surface 1435b of the muffler mounting groove 1435 facing in the radial direction.

Also in this case, the muffler sealing member 1617 may be interposed between the end surface 1613b of the suction muffler outlet 1613 and the second muffler support surface 1435b facing the same as in the above-described embodiment. As the muffler sealing member 1617, an O-ring or a gasket may be applied as in the above-described embodiment.

Since the basic configuration of the suction muffler 161 according to the present embodiment and the effects thereof are the same as those of the above-described embodiment, a detailed description thereof will be omitted. However, in the present embodiment, since the outlet extension is not formed on the outlet side of the suction muffler 161, the suction port 1431 may be formed with a single inner diameter.

Accordingly, processing of the suction port 1431 and the suction muffler 161 of the cylinder 143 may be facilitated.

In addition, based on the same thickness of the cylinder 143, the inner diameter of the suction port 1431 may be increased by the depth of the extension part insertion groove of the above-described embodiment, and through this, the suction area of the suction port 1431 is increased, so that the suction amount of the refrigerant This can be improved. In this case, the compression chamber sealing member 146 may be installed on the main bearing 141 or the sub bearing 142 .

On the other hand, another embodiment of the suction muffler is as follows.

That is, in the above embodiment, the muffler fixing part extends in the circumferential direction from both sides of the suction muffler outlet 1613 in the circumferential direction. .

12 is an exploded perspective view showing another embodiment of the suction muffler in FIG. 1 , and FIG. 13 is a perspective view showing the suction muffler of FIG. 12 in an assembled state.

12 and 13 , in the suction muffler 161 according to the present embodiment, a muffler fixing part 1615 may be formed at an upper end of the suction muffler outlet part 1613 . The muffler fixing part 1615 may extend in the circumferential direction from the upper end of the suction muffler outlet part 1613 to correspond to the upper surface 143c of the cylinder 143 .

However, as the vane slot 1432 or the oil storage groove 1722 is formed in an adjacent position on one side of the circumferential direction of the muffler mounting groove 1435 according to the present embodiment, the muffler fixing part 1615 is a vane slot 1432. Alternatively, the oil storage groove 1722 may be formed to extend to the other side in the circumferential direction where the groove 1722 is not formed.

In addition, the muffler fixing part 1615 may be formed flat to correspond to the upper surface 143c of the cylinder 143 . Accordingly, the muffler fixing part 1615 may be supported in the axial direction while seated on the upper surface of the cylinder 143 around the muffler mounting groove 1435 .

In addition, a fastening hole 1615a penetrating in the axial direction is formed in the muffler fixing part 1615 , and a fastening groove 143b may be formed on the upper surface of the cylinder 143 corresponding to the fastening hole 1615a. Accordingly, the muffler fastening bolt 1616 may pass through the fastening hole 1615a of the muffler fixing part 1615 to be fastened to the fastening groove 143b of the cylinder.

Even when the muffler fixing part 1615 is formed at the upper end of the suction muffler outlet 1613 as described above, the effect thereof is similar to that of the above-described embodiment of FIG. 5 . However, in this embodiment, as the muffler fixing part 1615 is formed at the upper end of the suction muffler outlet part 1613 , when the suction muffler 161 is installed, the muffler fixing part 1615 is on the upper surface of the cylinder 143 . It can be supported axially in a seated state. Accordingly, the suction muffler 161 has its suction muffler outlet 1613 inserted into the muffler mounting groove 1435 to be supported in the circumferential direction by the first muffler support surface 1435a, and at the same time, the upper surface of the cylinder 143 The suction muffler 161 can be more stably supported by the cylinder 143 by being supported in the axial direction by the muffler fixing part 1615 mounted on the muffler.

On the other hand, another embodiment of the suction muffler is as follows.

That is, in the above-described embodiments, the muffler fixing part is integrally formed with the suction muffler, but in some cases, it may be fixed to the cylinder using a separate muffler fixing member.

14 is an exploded perspective view showing another embodiment of the suction muffler in FIG. 1 , and FIG. 15 is a perspective view showing the suction muffler of FIG. 14 in an assembled state.

14 and 15 , the suction muffler 161 according to the present embodiment may be fixed by a muffler fixing member 1618 that surrounds the suction muffler outlet 1613 and is fastened to the outer circumferential surface of the cylinder 143. have.

For example, the muffler fixing member 1618 may be formed in a rectangular shape. For example, the circumferential length of the muffler fixing member 1618 may be longer than the circumferential length of the suction muffler outlet 1613 , specifically, the circumferential length of the muffler mounting groove 1435 .

That is, the muffler fixing member 1618 wraps around the outer circumferential surface of the suction muffler outlet portion (or the suction muffler connection portion) 1613 to be coupled to the outer circumferential surface 143d of the cylinder 143 from both sides in the circumferential direction of the muffler mounting groove 1435, respectively. can Accordingly, the vibration transmitted by the suction muffler 161 during the operation of the compressor is buffered and absorbed to a certain extent by the muffler fixing member 1618, thereby reducing the stress in the muffler fixing part 1615, thereby reducing the suction muffler 1616. It can be fixed stably.

In addition, fastening holes 1618a for bolting are formed at both ends of the muffler fixing member 1618, and fastening grooves 143a are formed on the outer peripheral surface 143d of the cylinder 143 corresponding to the fastening hole 1618a. can Accordingly, the suction muffler 161 can be stably fixed to the cylinder 143 by bolting the muffler fixing member 1618 to the cylinder 143 .

In addition, the muffler fixing member 1618 may be formed of a material or shape having elasticity so that the front end surface of the suction muffler outlet part 1613 is pressed toward the second muffler support surface 1435b of the cylinder 143 . For example, the muffler fixing member 1618 may be formed of a thin metal plate material having elasticity or a plastic material. In addition, the muffler fixing member 1618 may be formed in a curved arc shape when projected in an axial direction so as to exert an elastic force in the radial direction.

Accordingly, by elastically fixing the suction muffler outlet 1613 to the cylinder 143 using the muffler fixing member 1618, the end face 1613b of the suction muffler outlet 1613 is closed to the muffler sealing member 1617. It may be in close contact with the second muffler support surface (1435b)) with the interposed therebetween.

In addition, the muffler fixing member 1618 may be formed of a thick metal plate or plastic material whose shape has already been determined. In this case, the suction muffler 161 can be stably fixed.

In addition, when the suction muffler 161 is fixed to the cylinder 143 by the muffler fixing member 1618 surrounding the suction muffler 161 in the circumferential direction, the muffler support protrusion 1613c is formed at the suction muffler outlet 1613. can be formed.

For example, the muffler support protrusion 1613c may extend in a circumferential (or/and radial) direction from the upper end of the suction muffler outlet 1613 so as to span the upper surface 143c of the cylinder 143 . Accordingly, the suction muffler outlet portion 1613 is supported in the circumferential direction by the first muffler support surface 1435a, is radially supported by the second muffler support surface 1435b, and is attached to the muffler support protrusion 1613c. may be supported in the axial direction.

At this time, the muffler fixing member 1618 may be installed so as to be in close contact with the lower surface of the muffler support protrusion 1613c. Then, the muffler support protrusion 1613c is supported in the axial direction by the muffler fixing member 1618 so that the suction muffler 161 can be supported more stably.

Although not shown in the drawings, the muffler support protrusion 1613c may be formed to extend from the middle of the suction muffler outlet 1613 in the circumferential direction. In this case, the support groove may be stepped in a slit shape so that the muffler support protrusion 1613c is inserted into the first muffler support surface 1435a of the muffler mounting groove 1435 .

As described above, in the state in which the suction muffler 161 is supported by the cylinder 143, both ends of the muffler fixing member 1618 surrounding the suction muffler outlet 1613 are fastened to the outer circumferential surface of the cylinder 143, the suction muffler 161 may be stably fixed to the cylinder 143 .

In the above, specific embodiments of the present invention have been shown and described. However, since the present invention can be embodied in various forms without departing from the spirit or essential characteristics thereof, the embodiments described above should not be limited by the content of the detailed description.

In addition, even the embodiments not listed in the detailed description described above should be broadly interpreted within the scope of the technical spirit defined in the appended claims. And, all changes and modifications included within the technical scope of the claims and their equivalents should be included by the appended claims.

110: shell 110a: inner space
111: base shell 112: cover shell
115: suction pipe 116: discharge pipe
117: process pipe 118: loop pipe
120: electric part 121: stator
1211: stator core 1212: stator coil
1213: insulator 122: rotor
1221: rotor core 1222: magnet
130: rotation shaft 131: rotor coupling part
132: main bearing surface portion 133: eccentric portion
133a: eccentric part lubrication groove 134: sub bearing surface part
135: oil pumping hole 1361: first oil supply hole
1362: second oil supply hole 1363: third oil supply hole
138: oil feeder 140: compression unit
141: main bearing plate 1411: main plate part
1412: stator fixing protrusion 1413: main bearing part
1413a: main bearing hole 142: sub bearing plate
1421: sub-plate part 1422: sub-bearing part
1422a: sub bearing hole 1423: discharge port
143: cylinder 143a, 143b: fastening groove
143c: upper surface of the cylinder 143d: outer peripheral surface of the cylinder
1431: suction port 1431a: extension part insertion groove
1432: vane slot 1433: discharge guide home
1435: muffler mounting groove 1435a: first muffler support surface
1435b: second muffler support surface 144: vane roller
1441: roller 1441a: hinge groove
1445: vane 1445a: vane body part
1445b: vane hinge portion 145: discharge valve
146: compression chamber sealing member 150: support
151: spring cap 1511: first spring cap
1512: second spring cap 152: support spring
160: suction/discharge unit 161: suction muffler
1611: suction muffler body 1611a: suction space
1612: suction muffler inlet 1613: suction muffler outlet
1613a: outlet extension 1613b: end surface of the outlet of the suction muffler
1613c: muffler support protrusion 1614: suction muffler connection part
1615: muffler fixing part 1615a: fastening hole
1616: muffler fastening bolt 1617: muffler sealing member
162: discharge muffler 1621: discharge muffler body part
1621a: discharge space 1621b: refrigerant discharge hole
1621c: bearing part through hole 1622: discharge muffler fixing part
170: oil supply unit 171: oil guide
1711: oil receiving space 1712: guide exit
1713: oil guide protrusion 1713a: first guide protrusion
1713b: second guide protrusion 172: oil passage part
1721: oil passage hole 1722: oil storage groove
L1: : circumference length of muffler fixing part L2: circumference length of muffler mounting groove
O: center of inlet V: compression chamber

Claims (16)

shells that make up the facade;
an electric part provided to be spaced apart from the inner circumferential surface of the shell;
a rotating shaft coupled to the electric motor to rotate;
a cylinder spaced apart from the inner circumferential surface of the shell and provided on the upper side of the electric part, the cylinder being formed in an annular shape;
a roller coupled to the rotation shaft and provided inside the cylinder;
a vane provided between the cylinder and the roller to form a compression chamber inside the cylinder;
a support part for elastically supporting the electric part on the shell;
a suction muffler having an inlet communicating with the inner space of the shell and an outlet communicating with a suction side of the compression chamber; and
and a discharge muffler having an inlet connected to a discharge side of the compression chamber and an outlet communicating with a refrigerant discharge pipe passing through the shell. According to claim 1,
a main bearing plate provided on an upper side of the electric part; and
Further comprising; a sub-bearing plate coupled to the cylinder from an upper side of the main bearing plate with the cylinder interposed therebetween,
The suction muffler is
A rotary compressor positioned below the sub-bearing plate and provided between an outer peripheral surface of the transmission unit and an inner peripheral surface of the shell facing it. 3. The method of claim 2,
A suction port penetrating in a radial direction is formed in the cylinder, and a muffler mounting groove is formed on the outer circumferential surface of the cylinder by being depressed in a radial direction so as to communicate with the suction port,
A rotary compressor in which the outlet of the suction muffler is inserted into the muffler mounting groove and coupled thereto. 4. The method of claim 3,
A rotary compressor having a muffler fixing part fixed to the cylinder extended at the outlet of the suction muffler. 5. The method of claim 4,
The muffler fixing portion extends from both sides of the suction muffler to correspond to an outer circumferential surface of the cylinder. 5. The method of claim 4,
The muffler fixing part extends from an upper surface of the outlet of the suction muffler to correspond to the upper surface of the cylinder. 4. The method of claim 3,
The suction muffler is fixed to the cylinder by a muffler fixing member that wraps around an outlet of the suction muffler and is fastened to the cylinder. 8. The method of claim 7,
A muffler support protrusion supported in an axial direction on an upper circumferential surface of the muffler mounting groove extends from the outlet portion of the suction muffler. 9. The method of claim 8,
The muffler fixing member is a rotary compressor that axially supports the outlet of the suction muffler from the lower side of the muffler support protrusion. 4. The method of claim 3,
The muffler mounting groove is
The radially outer surface is opened, and both circumferential side surfaces and the radially inner surface are closed, respectively, to form a first muffler support surface and a second muffler support surface,
The suction port penetrates in a radial direction from a second muffler support surface forming a radially inner surface of the muffler mounting groove. 11. The method of claim 10,
An outlet extending portion inserted into the suction port extends toward the suction port at the outlet portion of the suction muffler. 11. The method of claim 10,
A muffler sealing member is provided between the outlet of the suction muffler and the second muffler support surface facing the same. 3. The method of claim 2,
The suction muffler is
a suction muffler body having a suction space therein;
a suction muffler inlet for connecting the suction space of the suction muffler body to the inner space of the shell;
a suction muffler outlet portion coupled to the cylinder to connect the suction space of the suction muffler body to the compression chamber; and
and a suction muffler connection part connecting the suction muffler body and the suction muffler outlet.
The suction muffler connection part,
A rotary compressor inclined toward the cylinder. 3. The method of claim 2,
The cylinder is provided with a vane slot into which the vane is slidably inserted,
A rotary compressor in which an oil passage hole communicating with the vane slot is formed in the sub-bearing plate. 15. The method of claim 14,
A discharge port is formed in the sub-bearing plate, and a discharge muffler having a discharge space to accommodate the discharge port is provided on an upper surface of the sub-bearing plate,
An oil guide is provided on an upper surface of the discharge muffler to collect oil discharged through the rotation shaft and guide it to the oil passage hole. 16. The method according to any one of claims 1 to 15,
One end of the vane is rotatably hinged to the outer peripheral surface of the roller rotary compressor.

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