JP7852354B2 - Closed-type compressor - Google Patents

Description

This invention relates to a sealed compressor and a method for manufacturing the same.

A known type of compressor comprises a vertical cylindrical compressor body and accumulators arranged radially within the compressor body.

Related compressor technologies include those in which the accumulator container is positioned below the main compressor body. This placement of the accumulator container below the main compressor body allows for miniaturization of the compressor in the radial direction.

Japanese Patent Publication No. 2011-27043 Japanese Patent Publication No. 2020-109283

In the compressor described above, the refrigerant supply pipes that supply gaseous refrigerant from the accumulator container to the compression cylinders are located outside the compressor body. This creates a problem where the compressor becomes larger to accommodate the space occupied by the refrigerant supply pipes in the radial direction of the compressor body. In particular, when the compression section has an upper cylinder and a lower cylinder, the two refrigerant supply pipes connected to each cylinder are located outside the compressor body, further increasing the compressor's size relative to the radial direction of the compressor body.

The disclosed technology was developed in view of the above, and aims to provide a sealed compressor and a method for manufacturing the same that can achieve miniaturization of the compressor body container in the radial direction.

One embodiment of the sealed compressor disclosed in this application is a sealed compressor in which a compression section having an upper cylinder and a lower cylinder for compressing inhaled gaseous refrigerant and discharging it into the compressor body container is housed inside a vertical cylindrical compressor body container, and a motor for driving the compression section is housed inside the compressor body container, and an accumulator container is provided below the compressor body container for separating the inhaled refrigerant into gaseous refrigerant and liquid refrigerant and supplying the gaseous refrigerant to the compression section, wherein the compressor body container has a cylindrical main shell and a bottom shell joined to the lower end of the main shell, and the accumulator container has a cup-shaped accumulator shell and an accumulator suction pipe for drawing refrigerant into the accumulator shell , the opening side of the accumulator shell is joined to the compressor body container, and the accumulator suction pipe is an accumulator The ends of the first and second refrigerant supply pipes extend through the bottom shell into the interior of the accumulator shell. Inside the accumulator shell, there is a first refrigerant supply pipe that supplies gaseous refrigerant from the accumulator shell to the upper cylinder of the compression section, and a second refrigerant supply pipe that supplies gaseous refrigerant from the accumulator shell to the lower cylinder of the compression section. The first and second refrigerant supply pipes are connected to the compression section by penetrating the bottom shell of the compressor body container from inside the accumulator shell. The compression section has a first refrigerant supply path that supplies gaseous refrigerant from the first refrigerant supply pipe to the upper compression chamber of the upper cylinder, and a second refrigerant supply path that supplies gaseous refrigerant from the second refrigerant supply pipe to the lower compression chamber of the lower cylinder. The first refrigerant supply pipe is connected to the first refrigerant supply path, and the second refrigerant supply pipe is connected to the second refrigerant supply path. Inside the accumulator shell, each of the first and second refrigerant supply pipes has a straight pipe section that extends linearly in the vertical direction of the compression section, and a curved pipe section that curves upward from the lower end of the straight pipe section. The upper ends of the curved sections of the first refrigerant supply pipe and the second refrigerant supply pipe are located above the aforementioned end of the accumulator suction pipe.

According to one embodiment of the sealed compressor disclosed in this application, the compressor body container can be miniaturized in the radial direction.

Figure 1 is a longitudinal cross-sectional view showing a rotary compressor according to an embodiment. Figure 2 is an exploded perspective view showing the compression section in the embodiment. Figure 3 is a longitudinal cross-sectional view showing an enlarged view of the main part of the embodiment. Figure 4 is a cross-sectional perspective view illustrating the shapes of the first and second refrigerant supply pipes in the embodiment. Figure 5 is a longitudinal cross-sectional view illustrating the shapes of the first and second refrigerant supply pipes in the embodiment. Figure 6 is a cross-sectional view illustrating the shapes of the first and second refrigerant supply pipes in the embodiment. Figure 7 is a longitudinal cross-sectional view showing the connection structure of the first refrigerant supply pipe and the second refrigerant supply pipe in the embodiment. Figure 8A is a plan view of the upper cylinder in the embodiment, seen from above. Figure 8B is a plan view of the upper cylinder in the embodiment, seen from below. Figure 9A is a plan view of the lower cylinder in the embodiment, seen from above. Figure 9B is a plan view of the lower cylinder in the embodiment, seen from below. Figure 10 is a plan view of the intermediate partition plate in the embodiment, seen from above. Figure 11 is a plan view of the lower end plate in the embodiment, seen from below. Figure 12 is a plan view of the lower end plate cover in the embodiment, viewed from below. Figure 13 is a longitudinal cross-sectional view showing another example of the connection structure between the first and second refrigerant supply pipes in the embodiment. Figure 14 is a longitudinal cross-sectional view illustrating the manufacturing method of the rotary compressor according to the embodiment. Figure 15 is a longitudinal cross-sectional view illustrating another example of the manufacturing method of the rotary compressor of the embodiment.

The following describes in detail, with reference to the drawings, embodiments of the sealed compressor and its manufacturing method disclosed in this application. Note that the following embodiments do not limit the sealed compressor and its manufacturing method disclosed in this application.

(Configuration of a rotary compressor)
In this embodiment, a rotary compressor will be described as an example of a closed-type compressor. Figure 1 is a longitudinal cross-sectional view showing the rotary compressor of the embodiment. Figure 2 is an exploded perspective view showing the compression section of the embodiment.

As shown in Figure 1, the rotary compressor 1 is an internal high-pressure, sealed compressor that houses a compression unit 12 inside the compressor body container 10. The compression unit 12 draws in refrigerant from the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S, compresses the refrigerant, and discharges the compressed refrigerant into the compressor body container 10, as well as a motor 11 that drives the compression unit 12. The high-pressure refrigerant compressed by the compression unit 12 is discharged into the compressor body container 10 and further discharged into the refrigeration cycle through a discharge pipe 107.

As shown in Figure 1, the compressor body container 10 has a vertical cylindrical main shell 10a, a cup-shaped top shell 10b, and a cup-shaped bottom shell 10c. The compressor body container 10 is constructed by welding the opening side 10g of the top shell 10b to the upper end of the main shell 10a, and welding the opening side 10d of the bottom shell to the lower end of the main shell 10a.

A discharge pipe 107 is provided, penetrating the top shell 10b, for discharging the high-pressure refrigerant compressed in the compression section 12 from inside the compressor body container 10 into the refrigeration cycle. The discharge pipe 107 is directly joined to the top shell 10b by brazing.

As shown in Figures 1 and 3, below the compressor body container 10, an accumulator container 25 is provided for separating the low-pressure refrigerant drawn in via the accumulator suction pipe 27 (described later) into gaseous and liquid refrigerants, and drawing only the gaseous refrigerant into the compression section 12. The accumulator container 25 has a cup-shaped accumulator shell 26, and the opening side 26a of the accumulator shell 26 is welded to the bottom shell 10c of the compressor body container 10. Therefore, the bottom shell 10c of the compressor body container 10 also serves as a lid that closes the opening side 26a of the accumulator shell 26. Although not shown, the cup-shaped accumulator shell 26 may have a cylindrical main shell and a dish-shaped bottom shell, and the outer circumference of the bottom shell may be joined to the lower end of the main shell.

The accumulator shell 26 is provided with an accumulator suction pipe 27 for drawing refrigerant into the accumulator container 25, and a first refrigerant supply pipe 31T and a second refrigerant supply pipe 31S for supplying gaseous refrigerant from inside the accumulator container 25 to the compression unit 12. The accumulator suction pipe 27 is welded to the accumulator shell 26, penetrating its side wall. The refrigerant supply pipe 31 is located inside the accumulator shell 26 and connects to the compression unit 12 by penetrating the bottom 10e of the bottom shell 10c of the compressor body container 10 from inside the accumulator shell 26. Details of the structure of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S will be described later.

As shown in Figure 1, a base member 310 supporting the entire rotary compressor 1 is fixed by welding to the lower part of the accumulator shell 26, that is, the side opposite the opening side 26a, i.e., the side 26b.

As shown in Figures 1 and 2, the compression section 12 comprises an upper cylinder 121T, a lower cylinder 121S, an intermediate partition plate 140, an upper end plate 160T, a lower end plate 160S, and a rotating shaft 15. The compression section 12 is constructed by stacking the upper end plate 160T, upper cylinder 121T, intermediate partition plate 140, lower cylinder 121S, and lower end plate 160S in that order, and is fixed by multiple bolts 175. Specifically, the intermediate partition plate 140 is positioned between the upper cylinder 121T and the lower cylinder 121S. The upper end plate 160T closes the upper end of the upper cylinder 121T. The lower end plate 160S closes the lower end of the lower cylinder 121S.

Furthermore, the upper end plate 160T is provided with a main bearing portion 161T. The lower end plate 160S is provided with a secondary bearing portion 161S. The rotating shaft 15 is provided with a main shaft portion 153, an upper eccentric portion 152T, a lower eccentric portion 152S, and a secondary shaft portion 151. The rotating shaft 15 is rotatably supported by fitting the main shaft portion 153 of the rotating shaft 15 into the main bearing portion 161T of the upper end plate 160T, and fitting the secondary shaft portion 151 of the rotating shaft 15 into the secondary bearing portion 161S of the lower end plate 160S.

The motor 11 has an externally positioned stator 111 and an internally positioned rotor 112. The stator 111 is fixed to the inner circumferential surface of the main shell 10a by shrink-fitting. The rotor 112 is fixed to the rotating shaft 15 by shrink-fitting.

The compressor body container 10 is filled with lubricating oil 18 in an amount sufficient to almost completely immerse the compression section 12, for the purpose of lubricating the sliding members of the compression section 12 and sealing the high-pressure and low-pressure sections within the compression chamber.

Next, the compression section 12 will be explained in detail using Figure 2. The upper cylinder 121T has a cylindrical upper hollow section 130T inside, and the upper piston 125T is positioned in the upper hollow section 130T. The upper piston 125T is fitted onto the upper eccentric section 152T of the rotating shaft 15. The lower cylinder 121S has a cylindrical lower hollow section 130S inside, and the lower piston 125S is positioned in the lower hollow section 130S. The lower piston 125S is fitted onto the lower eccentric section 152S of the rotating shaft 15.

The upper cylinder 121T has a groove extending from the upper hollow section 130T toward the outer circumference, and the upper vane 127T is positioned in the groove. The upper cylinder 121T has a protruding portion 122T from a part of its circular outer circumference. The upper cylinder 121T has an upper spring hole 124T that connects from the outer circumference of the protruding portion 122T to the groove, and the upper spring 126T is positioned in the upper spring hole 124T. The lower cylinder 121S has a groove extending from the lower hollow section 130S toward the outer circumference, and the lower vane 127S is positioned in the groove. The lower cylinder 121S has a protruding portion 122S from a part of its circular outer circumference. The lower cylinder 121S has a lower spring hole 124S that connects from the outer circumference of the protruding portion 122T to the groove, and the lower spring 126S is positioned in the lower spring hole 124S.

One end of the upper vane 127T is pressed against the upper piston 125T by the upper spring 126T, thereby dividing the space outside the upper piston 125T in the upper hollow portion 130T of the upper cylinder 121T into an upper suction chamber 131T and an upper discharge chamber 133T, which serve as upper compression chambers. The upper cylinder 121T has a first refrigerant supply path 143T formed therein, which supplies gaseous refrigerant to the upper suction chamber 131T through a first refrigerant supply pipe 31T. One end of the lower vane 127S is pressed against the lower piston 125S by the lower spring 126S, thereby dividing the space outside the lower piston 125S in the lower hollow portion 130S of the lower cylinder 121S into a lower suction chamber 131S and a lower discharge chamber 133S, which serve as lower compression chambers. The lower cylinder 121S has a second refrigerant supply path 143S that supplies gaseous refrigerant to the lower intake chamber 131S through a second refrigerant supply pipe 31S. Details of the first refrigerant supply path 143T of the upper cylinder 121T and the second refrigerant supply path 143S of the lower cylinder 121S will be described later.

The upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper discharge chamber 133T. An upper discharge valve 200T, which is a reed valve that opens and closes the upper discharge hole 190T, and an upper discharge valve retainer 201T that restricts the warping of the upper discharge valve 200T are fixed to the upper end plate 160T by upper rivets 202T. An upper end plate cover 170T is positioned above the upper end plate 160T, covering the upper discharge hole 190T, and an upper end plate cover chamber 180T is formed, which is closed by the upper end plate 160T and the upper end plate cover 170T. The upper end plate cover 170T is fixed to the upper end plate 160T by a plurality of bolts 175 that fix the upper end plate 160T and the upper cylinder 121T. The upper end plate cover 170T is provided with an upper end plate cover discharge hole 172 that connects the upper end plate cover chamber 180T to the inside of the compressor body container 10. Furthermore, when the compression section 12 is installed inside the compressor body container 10, the inner circumferential surface of the compressor body container 10 is shrink-fitted to the outer circumferential surface of the upper end plate 160T, and the upper end plate 160T is joined to the compressor body container 10 by welding.

The lower end plate 160S is provided with a lower discharge hole 190S that penetrates the lower end plate 160S and communicates with the lower discharge chamber 133S. A lower discharge valve 200S, which is a reed valve that opens and closes the lower discharge hole 190S, and a lower discharge valve retainer 201S that restricts the curvature of the lower discharge valve 200S are fixed to the lower end plate 160S by lower rivets 202S. A lower end plate cover 170S is positioned below the lower end plate 160S, covering the lower discharge hole 190S, and the lower end plate 160S and the lower end plate cover 170S form a lower end plate cover chamber 180S that is closed off (see Figure 1). The lower end plate cover 170S is fixed to the lower end plate 160S by a plurality of bolts 175 that fix the lower end plate 160S and the lower cylinder 121S. Furthermore, the lower end plate 160S is provided with a lower connection passage 148 that forms a second refrigerant supply path 143S for supplying gaseous refrigerant to the lower cylinder 121S. The upper end portion 32Sa of the straight pipe section 32S of the second refrigerant supply pipe 31S (described later) is connected to the lower connection passage 148.

Furthermore, the compression section 12 is provided with a refrigerant passage hole 136 (see Figure 2) that penetrates the lower end plate 160S, lower cylinder 121S, intermediate partition plate 140, upper end plate 160T, and upper cylinder 121T, and connects the lower end plate cover chamber 180S and the upper end plate cover chamber 180T.

The following describes the flow of refrigerant due to the rotation of the rotating shaft 15. As the rotating shaft 15 rotates, the upper piston 125T, fitted into the upper eccentric portion 152T of the rotating shaft 15, and the lower piston 125S, fitted into the lower eccentric portion 152S, revolve, causing the upper suction chamber 131T and the lower suction chamber 131S to expand in volume while drawing in refrigerant. As a refrigerant intake path, low-pressure refrigerant is drawn into the accumulator container 25 through the accumulator suction pipe 27, while only gaseous refrigerant is drawn into the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S. The gaseous refrigerant drawn into the first refrigerant supply pipe 31T is drawn into the upper suction chamber 131T of the upper cylinder 121T via the first refrigerant supply path 143T (described later). The gaseous refrigerant drawn into the second refrigerant supply pipe 31S is drawn into the lower suction chamber 131S of the lower cylinder 121S via the second refrigerant supply path 143S (described later).

Next, the flow of the discharged refrigerant due to the rotation of the rotating shaft 15 will be explained. As the rotating shaft 15 rotates, the upper piston 125T, fitted into the upper eccentric portion 152T of the rotating shaft 15, revolves, compressing the refrigerant while reducing the volume of the upper discharge chamber 133T. When the pressure of the compressed refrigerant becomes higher than the pressure in the upper end plate cover chamber 180T outside the upper discharge valve 200T, the upper discharge valve 200T opens, discharging the refrigerant from the upper discharge chamber 133T into the upper end plate cover chamber 180T. The refrigerant discharged into the upper end plate cover chamber 180T is then discharged into the compressor body container 10 through the upper end plate cover discharge hole 172 provided in the upper end plate cover 170T.

Furthermore, the rotation of the rotating shaft 15 causes the lower piston 125S, fitted into the lower eccentric portion 152S of the rotating shaft 15, to revolve, compressing the refrigerant while reducing the volume of the lower discharge chamber 133S. When the pressure of the compressed refrigerant becomes higher than the pressure in the lower end plate cover chamber 180S outside the lower discharge valve 200S, the lower discharge valve 200S opens, discharging the refrigerant from the lower discharge chamber 133S into the lower end plate cover chamber 180S. The refrigerant discharged into the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 and the upper end plate cover chamber 180T, and is then discharged into the compressor body container 10 through the upper end plate cover discharge hole 172T provided in the upper end plate cover 170T.

The refrigerant discharged into the compressor body container 10 is guided upwards to the motor 11 through a notch (not shown) connecting the upper and lower parts of the stator 111, or a gap (not shown) in the winding section of the stator 111, or a gap 115 (see Figure 1) between the stator 111 and the rotor 112, and is discharged from the discharge pipe 107 located at the top of the compressor body container 10.

Next, the flow of the lubricating oil 18 will be explained. The lubricating oil 18 sealed in the lower part of the compressor body container 10 is supplied to the compression section 12 by the centrifugal force of the rotating shaft 15, passing through the inside of the rotating shaft 15 (not shown). The lubricating oil 18 supplied to the compression section 12 is drawn into the refrigerant, becomes atomized, and is discharged into the compressor body container 10 together with the refrigerant. The lubricating oil 18 discharged into the compressor body container 10 as atomization is separated from the refrigerant by centrifugal force due to the rotational force of the motor 11, and returns to the lower part of the compressor body container 10 as oil droplets. However, some of the lubricating oil 18 is not separated and is discharged into the refrigeration cycle together with the refrigerant. The lubricating oil 18 discharged into the refrigeration cycle circulates back to the accumulator container 25, where it is separated and remains at the bottom of the accumulator container 25. The lubricating oil 18 accumulated in the lower part of the accumulator container 25 is drawn in small amounts along with the gaseous refrigerant into the upper intake chamber 131T and the lower intake chamber 131S through the oil return holes 37 provided in the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S, respectively (described later).

(Characteristic configuration of a rotary compressor)
Next, the characteristic configuration of the rotary compressor 1 of the embodiment will be described. The characteristics of the embodiment include a structure in which the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S are connected to the compression section 12 by penetrating the bottom shell 10c of the compressor body container 10 from inside the accumulator shell 26, and a structure having a first refrigerant supply path 143T that supplies gaseous refrigerant supplied from the first refrigerant supply pipe 31T to the compression section 12, and a second refrigerant supply path 143S that supplies gaseous refrigerant supplied from the second refrigerant supply pipe 31S to the compression section 12.

Figure 4 is a cross-sectional perspective view illustrating the shapes of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S in the embodiment. Figure 5 is a longitudinal cross-sectional view illustrating the shapes of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S in the embodiment. Figure 6 is a transverse cross-sectional view illustrating the shapes of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S in the embodiment. Figure 7 is a longitudinal cross-sectional view showing the connection structure of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S in the embodiment.

As shown in Figures 4, 5, and 6, the first refrigerant supply pipe 31T has a straight pipe section 32T that extends linearly along the vertical direction (axial direction of the rotation axis 15) of the compression section 12 from the bottom 10e of the bottom shell 10c to the compression section 12, and a curved pipe section 33T that is bent upward in a roughly U-shape from the lower end of the straight pipe section 32T. The curved pipe section 33T of the first refrigerant supply pipe 31T is bent on the same plane as the plane along the longitudinal direction of the straight pipe section 32T (see Figures 5 and 6). The upper end 32Ta of the straight pipe section 32T of the first refrigerant supply pipe 31T is connected to the upper connection passage 147 of the lower cylinder 121S. The upper end 33Ta of the curved pipe section 33T of the first refrigerant supply pipe 31T extends upward from the lower end 27a of the accumulator suction pipe 27, which is located inside the accumulator shell 26, and opens into the inside of the accumulator shell 26.

Similarly, the second refrigerant supply pipe 31S has a straight pipe section 32S that extends linearly along the vertical direction of the compression section 12 from the bottom 10e of the bottom shell 10c to the compression section 12, and a curved pipe section 33S that is bent upward in a roughly U-shape from the lower end of the straight pipe section 32S. The curved pipe section 33S of the second refrigerant supply pipe 31S is bent from a plane along the longitudinal direction of the straight pipe section 32S toward another plane parallel to this plane, and is also bent upward on this other plane (see Figures 5 and 6). The upper end 32Sa of the straight pipe section 32S of the second refrigerant supply pipe 31S is connected to the lower connection passage 148 of the lower end plate 160S. The upper end 33Sa of the curved pipe section 33S of the second refrigerant supply pipe 31S extends upward from the lower end 27a of the accumulator suction pipe 27 which is located inside the accumulator shell 26, and opens into the inside of the accumulator shell 26.

The first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S are positioned at the same height in the vertical direction of the rotary compressor 1 (axis direction of the rotation axis 15). This prevents a large amount of liquid refrigerant from flowing into the refrigerant supply pipe with a lower opening height. Furthermore, since the upper ends 33Ta of the curved section 33T of the first refrigerant supply pipe 31T and the upper end 33Sa of the curved section 33S of the second refrigerant supply pipe 31S extend above the lower end 27a of the accumulator suction pipe 27, it prevents liquid refrigerant flowing into the accumulator container 25 from flowing directly into the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S.

As shown in Figures 4 and 6, the straight section 32T of the first refrigerant supply pipe 31T and the straight section 32S of the second refrigerant supply pipe 31S are arranged adjacent to each other in the radial direction of the accumulator shell 26. In other words, the straight section 32T of the first refrigerant supply pipe 31T and the straight section 32S of the second refrigerant supply pipe 31S are arranged side by side in a direction perpendicular to the rotation axis 15.

As shown in Figures 5 and 6, the curved section 33S of the second refrigerant supply pipe 31S is bent away from the curved section 33T of the first refrigerant supply pipe 31T from the lower end of the straight section 32S, and extends parallel to the curved section 33T of the first refrigerant supply pipe 31T. Therefore, as shown in Figure 6, when viewed from the vertical direction of the compression section 12 (the axial direction of the rotation axis 15), the direction in which the curved section 33T of the first refrigerant supply pipe 31T and the curved section 33S of the second refrigerant supply pipe 31S are aligned is perpendicular to the direction in which the straight section 32T of the first refrigerant supply pipe 31T and the straight section 32S of the second refrigerant supply pipe 31S are aligned. As described above, the bending of the second refrigerant supply pipe 31S results in the total length of the first refrigerant supply pipe 31T and the total length of the second refrigerant supply pipe 31S being approximately equal.

Furthermore, the straight section 32T of the first refrigerant supply pipe 31T is positioned outside the lower end plate 160S without penetrating it. Therefore, by forming a protruding portion on the lower end plate 160S to create a through-hole for the first refrigerant supply pipe 31T, it is possible to prevent the compression section 12 from becoming larger in the radial direction of the compressor body container 10. In addition, the increase in material costs associated with forming the protruding portion on the lower end plate 160S is suppressed, and the process of machining the through-hole in the lower end plate 160S is eliminated, thus suppressing the increase in manufacturing costs of the compression section 12.

As shown in Figure 7, the upper connecting passage 147 of the lower cylinder 121S is provided with a first sealing member 34T that seals the space between the inner circumference of the upper connecting passage 147 and the outer circumference of the first refrigerant supply pipe 31T. The lower connecting passage 148 of the lower end plate 160S is provided with a second sealing member 34S that seals the space between the inner circumference of the lower connecting passage 148 and the outer circumference of the second refrigerant supply pipe 31S. For example, O-rings made of resin or metal materials can be used as the first sealing member 34T and the second sealing member 34S.

Furthermore, in this embodiment, as described above, the first refrigerant supply pipe 31T is positioned outside the lower end plate 160S, and the upper connection passage 147 to which the upper end 32Ta of the first refrigerant supply pipe 31T is connected, and the lower connection passage 148 to which the upper end 32Sa of the second refrigerant supply pipe 31S is connected, are positioned at different locations with respect to the vertical direction of the compression section 12. This prevents, for example, the enlargement of the lower end plate 160S and the resulting enlargement of the compression section 12 that would occur if the first sealing member 34T and the second sealing member 34S were aligned radially on the lower end plate 160S, as would happen if the upper connection passage 147 and the lower connection passage 148 were aligned radially on the lower end plate 160S.

The first refrigerant supply pipe 31T is passed through the through hole 10f in the bottom 10e of the bottom shell 10c and is located inside the accumulator shell 26. It is joined to the through hole 10f from the lower surface of the bottom 10e of the bottom shell 10c by a weld W. Similarly, the second refrigerant supply pipe 31S is passed through the through hole 10f in the bottom 10e of the bottom shell 10c and is located inside the accumulator shell 26. It is joined to the through hole 10f from the lower surface of the bottom 10e of the bottom shell 10c by a weld W.

As shown in Figure 3, the compression section 12 has a first refrigerant supply path 143T that supplies gaseous refrigerant from the first refrigerant supply pipe 31T to the upper suction chamber 131T of the upper cylinder 121T. The compression section 12 also has a second refrigerant supply path 143S that supplies gaseous refrigerant from the second refrigerant supply pipe 31S to the lower suction chamber 131S of the lower cylinder 121S. Thus, the compression section 12 has two independent refrigerant supply paths: the first refrigerant supply path 143T and the second refrigerant supply path 143S.

The first refrigerant supply path 143T includes an upper compression intake passage 144 formed in the upper cylinder 121T, a connecting passage 145 formed in the intermediate partition plate 140, and an upper connection passage 147 formed in the lower cylinder 121S. The second refrigerant supply path 143S includes a lower compression intake passage 146 formed in the lower cylinder 121S and a lower connection passage 148 formed in the lower end plate 160S.

Furthermore, the first refrigerant supply path 143T includes a first linear path 143a formed along the vertical direction of the compression section 12, from the upper connection path 147 of the lower cylinder 121S to the upper compression section intake path 144 of the upper cylinder 121T. The second refrigerant supply path 143S includes a second linear path 143b formed along the vertical direction of the compression section 12, from the lower connection path 148 of the lower end plate 160S to the lower compression section intake path 146 of the lower cylinder 121S. This allows for the simple formation of the first refrigerant supply path 143T and the second refrigerant supply path 143S, improving their machinability and enabling the radial miniaturization of the compression section 12 having the first and second refrigerant supply paths 143T and 143S. In addition, in the compression section 12, the first linear path 143a and the second linear path 143b are arranged side-by-side in a direction perpendicular to the rotation axis 15.

Figure 8A is a plan view of the upper cylinder 121T in the embodiment, viewed from above. Figure 8B is a plan view of the upper cylinder 121T in the embodiment, viewed from below. As shown in Figures 3 and 8A and 8B, the upper compression intake passage 144 of the upper cylinder 121T is formed as a groove opening to the lower end surface 121Tb of the upper cylinder 121T, which is in contact with the intermediate partition plate 140. The upper compression intake passage 144 has a first flow path 144a connected to the upper intake chamber 131T and a second flow path 144b connected to the communication passage 145 of the intermediate partition plate 140. The first flow path 144a extends radially along the upper cylinder 121T from the second flow path 144b to the inner circumferential surface of the upper cylinder 121T.

Figure 9A is a plan view of the lower cylinder 121S in the embodiment, viewed from above. Figure 9B is a plan view of the lower cylinder 121S in the embodiment, viewed from below. As shown in Figures 3 and 9A and 9B, the upper connecting passage 147 of the lower cylinder 121S is provided in the protruding portion 122S and is formed to penetrate the lower cylinder 121S in the thickness direction (vertical direction of the compression portion 12). The lower compression portion intake passage 146 of the lower cylinder 121S has a first passage 146a connected to the lower intake chamber 131S and a second passage 146b connected to the lower connecting passage 148 of the lower end plate 160S.

The first passage 146a and the second passage 146b of the lower compression intake passage 146 are formed in a groove shape that opens to the upper end surface 121Sa of the lower cylinder 121TS, which is in contact with the lower end plate 160S. The first passage 146a extends radially along the lower cylinder 121S from the second passage 146b to the inner circumferential surface of the lower cylinder 121S.

Furthermore, in the lower cylinder 121S, the upper connecting passage 147 and the lower compression intake passage 146 are arranged side by side in a direction perpendicular to the rotation axis 15, that is, in the radial direction of the lower cylinder 121S, with the upper connecting passage 147 located radially outside the lower cylinder 121S relative to the lower compression intake passage 146. This allows the upper compression intake passage 144 and the lower compression intake passage 146 to overlap when the compression section 12 is viewed from the axial direction of the rotation axis 15. In other words, the upper compression intake passage 144 and the lower compression intake passage 146 are formed such that the position of the upper compression intake passage 144 with respect to the circumferential direction of the inner surface of the upper cylinder 121T (circumferential direction of the rotation axis 15) and the position of the lower compression intake passage 146 with respect to the circumferential direction of the inner surface of the lower cylinder 121S (circumferential direction of the rotation axis 15) are the same. In this way, by aligning the positions of the upper compression intake passage 144 and the lower compression intake passage 146 in the circumferential direction of the rotating shaft 15, the rotation angles at which the upper piston 125T and the lower piston 125S are positioned when gaseous refrigerant intake begins and ends in the circumferential direction of the inner surfaces of the upper cylinder 121T and the lower cylinder 121S can be aligned in the upper intake chamber 131T and the lower intake chamber 131S.

Figure 10 is a plan view of the intermediate partition plate 140 in the embodiment, viewed from above. As shown in Figure 3, the intermediate partition plate 140 has an upper end surface 140a that contacts the upper cylinder 121T and a lower end surface 140b that contacts the lower cylinder 121S. As shown in Figures 3 and 10, the intermediate partition plate 140 has a protruding portion 141 that extends from a part of its circular outer circumference, and a connecting passage 145 is formed in the thickness direction of the intermediate partition plate 140, penetrating through the protruding portion 141.

The upper end surface 140a of the intermediate partition plate 140 contacts the upper cylinder 121T, forming the lower flow path wall of the first flow path 144a in the upper compression intake passage 144.

Figure 11 is a plan view of the lower end plate 160S in the embodiment, viewed from below. As shown in Figures 3 and 11, the upper end surface 160Sa of the lower end plate 160S contacts the lower cylinder 121S, forming the lower flow path wall of the first flow path 146a in the lower compression intake passage 146.

Figure 12 is a plan view of the lower end plate cover 170S in the embodiment, viewed from below. As shown in Figures 3 and 12, a U-shaped notch 171 is formed on the outer periphery of the lower end plate cover 170S to avoid interference with the second refrigerant supply pipe 31S connected to the lower end plate 160S. Therefore, when the second refrigerant supply pipe 31S is connected to the compression section 12, it passes through the notch 171 and connects to the lower connection passage 148 of the lower end plate 160S.

As described above, the upper compression section suction passage 144, connecting passage 145, and upper connection passage 147 (hereinafter also referred to as "each passage") that form the first refrigerant supply passage 143T are formed in the respective protruding sections 122T, 141, and 122S. This allows for a larger flow path cross-sectional area of each passage by utilizing the respective protruding sections 122T, 141, and 122S. As a result, the flow resistance of the gaseous refrigerant flowing through the first refrigerant supply passage 143T is reduced, increasing the compression efficiency of the gaseous refrigerant, while the mechanical strength of the parts where each passage is formed can be adequately ensured by the respective protruding sections 122T, 141, and 122S.

Furthermore, in the above-described embodiment, as shown in Figure 7, the connection portion between the upper end 32Ta of the first refrigerant supply pipe 31T and the upper connection passage 147 was sealed using the first sealing member 34T, and the connection portion between the upper end 32Sa of the second refrigerant supply pipe 31S and the lower connection passage 148 was sealed using the second sealing member 34S. However, the structure is not limited to the use of the first sealing member 34T and the second sealing member 34S. Figure 13 is a longitudinal cross-sectional view showing another example of the connection structure of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S in the embodiment.

As shown in Figure 13, the upper end 32Ta of the first refrigerant supply pipe 31T is formed in a tapered shape with a gradually decreasing outer diameter. The upper connecting passage 147 of the lower cylinder 121S is formed in a tapered shape with a gradually decreasing inner diameter. The upper end 32Ta of the first refrigerant supply pipe 31T is connected by being press-fitted into the upper connecting passage 147. Similarly, the upper end 32Sa of the second refrigerant supply pipe 31S is formed in a tapered shape with a gradually decreasing outer diameter. The lower connecting passage 148 of the lower end plate 160S is formed in a tapered shape with a gradually decreasing inner diameter. The upper end 32Sa of the second refrigerant supply pipe 31S is connected by being press-fitted into the lower connecting passage 148. By press-fitting the first refrigerant supply pipe 31T into the upper connection passage 147 in this manner, the space between the inner circumference of the upper connection passage 147 and the outer circumference of the first refrigerant supply pipe 31T is sealed. Therefore, the use of the first sealing member 34T and the machining of a groove for fixing the first sealing member 34T on the inner surface of the upper connection passage 147 are eliminated. The same applies when press-fitting the second refrigerant supply pipe 31S into the lower connection passage 148.

(Method of manufacturing a rotary compressor)
In the manufacturing method of the rotary compressor 1 configured as described above, the step of assembling the refrigerant supply pipe 31 inside the accumulator shell 26 will be explained. Figure 14 is a longitudinal cross-sectional view illustrating the manufacturing method of the rotary compressor 1 of the embodiment. Figure 15 is a longitudinal cross-sectional view illustrating another example of the manufacturing method of the rotary compressor 1 of the embodiment.

As shown in Figure 14, the motor 11 and compression unit 12 are assembled inside the main shell 10a. The upper end 32Ta of the first refrigerant supply pipe 31T, which is joined through the bottom 10e of the bottom shell 10c, is connected to the upper connection passage 147 of the compression unit 12. The upper end 32Sa of the second refrigerant supply pipe 31S is connected to the lower connection passage 148 of the compression unit 12. The opening side 10d of the bottom shell 10c is joined to the main shell 10a to manufacture the intermediate body. Subsequently, the opening side 26a of the accumulator shell 26 is welded to the bottom shell 10c, which is provided with the first and second refrigerant supply pipes 31T and 31S connected to the compression unit 12 and joined to the main shell 10a. The accumulator suction pipe 27 may be assembled after the accumulator shell 26 is joined to the bottom shell 10c.

Alternatively, as shown in Figure 15, an intermediate body is manufactured by welding the opening side 26a of the accumulator shell 26 to a bottom shell 10c, which has the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S joined to it, passing through the bottom 10e. Another intermediate body is manufactured by assembling the motor 11 and the compression unit 12 inside the main shell 10a. Then, the upper end 32Ta of the first refrigerant supply pipe 31T, which is provided passing through the bottom shell 10c to which the accumulator shell 26 is joined, is connected to the upper connection passage 147 of the compression unit 12, and the upper end 32Sa of the second refrigerant supply pipe 31S is connected to the lower connection passage 148 of the compression unit 12. At the same time, the opening side 10d of the bottom shell 10c is welded to the main shell 10a.

(Effects of the example)
As described above, the rotary compressor 1 of the embodiment is provided with a first refrigerant supply pipe 31T that supplies gaseous refrigerant from the accumulator shell 26 to the upper cylinder 121T, and a second refrigerant supply pipe 31S that supplies gaseous refrigerant from the accumulator shell 26 to the lower cylinder 121S. The first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S are connected to the compression section 12 by passing through the bottom shell 10c of the compressor body container 10 from inside the accumulator shell 26. The compression section 12 is provided with a first refrigerant supply path 143T that supplies gaseous refrigerant from a first refrigerant supply pipe 31T to the upper suction chamber 131T of the upper cylinder 121T, and a second refrigerant supply path 143S that supplies refrigerant from a second refrigerant supply pipe 31S to the lower suction chamber 131S of the lower cylinder 121S. The first refrigerant supply pipe 31T is connected to the first refrigerant supply path 143T, and the second refrigerant supply pipe 31S is connected to the second refrigerant supply path 143S. In this way, gaseous refrigerant is supplied from inside the compressor body container 10 to the compression section 12 through the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S from inside the accumulator shell 26. As a result, the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S are not located outside the compressor body container 10, thus enabling miniaturization of the compressor body container 10 in the radial direction.

Furthermore, in the compression section 12 of the rotary compressor 1 of this embodiment, the first refrigerant supply path 143T includes a first linear path 143a formed along the vertical direction of the compression section 12 from the upper connection path 147 of the lower cylinder 121S to the upper compression section intake path 144 of the upper cylinder 121T, and the second refrigerant supply path 143S includes a second linear path 143b formed along the vertical direction of the compression section 12 from the lower connection path 148 of the lower end plate 160S to the lower compression section intake path 146 of the lower cylinder 121S. This simplifies the design of the first refrigerant supply path 143T and the second refrigerant supply path 143S, improves the processability of the first and second refrigerant supply paths 143T and 143S, and allows for miniaturization of the compression section 12 having the first and second refrigerant supply paths 143T and 143S.

Furthermore, in the rotary compressor 1 of this embodiment, the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S extend linearly from the bottom shell 10c to the compression section 12, along the vertical direction of the compression section 12. This facilitates the routing of the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S within the compressor body container 10, and improves the workability of connecting the first refrigerant supply pipe 31T and the second refrigerant supply pipe 31S to the compression section 12.

Furthermore, in the rotary compressor 1 of this embodiment, the first refrigerant supply path 143T in the compression section 12 is formed in the protruding portion 122T of the upper cylinder 121T, the protruding portion 141 of the intermediate partition plate 140, and the protruding portion 122S of the lower cylinder 121S. This ensures adequate mechanical strength in the portions where each path of the first refrigerant supply path 143T is formed, making it possible to create a larger flow path cross-sectional area for each path. This reduces the flow resistance of the first refrigerant supply path 143T and improves the compression efficiency of the gaseous refrigerant.

Furthermore, in this embodiment, the lower cylinder 121S of the compression section 12 has an upper connection passage 147 for the first refrigerant supply path 143T and a lower compression section intake passage 146 for the second refrigerant supply path 143S, arranged side by side in a direction perpendicular to the rotation axis 15 of the motor 11. This allows the upper compression section intake passage 144 and the lower compression section intake passage 146 to overlap when the compression section 12 is viewed from the axial direction of the rotation axis 15.

Furthermore, in the rotary compressor 1 of this embodiment, the upper compression intake passage 144 and the lower compression intake passage 146 are arranged to overlap when the compression section 12 is viewed from the axial direction of the rotation shaft 15 of the motor 11. This ensures that the position of the upper compression intake passage 144 relative to the circumferential direction of the inner surface of the upper cylinder 121T is the same as the position of the lower compression intake passage 146 relative to the circumferential direction of the inner surface of the lower cylinder 121S. This allows the rotational angles at which the upper piston 125T and lower piston 125S are positioned when gaseous refrigerant intake begins and ends in the circumferential direction of the inner surfaces of the upper cylinder 121T and lower cylinder 121S to be aligned between the upper intake chamber 131T and the lower intake chamber 131S.

Furthermore, in the rotary compressor 1 of this embodiment, the first refrigerant supply pipe 31T is positioned on the outside of the lower end plate 160S. This prevents the compression section 12 from becoming larger in the radial direction of the compressor body container 10 by forming a through-hole through which the first refrigerant supply pipe 31T passes. In addition, it suppresses the increase in material costs associated with forming a protrusion on the lower end plate 160S and eliminates the process of machining the through-hole in the lower end plate 160S, thus suppressing the increase in manufacturing costs of the compression section 12.

1. Rotary compressor (closed-type compressor)
10 Compressor body container 10a Main shell 10c Bottom shell 11 Motor 12 Compression section 25 Accumulator container 26 Accumulator shell 26a Opening side 31T First refrigerant supply pipe 31S Second refrigerant supply pipe 32Ta Upper end (one end)
32Sa Upper end (one end)
34T First sealing member 34S Second sealing member 121T Upper cylinder 121S Lower cylinder 122T Protruding part 122S Protruding part 131T Upper intake chamber (upper compression chamber)
131S Lower intake chamber (lower compression chamber)
140 Intermediate partition plate (partition plate)
140a Upper end surface (end surface)
141 Protruding section 143T First refrigerant supply path 143S Second refrigerant supply path 143a First straight path 143b Second straight path 144 Upper compression section intake path 145 Connecting passage 146 Lower compression section intake path 147 Upper connecting path 148 Lower connecting path 160S Lower end plate 160Sa Upper end surface (end surface)
170S Lower end plate cover

Claims (12)

A compression unit having an upper cylinder and a lower cylinder that compress the inhaled gaseous refrigerant and discharge it into the compressor unit is housed inside a vertical cylindrical compressor body container, and a motor that drives the compression unit is also housed inside.
A sealed compressor is provided with an accumulator container located below the compressor body container, which separates the inhaled refrigerant into gaseous and liquid refrigerants and supplies the gaseous refrigerant to the compression section.
The compressor body container comprises a cylindrical main shell and a bottom shell joined to the lower end of the main shell.
The accumulator container comprises a cup-shaped accumulator shell and an accumulator suction pipe for drawing refrigerant into the interior of the accumulator shell , with the opening side of the accumulator shell joined to the compressor body container.
The accumulator suction tube penetrates the accumulator shell and extends its end into the interior of the accumulator shell.
Inside the accumulator shell, there is a first refrigerant supply pipe that supplies gaseous refrigerant from the accumulator shell to the upper cylinder of the compression unit, and a second refrigerant supply pipe that supplies gaseous refrigerant from the accumulator shell to the lower cylinder of the compression unit.
The first refrigerant supply pipe and the second refrigerant supply pipe are connected to the compression section by passing through the bottom shell of the compressor body container from inside the accumulator shell.
The compression section is provided with a first refrigerant supply path that supplies gaseous refrigerant from the first refrigerant supply pipe to the upper compression chamber of the upper cylinder, and a second refrigerant supply path that supplies refrigerant from the second refrigerant supply pipe to the lower compression chamber of the lower cylinder.
The first refrigerant supply path is connected to the first refrigerant supply pipe, and the second refrigerant supply path is connected to the second refrigerant supply pipe .
Inside the accumulator shell, each of the first refrigerant supply pipe and the second refrigerant supply pipe has a straight pipe section extending linearly in the vertical direction of the compression section, and a curved pipe section that is curved upward from the lower end of the straight pipe section.
A sealed compressor in which the upper ends of the curved sections of the first refrigerant supply pipe and the second refrigerant supply pipe are located above the end of the accumulator suction pipe . The upper ends of the curved sections of the first refrigerant supply pipe and the second refrigerant supply pipe are located at the same height in the vertical direction.
A sealed compressor according to claim 1. The curved portion of the second refrigerant supply pipe is bent in a direction that intersects the vertical direction, and the total length of the second refrigerant supply pipe is equal to the total length of the first refrigerant supply pipe.
A sealed compressor according to claim 1 or 2. At least one of the first refrigerant supply pipe and the second refrigerant supply pipe has an oil return hole for returning the lubricating oil that accumulates in the lower part of the accumulator container to the compression section together with the refrigerant.
A sealed compressor according to any one of claims 1 to 3. The compression section includes a partition plate positioned between the upper cylinder and the lower cylinder, and a lower end plate that closes the lower end of the lower cylinder.
The first refrigerant supply path comprises an upper compression intake passage formed in the upper cylinder, a connecting passage formed in the partition plate, and an upper connecting passage formed in the lower cylinder, with the first refrigerant supply pipe connected to the upper connecting passage.
The second refrigerant supply path comprises a lower compression intake passage formed in the lower cylinder and a lower connection passage formed in the lower end plate, and the second refrigerant supply pipe is connected to the lower connection passage.
A sealed compressor according to any one of claims 1 to 4 . The first refrigerant supply path includes a first straight path formed along the vertical direction of the compression section from the upper connection passage of the lower cylinder to the upper compression section intake passage of the upper cylinder,
The second refrigerant supply path includes a second straight path formed along the vertical direction of the compression section from the lower connection passage of the lower end plate to the lower compression section intake passage of the lower cylinder.
The sealed compressor according to claim 5 . The upper cylinder, the partition plate, and the lower cylinder each have a protruding portion that extends from a part of their outer circumference.
A portion of at least one of the first refrigerant supply path and the second refrigerant supply path is formed in each protruding portion.
A sealed compressor according to any one of claims 5 to 6 . In the lower cylinder, the upper connecting passage of the first refrigerant supply path and the lower compression section suction passage of the second refrigerant supply path are arranged side by side in a direction perpendicular to the rotation axis of the motor.
A sealed compressor according to any one of claims 5 to 7 . When the compression section is viewed from the axial direction of the motor's rotating shaft, the upper compression section intake passage and the lower compression section intake passage are arranged to overlap.
The sealed compressor according to claim 8 . The first refrigerant supply pipe is positioned on the outside of the lower end plate.
A sealed compressor according to any one of claims 5 to 9 . The end face of the partition plate forms part of the upper compression intake passage.
A sealed compressor according to any one of claims 5 to 10 . The end face of the lower end plate forms part of the intake passage of the lower compression section.
A sealed compressor according to any one of claims 5 to 11 .