JP7534859B2 - Horizontal rotary compressor - Google Patents

Description

The present invention relates to a horizontal rotary compressor.

The compressor (horizontal rotary compressor) described in Patent Document 1 is known as an example of a horizontal rotary compressor. In the compressor described in Patent Document 1, the inside of the sealed container (housing) is partitioned by a partition member into an oil storage space in which a rotary type compression mechanism is located and an electric motor side space in which an electric motor is located. The compression mechanism is composed of a first compression mechanism and a second compression mechanism provided on both the left and right sides of an intermediate partition plate. Each of the first compression mechanism and the second compression mechanism has a cylinder chamber, an eccentric roller (piston member) that rotates eccentrically within the cylinder chamber, and a blade (vane) that comes into contact with the eccentric roller to divide the cylinder chamber into a high pressure side and a low pressure side.

In the compressor described in Patent Document 1, the refrigerant (high-pressure refrigerant) compressed in the first compression mechanism and the second compression mechanism is discharged into the motor-side space, filling the motor-side space, and is also guided to the oil storage space, filling the oil storage space, and the high-pressure refrigerant filling the oil storage space is discharged to the outside from a discharge refrigerant pipe. In addition, the compressor described in Patent Document 1 has an oil supply passage that sucks up the lubricating oil stored in the lower part of the oil storage space and supplies it to each sliding part of the first compression mechanism and the second compression mechanism.

JP 2004-60533 A

In the compressor described in Patent Document 1, the blades of the first compression mechanism and the blades of the second compression mechanism are in contact with the corresponding eccentric rollers while simply being elastically pressed against them. Therefore, depending on the operating state of the compressor, the pressing force of the blades of the first compression mechanism and the blades of the second compression mechanism against the corresponding eccentric rollers may be insufficient, and the blades of the first compression mechanism and the blades of the second compression mechanism may separate from the corresponding eccentric rollers.

In the compressor described in Patent Document 1, the blades of the first compression mechanism and the blades of the second compression mechanism are immersed in the lubricating oil stored in the lower part of the oil storage space. The blades of the first compression mechanism and the blades of the second compression mechanism reciprocate with the eccentric rotation of the corresponding eccentric roller, so that the lubricating oil stored in the lower part of the oil storage space is agitated. When the stored lubricating oil is agitated, the amount of lubricating oil discharged from the discharge refrigerant pipe together with the high-pressure refrigerant may increase, or the suction of the lubricating oil by the oil supply passage, and thus the supply of lubricating oil to each sliding part of the first compression mechanism and the second compression mechanism, may become unstable.

The present invention aims to provide a horizontal rotary compressor that can prevent the vanes from separating from the piston member and prevent the agitation of the lubricating oil caused by the reciprocating motion of the vanes.

According to one aspect of the present invention, there is provided a horizontal rotary compressor. The horizontal rotary compressor includes a horizontally extending rotary shaft rotatably supported by a bearing, and a rotary type compression mechanism driven by the rotary shaft, inside a housing. The compression mechanism includes a first compression mechanism and a second compression mechanism arranged on both sides of a partition member, and a lubricating oil reservoir for storing lubricating oil is provided on the inner bottom of the housing. Each of the first compression mechanism and the second compression mechanism includes a cylinder chamber, a piston member that rotates eccentrically in the cylinder chamber as the rotary shaft rotates, a vane whose tip portion contacts the piston member to divide the cylinder chamber into a suction chamber and a compression chamber, a biasing member that biases the vane toward the piston member, and a back pressure chamber into which lubricating oil is introduced to apply pressure to the back surface of the vane . The piston member of the first compression mechanism and the piston member of the second compression mechanism eccentrically rotate with a phase difference of 180°, and the back pressure chamber of the first compression mechanism and the back pressure chamber of the second compression mechanism communicate with each other through a communication hole formed in the partition member. The lubricating oil reservoir has a main reservoir for storing most of the lubricating oil, an auxiliary reservoir formed between an outer periphery of the compression mechanism and an inner periphery of the housing for storing lubricating oil to be introduced into the back pressure chamber of the first compression mechanism and the back pressure chamber of the second compression mechanism, and a lubricating oil flow path communicating the main reservoir and the auxiliary reservoir, and the lubricating oil flow path includes a narrow portion having a flow path cross-sectional area smaller than the flow path cross-sectional area of the auxiliary reservoir.

According to one aspect of the present invention, it is possible to provide a horizontal rotary compressor that can suppress the separation of the vanes from the piston member and the agitation of the lubricating oil caused by the reciprocating motion of the vanes.

1 is a cross-sectional view showing a schematic configuration of a horizontal rotary compressor according to an embodiment of the present invention. 2A is an enlarged view of a compression mechanism 30 and its surroundings in the horizontal rotary compressor, FIG. 2A is an enlarged view of a main part of FIG. 1, FIG. 2B is an enlarged view of an X part of FIG. 2A, and FIG. 2C is an enlarged view of a Y part of FIG. 2 is a cross-sectional view taken along line AA of FIG. 1. This is a cross-sectional view taken along line B-B of FIG. This is a cross-sectional view taken along the line CC of FIG. This is a cross-sectional view taken along the line D-D of FIG. 2 is a cross-sectional view taken along the line E-E of FIG. 1. This is a cross-sectional view taken along the line FF in FIG. FIG. 2 is a diagram showing a flow of a refrigerant (gas) in the horizontal electric compressor. FIG. 4 is a diagram showing a flow of lubricating oil in the horizontal electric compressor.

The following describes an embodiment of the present invention with reference to the attached drawings.

Figure 1 is a cross-sectional view showing the schematic configuration of a horizontal rotary compressor according to one embodiment of the present invention. The horizontal rotary compressor (hereinafter simply referred to as "compressor") 100 according to the embodiment has a housing 110. The housing 110 includes a cylindrical center housing 111, a bottomed cylindrical front housing 112 whose open end is joined to the front end (left end in Figure 1) of the center housing 111, and a bottomed cylindrical rear housing 113 whose open end is joined to the rear end (right end in Figure 1) of the center housing 111.

The peripheral walls of the center housing 111, the front housing 112, and the rear housing 113 form a horizontally elongated cylindrical housing body 110a, the bottom wall of the front housing 112 forms a first housing end wall 110b that closes one (front) open end of the housing body 110a, and the bottom wall of the rear housing 113 forms a second housing end wall 110c that closes the other (rear) open end of the housing body 110a.

The interior of the housing 110 is divided by a partition 114 provided on the center housing 111 into a first storage chamber 115 on the first housing end wall portion 110b side (front side) and a second storage chamber 116 on the second housing end wall portion 110c side (rear side).

The inner bottom of the housing 110 is provided with a lubricant oil reservoir 150 in which the lubricant oil O is stored. More specifically, in this embodiment, the lubricant oil reservoir 150 is provided in the lower part of the second storage chamber 116. The lubricant oil reservoir 150 will be described later.

A boss portion 114a is formed in the radial center of the partition portion 114, protruding toward the first storage chamber 115. In addition, a first shaft hole 114b is formed in the partition portion 114, penetrating from the tip surface of the boss portion 114a to the surface on the second storage chamber 116 side.

The compressor 100 has a rotating shaft 200 inside the housing 110. In the housing 110, the rotating shaft 200 extends horizontally (front-rear direction), and the axial middle portion is inserted into the first shaft hole 114b and supported for free rotation. That is, the rotating shaft 200 extends through the partition wall 114, and one end (front end) of the rotating shaft 200 is located in the first storage chamber 115, and the other end (rear end) of the rotating shaft 200 is located in the second storage chamber 116. In addition, a first minute gap (clearance) is formed between the inner peripheral surface of the first shaft hole 114b and the outer peripheral surface of the rotating shaft 200. This first minute gap is set so that it can be sealed by the lubricating oil O.

The first chamber 115 accommodates the motor unit 10 that rotates the rotating shaft 200. That is, the motor unit 10 is provided at one end (front end) of the rotating shaft 200 within the housing 110. The first chamber 115 also communicates with an external refrigerant circuit (low pressure side) (not shown) via a refrigerant inlet hole 117 formed in the front housing 112. The refrigerant inlet hole 117 is provided at a position opposite the partition wall 114 across the motor unit 10 in the axial direction of the rotating shaft 200, and at a position corresponding to the rotating shaft 200 in the vertical direction (at approximately the same height as the rotating shaft 200).

The motor section 10 includes a stator 11 and a rotor 12.

The stator 11 is fixed to the inner circumferential surface of the housing 110. Specifically, the stator 11 is fixed to the inner circumferential surface of a portion of the center housing 111 closer to the front housing 112 than the partition wall portion 114. The stator 11 has a stator core 11a formed in a cylindrical shape from a magnetic material, and a stator coil 11b wound, for example, in a concentrated winding manner around the stator core 11a (the teeth portion).

The rotor 12 is disposed radially inside the stator 11 with a specified gap between it and the stator 11. A permanent magnet is incorporated in the rotor 12. The rotor 12 is formed in a cylindrical shape and is fixed to the rotating shaft 200 with one end (front end) of the rotating shaft 200 inserted into the hollow portion of the rotor 12.

The electric motor unit 10 is configured so that power is supplied to the stator 11 (stator coil 11b) via the airtight terminal unit 20 provided on the front housing 112, causing the rotor 12 to rotate, thereby rotating the rotating shaft 200.

The second chamber 116 contains a rotary type compression mechanism 30 driven by the rotating shaft 200. That is, the compression mechanism 30 is provided on the other end (rear end) side of the rotating shaft 200 inside the housing 110. The second chamber 116 also communicates with the external refrigerant circuit (the high pressure side) via a refrigerant outlet hole 118 formed in the rear housing 113. The refrigerant outlet hole 118 is provided at a position closer to the partition wall 114 than the discharge hole 52a (described later) in the axial direction of the rotating shaft 200, and at a position corresponding to the rotating shaft 200 in the height direction, similar to the refrigerant inlet hole 117.

In this embodiment, the compression mechanism 30 is configured as a so-called "twin rotary compression mechanism". The compression mechanism 30 includes a first compression mechanism 30A and a second compression mechanism 30B arranged horizontally, and an intermediate partition plate (partition member) 50 is provided between the first compression mechanism 30A and the second compression mechanism 30B. In other words, the first compression mechanism 30A and the second compression mechanism 30B are arranged on both sides of the intermediate partition plate 50. The first compression mechanism 30A is arranged on the partition wall 114 side (i.e., the front side) of the intermediate partition plate 50, and the second compression mechanism 30B is arranged on the opposite side (i.e., the rear side) of the intermediate partition plate 50 from the partition wall 114 side. An insertion hole through which the rotary shaft 200 is inserted is formed in the radial center of the intermediate partition plate 50.

Figure 2 shows the compression mechanism section 30 and its surroundings. Figure 2(a) is an enlarged view of the main parts of Figure 1, Figure 2(b) is an enlarged view of part X of Figure 2(a), and Figure 2(c) is an enlarged view of part Y of Figure 2(a). Figure 3 is a cross-sectional view taken along line A-A of Figure 1 (partially omitted), and mainly shows the configuration of the first compression mechanism section 30A. Figure 4 is a cross-sectional view taken along line B-B of Figure 1 (partially omitted), and mainly shows the configuration of the second compression mechanism section 30B.

As shown in Figures 2 and 3, the first compression mechanism 30A includes a first cylinder 31A, a first piston member 34A, and a first vane 35A.

The first cylinder 31A has an outer diameter smaller than the inner diameter of the housing 110. A first annular space is formed between the outer periphery of the first cylinder 31A and the inner periphery of the housing 110. Here, as shown in FIG. 3, the first cylinder 31A has a first enlarged diameter portion 32A, which is partially enlarged in diameter, on the lower side, and the outer periphery of the first enlarged diameter portion 32A is close to the inner periphery of the housing 110. Therefore, a gap space narrower than other spaces in the first annular space is formed between the outer periphery of the first enlarged diameter portion 32A and the inner periphery of the housing 110. In the following, the space (gap space) formed between the outer periphery of the first enlarged diameter portion 32A and the inner periphery of the housing 110 in the first annular space is referred to as the "first gap portion G1".

One surface (front surface) of the first cylinder 31A is in close contact with the surface of the partition wall 114 on the second storage chamber 116 side, and the other surface (rear surface) of the first cylinder 31A is in close contact with one surface (front surface) of the intermediate partition plate 50. The first cylinder 31A also has a first cylinder chamber 33A with a circular cross section in the radial center.

The first piston member 34A is formed in an annular shape and is attached to the outer peripheral surface of the first eccentric portion 201 of the rotating shaft 200 located in the first cylinder chamber 33A of the first cylinder 31A. The first piston member 34A rotates eccentrically within the first cylinder chamber 33A as the rotating shaft 200 rotates.

The first vane 35A is accommodated in a first vane groove 36A formed in the first cylinder 31A. The first vane groove 36A is formed as a groove that opens to the lower part of the inner circumferential surface of the first cylinder chamber 33A and has a predetermined depth downward. The first vane 35A is accommodated in the first vane groove 36A so as to be movable in the direction of advancing into the first cylinder chamber 33A and in the direction of retreating from the first cylinder chamber 33A.

The first vane 35A is elastically biased by the first biasing member 37A housed in the first vane groove 36A in a direction advancing into the first cylinder chamber 33A, in other words, toward the first piston member 34A. In this embodiment, the first biasing member 37A is a compression coil spring and is disposed between the first vane 35A and the bottom of the first vane groove 36A. Specifically, one end (lower end) of the compression coil spring as the first biasing member 37A is fitted into the first mounting hole 38A formed in the bottom of the first vane groove 36A, and the other end (upper end) of the compression coil spring as the first biasing member 37A is pressed against the back surface of the first vane 35A.

The tip of the first vane 35A contacts the outer peripheral surface of the first piston member 34A to divide the first cylinder chamber 33A into a suction chamber (low pressure chamber) where the first suction port 42A opens, and a compression chamber (high pressure chamber) where the first discharge port 43A opens (see FIG. 3). In this embodiment, the first suction port 42A and the first discharge port 43A are located below the rotating shaft 200.

The space between the back surface of the first vane 35A in the first vane groove 36A and the bottom of the first vane groove 36A constitutes a first back pressure chamber 39A. The first back pressure chamber 39A is connected to the first gap portion G1 via a first lubricating oil introduction hole 40A that penetrates the bottom of the first mounting hole 38A. The first back pressure chamber 39A is configured to introduce lubricating oil through the first lubricating oil introduction hole 40A and apply pressure to the back surface of the first vane 35A, i.e., to apply back pressure to the first vane 35A.

2, in this embodiment, a first recess 114c is formed on the surface of the partition wall 114 facing the first storage chamber 115 so as to surround the boss portion 114a. The opening of the first recess 114c is closed by a first closing plate 121 that is in close contact with the surface of the partition wall 114 facing the first storage chamber 115, thereby forming a first discharge sound-absorbing chamber 41A partitioned from the first storage chamber 115. In other words, in this embodiment, the partition wall 114 is provided with the first discharge sound-absorbing chamber 41A. The first closing plate 121 has an outer diameter approximately equal to the inner diameter of the housing 110, and a through hole through which the boss portion 114a is inserted is formed in the center of the first closing plate 121. The first discharge muffler chamber 41A is connected to the first discharge port 43A (see FIG. 3) that opens into the compression chamber in the first cylinder chamber 33A through a first communication hole 114d formed in the partition wall 114.

The second compression mechanism 30B has a similar configuration to the first compression mechanism 30A. That is, as shown in FIG. 2 and FIG. 4, the second compression mechanism 30B includes a second cylinder 31B, a second piston member 34B, and a second vane 35B.

The second cylinder 31B, like the first cylinder 31A, has an outer diameter smaller than the inner diameter of the housing 110, and a second annular space is formed between the outer periphery of the second cylinder 31B and the inner periphery of the housing 110. Also, as shown in FIG. 4, the second cylinder 31B has a second enlarged diameter portion 32B, which is partially enlarged, on the lower side. The outer periphery of the second enlarged diameter portion 32B is close to the inner periphery of the housing 110, and a gap space narrower than other spaces in the second annular space is formed between the outer periphery of the second enlarged diameter portion 32B and the inner periphery of the housing 110. As in the case of the first compression mechanism portion 30A, the space (gap space) formed between the outer periphery of the second enlarged diameter portion 32B and the inner periphery of the housing 110 in the second annular space is referred to as the "second gap portion G2" below.

One surface (front surface) of the second cylinder 31B is in close contact with the other surface (rear surface) of the intermediate partition plate 50, and the other side surface (rear surface) of the second cylinder 31B is in close contact with one surface (front surface) of the discharge sound-absorbing chamber forming member 51. In addition, the second cylinder 31B has a second cylinder chamber 33B with a circular cross section in the radial center.

The second piston member 34B is formed in an annular shape and is attached to the outer circumferential surface of the second eccentric portion 202 of the rotating shaft 200 located in the second cylinder chamber 33B of the second cylinder 31B. The second piston member 34B rotates eccentrically within the second cylinder chamber 33B as the rotating shaft 200 rotates. Here, the second eccentric portion 202 is disposed 180° offset (having a phase difference of 180°) around the axis of the rotating shaft 200 relative to the first eccentric portion 201, and the first piston member 34A and the second piston member 34B rotate eccentrically with a phase difference of 180°.

The second vane 35B is accommodated in a second vane groove 36B formed in the second cylinder 31B. The second vane groove 36B is formed as a groove that opens to the lower part of the inner circumferential surface of the second cylinder chamber 33B and has a predetermined depth downward. The second vane 35B is accommodated in the second vane groove 36B so as to be movable in the direction of advancing into the second cylinder chamber 33B and in the direction of retreating from the second cylinder chamber 33B.

The second vane 35B is elastically biased by the second biasing member 37B housed in the second vane groove 36B in a direction advancing into the second cylinder chamber 33B, i.e., toward the second piston member 34B. The second biasing member 37B is a compression coil spring, similar to the first biasing member 37A, and is disposed between the second vane 35B and the bottom of the second vane groove 36B. Specifically, one end (lower end) of the compression coil spring as the second biasing member 37B is fitted into the second mounting hole 38B formed in the bottom of the second vane groove 36B, and the other end (upper end) of the compression coil spring as the second biasing member 37B is pressed against the back surface of the second vane 35B.

The tip of the second vane 35B abuts against the outer peripheral surface of the second piston member 34B to divide the second cylinder chamber 33B into a suction chamber (low pressure chamber) where the second suction port 42B opens, and a compression chamber (high pressure chamber) where the second discharge port 43B opens (see FIG. 4). In this embodiment, the second suction port 42B and the second discharge port 43B are located below the rotating shaft 200, similar to the first suction port 42A and the first discharge port 43A.

The space between the back surface of the second vane 35B in the second vane groove 36B and the bottom of the second vane groove 36B constitutes a second back pressure chamber 39B. The second back pressure chamber 39B is connected to the second gap portion G2 via a second lubricating oil introduction hole 40B that penetrates the bottom of the second mounting hole 38B. The second back pressure chamber 39B is configured to introduce lubricating oil O through the second lubricating oil introduction hole 40B and apply pressure to the back surface of the second vane 35B, i.e., to apply back pressure to the second vane 35B.

The second back pressure chamber 39B is connected to the first back pressure chamber 39A through a communication hole 50a formed in the intermediate partition plate 50. That is, in this embodiment, the first back pressure chamber 39A of the first compression mechanism section 30A and the second back pressure chamber 39B of the second compression mechanism section 30B are connected to each other through the communication hole 50a formed in the intermediate partition plate 50. Here, the opening area (flow path cross-sectional area) of the communication hole 50a is set to be larger than the flow path cross-sectional area of the first gap portion G1 and the flow path cross-sectional area of the second gap portion G2.

2, a second shaft hole 51a is formed in the radial center of the discharge silencing chamber forming member 51. The rear end of the rotating shaft 200 and its vicinity are rotatably inserted into the second shaft hole 51a. In other words, the rotating shaft 200 is rotatably supported by the first shaft hole 114b formed in the partition wall portion 114 and the second shaft hole 51a formed in the discharge silencing chamber forming member 51, and these first shaft hole 114b and second shaft hole 51a each constitute a bearing portion of the rotating shaft 200. As in the case of the first shaft hole 114b, a second minute gap (clearance) is formed between the inner peripheral surface of the second shaft hole 51a and the outer peripheral surface of the rotating shaft 200.

A second recess 51b is formed on the other surface of the discharge silencing chamber forming member 51, i.e., the surface opposite the second cylinder 31B side (rear surface), so as to surround the second axial hole 51a. The opening of the second recess 51b is closed by a second closing plate 52 that is in close contact with the other surface of the discharge silencing chamber forming member 51, thereby forming the second discharge silencing chamber 41B. The second discharge silencing chamber 41B is connected to a second discharge port 43B (see FIG. 4) that opens into the compression chamber in the second cylinder chamber 33B through a second communication hole 51c formed in the discharge silencing chamber forming member 51.

5 is a cross-sectional view of C-C in FIG. 1. As shown in FIG. 5, the discharge silencing chamber forming member 51 has an outer diameter smaller than the inner diameter of the housing 110, and a third annular space is formed between the outer periphery of the discharge silencing chamber forming member 51 and the inner periphery of the housing 110. In addition, the discharge silencing chamber forming member 51 has a third enlarged diameter portion 51d on the lower side, which is partially enlarged in diameter, similar to the first cylinder 31A and the second cylinder 31B. The outer periphery of the third enlarged diameter portion 51d is close to the inner periphery of the housing 110, and a gap space narrower than the other spaces in the third annular space is formed between the outer periphery of the third enlarged diameter portion 51d and the inner periphery of the housing 110. However, the circumferential length of the third enlarged diameter portion 51d is greater than the circumferential length of the first enlarged diameter portion 32A of the first cylinder 31A and the circumferential length of the second enlarged diameter portion 32B of the second cylinder 31B. Preferably, the third enlarged diameter portion 51d is set so that its upper end is located above the liquid level of the lubricating oil O stored in the inner bottom portion of the housing 110 (the lower portion of the second storage chamber 116). The third enlarged diameter portion 51d may be formed by attaching a spacer member or the like to the discharge sound-absorbing chamber forming member 51.

Here, in this embodiment, the first closure plate 121, the first cylinder 31A, the intermediate partition plate 50, the second cylinder 31B, the discharge sound-absorbing chamber forming member 51, and the second closure plate 52 are fastened by a plurality of fastening members (e.g., through bolts) 60 and fixed to the partition wall portion 114. In other words, in this embodiment, the compression mechanism portion 30 (the first compression mechanism portion 30A and the second compression mechanism portion 30B) is attached and fixed to the partition wall portion 114.

Figure 6 is a cross-sectional view taken along line D-D in Figure 3, and Figure 7 is a cross-sectional view taken along line E-E in Figure 1.

As shown in FIG. 6, the first discharge silencing chamber 41A and the second discharge silencing chamber 41B are connected via a discharge communication passage 61. In this embodiment, the discharge communication passage 61 is provided above the rotating shaft 200 and is formed as a passage penetrating the bottom of the first recess 114c forming the first discharge silencing chamber 41A, the first cylinder 31A, the intermediate partition plate 50, the second cylinder 31B, and the bottom of the second recess 51b forming the second discharge silencing chamber 41B. In addition, the second discharge silencing chamber 41B is connected to the second storage chamber 116 via a discharge hole 52a formed in the second closing plate 52.

6, the first suction port 42A opening into the suction chamber in the first cylinder chamber 33A of the first cylinder 31A is connected to the first storage chamber 115 via a first suction passage 62. In this embodiment, the first suction passage 62 is provided below the rotating shaft 200. As shown in Figures 2, 3, 6 and 7, the first suction passage 62 is formed as a passage penetrating a portion adjacent to the first suction port 42A of the first cylinder 31A, the partition wall portion 114 and the first blocking plate 121. Here, as shown in FIG. 7, the first suction passage 62 is bent inside the first blocking plate 121, and the opening end 62a that opens to the side of the first blocking plate 121 opposite the side of the partition wall 114, i.e., the inlet side opening end 62a of the first suction passage 62 that opens to the first storage chamber 115, is located at the bottom of the first storage chamber 115 and vertically below the first axial hole 114b.

Furthermore, as shown in Figures 3 and 6, the second suction port 42B, which opens into the suction chamber in the second cylinder chamber 33B of the second cylinder 31B, is connected to the first storage chamber 115 via the second suction passage 63, which penetrates the intermediate partition plate 50 and connects the first suction port 42A and the second suction port 42B, and the first suction passage 62.

Here, the lubricating oil reservoir 150 will be described. As described above, in this embodiment, the lubricating oil reservoir 150 is provided in the inner bottom of the housing 110, more specifically, in the lower part of the second storage chamber 116. As shown in Figures 1 and 2, the lubricating oil reservoir 150 includes a main reservoir 151, a secondary reservoir 152, and a lubricating oil flow path 153 that connects the main reservoir 151 and the secondary reservoir 152.

The main reservoir 151 stores most of the lubricating oil O. In other words, the main reservoir 151 is a primary reservoir where the lubricating oil O is temporarily stored. There are no particular limitations on the size or position of the main reservoir 151, but in this embodiment, the main reservoir 151 is provided between the second housing end wall 110c and the component of the compression mechanism 30 that is closest thereto (here, the second closure plate 52), and a space is formed above the main reservoir 151. In other words, the main reservoir 151 is located below a relatively large space within the housing 110.

The auxiliary storage section 152 stores the lubricating oil O introduced into the first back pressure chamber 39A of the first compression mechanism section 30A and the second back pressure chamber 39B of the second compression mechanism section 30B. The auxiliary storage section 152 mainly stores the lubricating oil O that has moved from the main storage section 151 through the lubricating oil flow path 153. In other words, the auxiliary storage section 152 is a secondary storage section that secondarily stores the lubricating oil O. As shown in Figures 1 to 4, the auxiliary storage section 152 is formed between the outer periphery of the lower side of the compression mechanism section 30 and the inner periphery of the lower side of the housing 110, and includes a first gap section G1 formed between the outer periphery of the first enlarged diameter section 32A of the first cylinder 31A and the inner periphery of the housing 110, and a second gap section G2 formed between the outer periphery of the second enlarged diameter section 32B of the second cylinder 31B and the inner periphery of the housing 110.

The lubricating oil flow passage 153 is provided between the main reservoir 151 and the sub-reservoir 152. FIG. 8 is a cross-sectional view taken along the line F-F of FIG. 1. As shown in FIGS. 1, 2, 5, and 8, in this embodiment, the lubricating oil flow passage 153 is composed of a first flow passage portion 153a formed by the outer periphery of the lower side of the second closure plate 52 and the inner periphery of the housing 110, and a second flow passage portion 153b formed by the outer periphery of the third enlarged diameter portion 51d of the discharge sound-absorbing chamber forming member 51 and the inner periphery of the lower side of the housing 110.

In this embodiment, the flow path cross-sectional area of the second flow path portion 153b of the lubricating oil flow path 153 (see FIG. 5) is set to be significantly smaller (narrower) than the flow path cross-sectional area of the secondary storage portion 152 (see FIG. 3 and FIG. 4) and the flow path cross-sectional area of the first flow path portion 153a of the lubricating oil flow path 153 (see FIG. 8).

Returning to FIG. 1, the compressor 100 has an oil supply passage 70 for supplying lubricating oil O to the bearing portion (first shaft hole 114b, second shaft hole 51a) of the rotating shaft 200 and each sliding portion of the compression mechanism portion 30 (first compression mechanism portion 30A, second compression mechanism portion 30B). As shown in FIG. 2, the oil supply passage 70 includes a first oil passage 71 formed inside the second closure plate 52, a second oil passage 72 extending inside the rotating shaft 200 in the axial direction of the rotating shaft 200, and first to fourth oil guide holes 73 to 76 extending radially inside the rotating shaft 200.

The first oil passage 71 is formed as a passage whose one end (lower end) opens at the bottom of the second closure plate 52, extends upward, and then bends toward the rear end surface of the rotating shaft 200, and whose other end (upper end) opens into the second shaft hole 51a. Specifically, the first oil passage 71 is composed of a vertical hole that extends vertically from the bottom of the second closure plate 52 to a position corresponding to the rotating shaft 200, and a horizontal hole that extends horizontally from a portion corresponding to the second shaft hole 51a on the surface of the second closure plate 52 on the discharge sound-absorbing chamber forming member 51 side and connects to the vertical hole. The one end (lower end) of the first oil passage 71, i.e., the opening of the vertical hole, functions as a suction port of the oil supply passage 70 that sucks up the lubricating oil O from the lubricating oil reservoir 150.

The second oil passage 72 is formed as a passage whose one end (rear end) opens to the rear end face of the rotating shaft 200 and extends within the rotating shaft 200 along the axis of the rotating shaft 200 to a position beyond the first cylinder 31A (inside the first shaft hole 114b). The other end (front end) of the second oil passage 72 is closed. The one end (rear end) of the second oil passage 72 is connected to the other end (upper end) of the first oil passage 71, and the first oil passage 71 and the second oil passage 72 form a single passage.

The first oil guide hole 73 has one end that opens into the second oil passage 72 and extends radially through the rotating shaft 200, with the other end opening into the outer circumferential surface of the rotating shaft 200 located in the second shaft hole 51a. More specifically, the other end of the first oil guide hole 73 opens into the outer circumferential surface of the rotating shaft 200 located in the second shaft hole 51a at a position adjacent to the second cylinder 31B. That is, the first oil guide hole 73 communicates with the second oil passage 72 and the second minute gap formed between the outer circumferential surface of the rotating shaft 200 and the inner circumferential surface of the second shaft hole 51a. Here, the portion of the outer circumferential surface of the rotating shaft 200 located in the second shaft hole 51a where the other end of the first oil guide hole 73 opens is slightly smaller in diameter than the other portions, and functions as a lubricating oil reservoir.

The second oil guide hole 74 has one end opening into the second oil passage 72 and extends radially inside the rotating shaft 200, with the other end opening into the outer circumferential surface of the second eccentric portion 202 of the rotating shaft 200 (see Figures 2 and 4). Here, the portion of the outer circumferential surface of the second eccentric portion 202 where the other end of the second oil guide hole 74 opens is a flat surface, and a third minute gap is formed between the outer circumferential surface of the second eccentric portion 202 and the inner circumferential surface of the second piston member 34B. In other words, the second oil guide hole 74 communicates with the second oil passage 72 and the third minute gap formed between the outer circumferential surface of the second eccentric portion 202 and the inner circumferential surface of the second piston member 34B.

The third oil guide hole 75 has one end opening into the second oil passage 72 and extends radially inside the rotating shaft 200, with the other end opening into the outer circumferential surface of the first eccentric portion 201 of the rotating shaft 200. Here, similar to the second eccentric portion 202, the portion of the outer circumferential surface of the first eccentric portion 201 where the other end of the third oil guide hole 75 opens is a flat surface, and a fourth minute gap is formed between the outer circumferential surface of the first eccentric portion 201 and the inner circumferential surface of the first piston member 34A. In other words, the third oil guide hole 75 communicates with the second oil passage 72 and the fourth minute gap formed between the outer circumferential surface of the first eccentric portion 201 and the inner circumferential surface of the first piston member 34A.

The fourth oil guide hole 76 has one end that opens into the second oil passage 72 and extends radially through the rotating shaft 200, with the other end opening into the outer circumferential surface of the rotating shaft 200 located in the first shaft hole 114b. More specifically, the other end of the fourth oil guide hole 76 opens into the outer circumferential surface of the rotating shaft 200 located in the first shaft hole 114b at a portion adjacent to the first cylinder 31A. That is, the fourth oil guide hole 76 communicates with the second oil passage 72 and the first minute gap formed between the outer circumferential surface of the rotating shaft 200 and the inner circumferential surface of the first shaft hole 114b. Here, the portion of the outer circumferential surface of the rotating shaft 200 located in the first shaft hole 114b where the other end of the fourth oil guide hole 76 opens is slightly smaller in diameter than the other portions, and functions as a lubricating oil reservoir.

Next, the operation of the compressor 100 will be described with reference to Figures 9 and 10. Figure 9 is a diagram equivalent to Figure 6, in which the flow of refrigerant (gas) in the compressor 100 is indicated by arrows. Figure 10 is a diagram equivalent to Figure 1, in which the flow of lubricating oil O in the compressor 100 is indicated by arrows.

As shown in FIG. 9, first, the refrigerant on the low pressure side of the external refrigerant circuit (low pressure refrigerant), which is the object of compression by the compressor 100 according to this embodiment, flows into the first storage chamber 115 from the refrigerant inlet hole 117. Therefore, the pressure in the first storage chamber 115 is approximately equal to the pressure of the low pressure refrigerant (the pressure on the low pressure side of the external refrigerant circuit).

The low-pressure refrigerant that flows into the first storage chamber 115 passes through the motor unit 10 (the gap between the stator 11 and the rotor 12), then passes through the first suction passage 62 and the first suction port 42A to be sucked into the first cylinder chamber 33A of the first compression mechanism unit 30A, and passes through the first suction passage 62, the second suction passage 63, and the second suction port 42B to be sucked into the second cylinder chamber 33B of the second compression mechanism unit 30B. The low-pressure refrigerant passes through the motor unit 10 to cool the motor unit 10. Also, as described above, the inlet side opening end 62a of the first suction passage 62 is located at the bottom of the first storage chamber 115, and when lubricating oil O is stored at the bottom of the first storage chamber 115, a portion of the stored lubricating oil O can be sucked into the first cylinder chamber 33A and the second cylinder chamber 33B together with the low-pressure refrigerant.

The low-pressure refrigerant sucked into the first cylinder chamber 33A is compressed in the first cylinder chamber 33A by the eccentric rotation of the first piston member 34A to become a high-pressure refrigerant. The high-pressure refrigerant is discharged from the first cylinder chamber 33A through the first discharge port 43A (see FIG. 3) and the first communication hole 114d (see FIG. 2) into the first discharge silencing chamber 41A, and then passes through the discharge communication passage 61 to flow into the second discharge silencing chamber 41B.

The low-pressure refrigerant sucked into the second cylinder chamber 33B is compressed in the second cylinder chamber 33B by the eccentric rotation of the second piston member 34B to become a high-pressure refrigerant. The high-pressure refrigerant is discharged from the second cylinder chamber 33B through the second discharge port 43B (see FIG. 4) and the second communication hole 51c (see FIG. 2) into the second discharge sound-reducing chamber 41B.

The high-pressure refrigerant discharged from the first cylinder chamber 33A and the high-pressure refrigerant discharged from the second cylinder chamber 33B join in the second discharge sound-reducing chamber 41B, and the joined high-pressure refrigerant is discharged through the discharge hole 52a into the second storage chamber 116. In other words, the second storage chamber 116 constitutes a "discharge chamber" from which the high-pressure refrigerant compressed by the compression mechanism 30 is discharged. Therefore, the pressure in the second storage chamber 116 is approximately equal to the pressure of the high-pressure refrigerant (the pressure on the high-pressure side of the external refrigerant circuit).

The high-pressure refrigerant discharged into the second storage chamber 116 comes into contact with and/or collides with the second housing end wall portion 110c, etc., which separates the lubricating oil O contained therein from the high-pressure refrigerant. The high-pressure refrigerant from which the lubricating oil O has been separated then flows out to the high-pressure side of the external refrigerant circuit via the refrigerant outlet hole 118. Meanwhile, the lubricating oil O separated from the high-pressure refrigerant moves downward by gravity and is stored in the lubricating oil storage portion 150 (mainly the main storage portion 151).

As described above, in the lubricating oil reservoir 150, the auxiliary reservoir 152 is connected to the main reservoir 151 via the lubricating oil flow path 153. Therefore, as shown in FIG. 10, a portion of the lubricating oil O stored in the main reservoir 151 moves to the auxiliary reservoir 152 via the lubricating oil flow path 153 and is stored in the auxiliary reservoir 152.

The lubricating oil O stored in the auxiliary storage section 152 is introduced into the first back pressure chamber 39A of the first compression mechanism section 30A through the first lubricating oil introduction hole 40A, and into the second back pressure chamber 39B of the second compression mechanism section 30B through the second lubricating oil introduction hole 40B. The lubricating oil O in the first back pressure chamber 39A can move to the second back pressure chamber 39B through the communication hole 50a formed in the intermediate partition plate 50, and the lubricating oil O in the second back pressure chamber 39B can move to the first back pressure chamber 39A through the communication hole 50a formed in the intermediate partition plate 50.

As described above, the oil supply passage 70 for supplying lubricating oil O to the bearing portion of the rotating shaft 200 and each sliding portion of the compression mechanism portion 30 includes a first oil passage 71 formed inside the second closure plate 52, a second oil passage 72 extending inside the rotating shaft 200 in the axial direction of the rotating shaft 200, and first to fourth oil guide holes 73 to 76 extending radially inside the rotating shaft 200.

One end of the oil supply passage 70 (one end (lower end) of the first oil passage 71) is located in the second storage chamber 116. The other end of the oil supply passage 70 (fourth oil guide hole 76) is connected to the first storage chamber 115 via the first shaft hole 114b, more specifically, via the first minute gap formed between the outer circumferential surface of the rotating shaft 200 and the inner circumferential surface of the first shaft hole 114b. The pressure in the first storage chamber 115 is equal to the pressure of the low-pressure refrigerant, and the pressure in the second storage chamber 116 is equal to the pressure of the high-pressure refrigerant. In other words, the pressure in the second storage chamber 116 is higher than the pressure in the first storage chamber 115.

As a result, the pressure difference between the second storage chamber 116 and the first storage chamber 115 causes the lubricating oil O in the lubricating oil reservoir 150 to be sucked up into the oil supply passage 70. Specifically, the lubricating oil O in the lubricating oil reservoir 150 flows into the first oil passage 71 from the one end (lower end) of the first oil passage 71 and is guided to the second oil passage 72.

The lubricating oil O guided to the second oil passage 72 is supplied to the first shaft hole 114b through the fourth oil guide hole 76. The lubricating oil O guided to the second oil passage 72 is also supplied to the second shaft hole 51a through the first oil guide hole 73. The lubricating oil O guided to the second oil passage 72 is further guided to the inside of the second piston member 34B through the second oil guide hole 74, and is supplied from there to each sliding part of the second compression mechanism part 30B. Similarly, the lubricating oil O guided to the second oil passage 72 is guided to the inside of the first piston member 34A through the third oil guide hole 75, and is supplied from there to each sliding part of the first compression mechanism part 30A.

The lubricating oil O supplied to the first shaft hole 114b passes through the first minute gap formed between the inner peripheral surface of the first shaft hole 114b and the outer peripheral surface of the rotating shaft 200 and flows out into the first storage chamber 115. The lubricating oil O that flows out into the first storage chamber 115 then falls and is stored in the lower part of the first storage chamber 115, or is sucked into the first cylinder chamber 33A of the first compression mechanism unit 30A and the second cylinder chamber 33B of the second compression mechanism unit 30B together with the low-pressure refrigerant in the first storage chamber 115.

The compressor 100 according to this embodiment provides the following advantages:

The lubricating oil reservoir 150 is provided at the bottom of the high-pressure second storage chamber 116. In the first compression mechanism 30A, the high-pressure lubricating oil O stored in the sub-reservoir 152 of the lubricating oil reservoir 150 is introduced into the first back pressure chamber 39A through the first lubricating oil introduction hole 40A. Therefore, the first vane 35A is pressed against the first piston member 34A by the pressure difference between the pressure of the first back pressure chamber 39A (pressure of the high-pressure lubricating oil O) and the pressure of the first cylinder chamber 33A as the back pressure. In other words, the first vane 35A is pressed against the first piston member 34A by the biasing force of the first biasing member 37A and the pressing force based on the pressure of the high-pressure lubricating oil O introduced into the first back pressure chamber 39A. Similarly, in the second compression mechanism 30B, high-pressure lubricating oil O stored in the secondary storage section 152 of the lubricating oil storage section 150 is introduced into the second back pressure chamber 39B through the second lubricating oil introduction hole 40B, and the second vane 35B is pressed against the second piston member 34B by the biasing force of the second biasing member 37B and the pressing force based on the pressure of the high-pressure lubricating oil O introduced into the second back pressure chamber 39B.

Therefore, the first vane 35A is pressed against the first piston member 34A with sufficient pressing force, and the first vane 35A is prevented from moving away from the first piston member 34A. Similarly, the second vane 35B is pressed against the second piston member 34B with sufficient pressing force, and the second vane 35B is prevented from moving away from the second piston member 34B.

The first vane 35A reciprocates in the first vane groove 36A in association with the eccentric rotation of the first piston member 34A. That is, the first vane 35A advances into the first cylinder chamber 33A by the biasing force of the first biasing member 37A and is pressed by the first piston member 34A to retreat from the first cylinder chamber 33A (is pushed back by the first piston member 34A). When the first vane 35A reciprocates, the volume of the first back pressure chamber 39A changes. Similarly, the second vane 35B reciprocates in the second vane groove 36B in association with the eccentric rotation of the second piston member 34B, and the volume of the second back pressure chamber 39B changes in response to the reciprocating movement of the second vane 35B. On the other hand, because the lubricating oil O has a relatively high viscosity, the following phenomenon may occur, especially during high-speed rotation, that is, when the first vane 35A and the second vane 35B reciprocate at high speed.

When the volume of the first back pressure chamber 39A increases, the amount of lubricating oil O corresponding to the increase in volume is not quickly introduced into the first back pressure chamber 39A, and as a result, the pressure in the first back pressure chamber 39A temporarily drops. Similarly, when the volume of the second back pressure chamber 39B increases, the amount of lubricating oil O corresponding to the increase in volume is not quickly introduced into the second back pressure chamber 39B, and as a result, the pressure in the second back pressure chamber 39B temporarily drops. The former causes the first vane 35A to separate from the first piston member 34A, and the latter causes the second vane 35B to separate from the second piston member 34B. For this reason, it is desirable to suppress the occurrence of these phenomena.

In this embodiment, the first back pressure chamber 39A of the first compression mechanism 30A and the second back pressure chamber 39B of the second compression mechanism 30B are connected through a communication hole 50a formed in the intermediate partition plate 50. In addition, the first piston member 34A and the second piston member 34B rotate eccentrically with a phase difference of 180°. Therefore, when the first vane 35A is pushed back by the first piston member 34A and the volume of the first back pressure chamber 39A decreases, the high-pressure lubricating oil O in the first back pressure chamber 39A passes through the communication hole 50a and moves to the second back pressure chamber 39B whose volume has increased. Similarly, when the second vane 35B is pushed back by the second piston member 34B and the volume of the second back pressure chamber 39B decreases, the high-pressure lubricating oil O in the second back pressure chamber 39B passes through the communication hole 50a and moves to the first back pressure chamber 39A whose volume has increased. In other words, high-pressure lubricating oil O is directly exchanged between the first back pressure chamber 39A and the second back pressure chamber 39B.

As a result, the introduction of lubricating oil O into the first back pressure chamber 39A, whose volume has increased, and the introduction of lubricating oil O into the second back pressure chamber 39B, whose volume has increased, are performed quickly, thereby preventing the occurrence of the above-mentioned phenomenon.

In particular, in this embodiment, the first back pressure chamber 39A communicates with the first gap G1 of the auxiliary reservoir 152 via the first lubricant introduction hole 40A, and the second back pressure chamber 39B communicates with the second gap G2 of the auxiliary reservoir 152 via the second lubricant introduction hole 40B. The flow path cross-sectional area of the first gap G1 and the flow path cross-sectional area of the second gap G2 are smaller than the opening area (flow path cross-sectional area) of the communication hole 50a. This suppresses the outflow of lubricant O from the first back pressure chamber 39A, whose volume has been reduced, to the auxiliary reservoir 152, and the outflow of lubricant O from the second back pressure chamber 39B, whose volume has been reduced, to the auxiliary reservoir 152.

As a result, high-pressure lubricating oil O is efficiently exchanged between the first back pressure chamber 39A and the second back pressure chamber 39B, effectively preventing the occurrence of the above-mentioned phenomenon.

The lubricating oil O introduced into the first back pressure chamber 39A is also used for sealing between the first vane 35A and the first vane groove 36A, and the lubricating oil O introduced into the second back pressure chamber 39B is also used for sealing between the second vane 35B and the second vane groove 36B. For this reason, more lubricating oil O needs to be introduced into the first back pressure chamber 39A and the second back pressure chamber 39B during high speed rotation than during low speed rotation.

In this embodiment, the lubricating oil flow path 153, which connects the main reservoir 151 that stores most of the lubricating oil O with the auxiliary reservoir 152 that stores the lubricating oil O introduced into the first back pressure chamber 39A of the first compression mechanism 30A and the second back pressure chamber 39B of the second compression mechanism 30B, has a second flow path portion 153b that has a flow path cross-sectional area smaller than the flow path cross-sectional area of the auxiliary reservoir 152. Therefore, the second flow path portion 153b functions as a "throttle" in the lubricating oil flow path 153, and the outflow of the lubricating oil O from the auxiliary reservoir 152 is suppressed.

Therefore, even if the compressor 100 tilts during high-speed rotation, the lubricating oil O in the secondary storage section 152 is prevented from running short, and more specifically, the lubricating oil O introduced into the first back pressure chamber 39A and the second back pressure chamber 39B is prevented from running short. In this embodiment, the second flow path section 153b corresponds to the "narrow section" of the present invention.

In addition, since the lubricating oil flow passage 153 has the second flow passage section 153b (i.e., a narrow section) whose flow passage cross-sectional area is smaller than the flow passage cross-sectional area of the secondary storage section 152, the lubricating oil O in the main storage section 151 is hardly affected by the reciprocating motion of the first vane 35A and the second vane 35B. In other words, the lubricating oil O in the main storage section 151 is hardly stirred by the reciprocating motion of the first vane 35A and the second vane 35B. Therefore, the amount of lubricating oil O that flows out of the refrigerant outlet hole 118 together with the high-pressure refrigerant is reduced.

Furthermore, in this embodiment, the one end (lower end) of the first oil passage, which functions as a suction port for suctioning the lubricating oil O from the lubricating oil reservoir 150, opens to the bottom of the second closure plate 52. In other words, the oil supply passage 70 suctions up the lubricating oil O that is closer to the main reservoir 151 than the second flow passage 153b in the lubricating oil reservoir 150, that is, the lubricating oil O that is hardly affected (hardly stirred) by the reciprocating motion of the first vane 35A and the second vane 35B. Therefore, the suction of the lubricating oil O by the oil supply passage 70, and thus the supply of the lubricating oil O to the bearing portion of the rotating shaft 200 and each sliding portion of the compression mechanism 30, are stably performed.

In the above embodiment, the compressor 100 has the rotating shaft 200, the electric motor unit 10 that rotates the rotating shaft 200, and the compression mechanism unit 30 that is driven by the rotating shaft 200 inside the housing 110. However, this is not limited to this. For example, the compressor 100 may be configured so that the rotating shaft 200 is rotated by a drive source outside the housing 110, without having the electric motor unit 10 inside the housing 110. When the compressor 100 is configured in this way, a part of the rotating shaft 200 may protrude outside the housing 110, but this case is also included in the "compressor having a rotating shaft inside the housing".

The above describes the embodiments of the present invention and their variations, but the present invention is not limited to the above-mentioned embodiments and variations, and further variations and modifications are possible based on the technical concept of the present invention.

10...motor section, 11...stator, 12...rotor, 30...compression mechanism section, 30A...first compression mechanism section, 30B...second compression mechanism section, 31A...first cylinder, 31B...second cylinder, 33A...first cylinder chamber, 33B...second cylinder chamber, 34A...first piston member, 34B...second piston member, 35A...first vane, 35B...second vane, 37A...first biasing member, 37B...second biasing member, 39A...first back pressure chamber, 39B...second back pressure chamber, 40A...first lubricating oil introduction hole, 40B...second lubricating oil introduction hole, 50...intermediate partition plate (partition member), 50a...communication hole, 51...discharge muffling chamber forming member, 51a...second shaft hole (bearing portion), 70...oil supply passage, 100...horizontal rotary compressor, 114...partition wall portion, 114b...first shaft hole (bearing portion), 115...first storage chamber, 116...second storage chamber, 150...lubricating oil storage portion, 151...main storage portion, 152...second storage portion, 153...lubricating oil flow path, 153a...first flow path portion, 153b...second flow path portion (narrow portion), 200...rotating shaft, G1...first gap portion, G2...second gap portion, O...lubricating oil

Claims (4)

A horizontally placed rotary compressor includes a horizontally extending rotary shaft rotatably supported by a bearing portion, and a rotary type compression mechanism portion driven by the rotary shaft, the compression mechanism portion including a first compression mechanism portion and a second compression mechanism portion disposed on either side of a partition member, and a lubricating oil reservoir portion for storing lubricating oil is provided on an inner bottom portion of the housing,
Each of the first compression mechanism and the second compression mechanism includes a cylinder chamber, a piston member which rotates eccentrically within the cylinder chamber in association with the rotation of the rotary shaft, a vane whose tip portion contacts the piston member to divide the cylinder chamber into a suction chamber and a compression chamber, a biasing member which biases the vane toward the piston member, and a back pressure chamber into which lubricating oil is introduced to apply pressure to a back surface of the vane,
a piston member of the first compression mechanism and a piston member of the second compression mechanism eccentrically rotate with a phase difference of 180°;
the back pressure chamber of the first compression mechanism and the back pressure chamber of the second compression mechanism are in communication with each other via a communication hole formed in the partition member,
the lubricating oil reservoir includes a main reservoir that reserves most of the lubricating oil, an auxiliary reservoir that is formed between an outer periphery of the compression mechanism and an inner periphery of the housing and reserves the lubricating oil to be introduced into the back pressure chamber of the first compression mechanism and the back pressure chamber of the second compression mechanism, and a lubricating oil flow path that connects the main reservoir and the auxiliary reservoir;
The lubricant flow path includes a narrow portion having a flow path cross-sectional area smaller than a flow path cross-sectional area of the secondary reservoir.
Horizontal rotary compressor. the auxiliary storage portion includes a first gap portion formed between an outer periphery of the first compression mechanism portion and an inner periphery of the housing, the first gap portion having a flow path cross-sectional area smaller than the flow path cross-sectional area of the communication hole, and a second gap portion formed between an outer periphery of the second compression mechanism portion and an inner periphery of the housing, the second gap portion having a flow path cross-sectional area smaller than the flow path cross-sectional area of the communication hole,
The back pressure chamber of the first compression mechanism communicates with the first gap of the auxiliary storage portion through a first lubricant oil introduction hole, and the back pressure chamber of the second compression mechanism communicates with the second gap of the auxiliary storage portion through a second lubricant oil introduction hole.
2. The horizontal rotary compressor according to claim 1. an oil supply passage that draws up the lubricating oil from the lubricating oil reservoir and supplies it to at least one of the bearing portion and each sliding portion of the compression mechanism portion;
The oil supply passage is configured to suck up the lubricating oil on the main reservoir side rather than the narrow portion in the lubricating oil reservoir.
3. The horizontal rotary compressor according to claim 1 or 2. The rotary shaft is rotated by an electric motor unit disposed inside the housing.
an interior of the housing is partitioned by a partition into a first storage chamber that accommodates the electric motor unit and a second storage chamber that accommodates the compression mechanism unit and has a higher pressure than the first storage chamber;
The lubricant oil reservoir is provided in the second chamber.
The horizontal rotary compressor according to any one of claims 1 to 3.