CN115552123A - Horizontal rotary compressor - Google Patents

Abstract

Provided is a horizontal rotary compressor capable of suppressing separation of a vane and a piston member and suppressing stirring of lubricating oil caused by reciprocation of the vane. In a horizontal rotary compressor, a first back pressure chamber (39A) of a first compression mechanism part (30A) which introduces lubricating oil and causes back pressure to act on a first vane (35A) and a second back pressure chamber (39B) of a second compression mechanism part (30B) which introduces lubricating oil and causes back pressure to act on a second vane (35B) are communicated through a communication hole (50A) formed in an intermediate partition plate (50), a lubricating oil storage part (150) is provided with a main storage part (151), an auxiliary storage part (152) which stores the lubricating oil introduced into the first back pressure chamber (39A) and the second back pressure chamber (39B), and a lubricating oil flow path (153) which communicates the main storage part (151) and the auxiliary storage part (152), and the lubricating oil flow path (153) comprises a second flow path part (153B) with the flow path cross-sectional area smaller than that of the auxiliary storage part (152).

Description

Horizontal rotary compressor

Technical Field

The present invention relates to a horizontal rotary compressor.

Background

As an example of a horizontal rotary compressor, a compressor (horizontal rotary compressor) described in patent document 1 is known. In the compressor described in patent document 1, the inside of a sealed container (housing) is partitioned by a partition member into an oil reservoir space in which a rotary compression mechanism portion is located and a motor-side space in which a motor portion is located. The compression mechanism unit includes a first compression mechanism unit and a second compression mechanism unit provided on both left and right sides of the intermediate partition plate. Each of the first compression mechanism and the second compression mechanism includes: a cylinder chamber; an eccentric roller (piston member) eccentrically rotating in the cylinder chamber; and a vane (blade) which is in contact with the eccentric roller to divide the inside of 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 by the first compression mechanism unit and the second compression mechanism unit is discharged to the motor-side space to fill the motor-side space, is guided to the oil reservoir space to fill the oil reservoir space, and the high-pressure refrigerant filled in the oil reservoir space is discharged to the outside through a discharge refrigerant pipe. The compressor described in patent document 1 includes an oil supply passage for sucking up lubricating oil stored in a lower portion of the oil storage space and supplying the lubricating oil to the sliding portions of the first compression mechanism and the second compression mechanism.

Documents of the prior art

Patent document

[ patent document 1]

Japanese patent laid-open No. 2004-60533

Disclosure of Invention

Technical problems to be solved by the invention

In the compressor described in patent document 1, the fins of the first compression mechanism and the fins of the second compression mechanism are simply pressed elastically against the corresponding eccentric rollers. Therefore, depending on the operating state of the compressor, etc., the pressing force of the fins of the first compression mechanism and the fins of the second compression mechanism against the corresponding eccentric rollers may be insufficient, and the fins of the first compression mechanism and the fins of the second compression mechanism may be separated from the corresponding eccentric rollers.

In the compressor described in patent document 1, the fins of the first compression mechanism and the fins of the second compression mechanism are immersed in the lubricating oil stored in the lower portion of the oil storage space. The vane of the first compression mechanism and the vane of the second compression mechanism reciprocate with the eccentric rotation of the corresponding eccentric roller, and therefore agitate the lubricating oil stored in the lower portion of the oil storage space. If the stored lubricating oil is stirred, the amount of lubricating oil discharged from the discharge refrigerant pipe together with the high-pressure refrigerant increases, or the lubricating oil is sucked up by the oil supply path and the supply of lubricating oil to the sliding portions of the first compression mechanism unit and the second compression mechanism unit may become unstable.

Accordingly, an object of the present invention is to provide a horizontal rotary compressor capable of suppressing separation of a vane and a piston member and suppressing stirring of lubricating oil due to reciprocation of the vane.

Technical scheme for solving technical problem

According to an aspect of the present invention, there is provided a recumbent rotary compressor. The horizontal rotary compressor includes a horizontally extending rotary shaft rotatably supported by a bearing portion and a rotary compression mechanism driven by the rotary shaft, in a casing. The compression mechanism portion includes a first compression mechanism portion and a second compression mechanism portion disposed on both sides of the partition member with the partition member interposed therebetween, and a lubricating oil reservoir portion for storing lubricating oil is provided in an inner bottom portion of the housing. Each of the first compression mechanism portion and the second compression mechanism portion includes: a cylinder chamber; a piston member that eccentrically rotates in the cylinder chamber as the rotary shaft rotates; a vane having a tip portion contacting 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, wherein the back pressure chamber of the first compression mechanism communicates with the back pressure chamber of the second compression mechanism via a communication hole formed in the partition member. Further, the lubricant oil reservoir includes: a main reservoir for storing most of the lubricating oil; a sub reservoir portion that is formed between an outer peripheral portion of the compression mechanism portion and an inner peripheral portion of the housing and that stores the lubricating oil introduced into the back pressure chamber of the first compression mechanism portion and the back pressure chamber of the second compression mechanism portion; and a lubricating oil flow path that connects the main reservoir and the sub reservoir, wherein the lubricating oil flow path includes a narrowed portion having a flow path cross-sectional area smaller than a flow path cross-sectional area of the sub reservoir.

Effects of the invention

According to an aspect of the present invention, it is possible to provide a horizontal rotary compressor capable of suppressing separation of a vane and a piston member and suppressing stirring of lubricating oil caused by reciprocation of the vane.

Drawings

Fig. 1 is a sectional view showing a schematic configuration of a horizontal rotary compressor according to an embodiment of the present invention.

Fig. 2 is a diagram showing the compression mechanism 30 and its periphery in the horizontal rotary compressor, where fig. 2 (a) is an enlarged view of a main portion of fig. 1, fig. 2 (b) is an enlarged view of a portion X of fig. 2 (a), and fig. 2 (c) is an enlarged view of a portion Y of fig. 2 (a).

Fig. 3 isbase:Sub>A sectional viewbase:Sub>A-base:Sub>A of fig. 1.

Fig. 4 is a sectional view B-B of fig. 1.

Fig. 5 is a cross-sectional view C-C of fig. 1.

Fig. 6 is a cross-sectional view taken along line D-D of fig. 3.

Fig. 7 is a cross-sectional view E-E of fig. 1.

Fig. 8 is a sectional view F-F of fig. 1.

Fig. 9 is a view showing the flow of the refrigerant (gas) in the horizontal electric compressor.

Fig. 10 is a view showing the flow of the lubricating oil in the horizontal electric compressor.

Detailed Description

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

Fig. 1 is a sectional view showing a schematic configuration of a horizontal rotary compressor according to an embodiment of the present invention. The horizontal rotary compressor (hereinafter, simply referred to as "compressor") 100 of the embodiment has a casing 110. The housing 110 includes: a cylindrical intermediate housing 111; a bottomed cylindrical front case 112, an opening end side of the front case 112 being joined to a front end (left end in fig. 1) of the intermediate case 111; and a bottomed cylindrical rear case 113, and an open end side of the rear case 113 is joined to a rear end (right end in fig. 1) of the intermediate case 111.

A laterally long cylindrical housing body 110a is formed by the peripheral wall of the intermediate housing 111, the peripheral wall of the front housing 112, and the peripheral wall of the rear housing 113, a first housing end wall 110b that closes one (front) opening end of the housing body 110a is formed by the bottom wall of the front housing 112, and a second housing end wall 110c that closes the other (rear) opening end of the housing body 110a is formed by the bottom wall of the rear housing 113.

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

Further, a lubricant oil reservoir 150 storing lubricant oil O is provided in the inner bottom portion of the housing 110. More specifically, in the present embodiment, the lubricant storage unit 150 is provided at the lower portion of the second housing chamber 116. The lubricant reservoir 150 will be described later.

A boss portion 114a protruding toward the first accommodation chamber 115 is formed at a radially central portion of the partition wall portion 114. Further, a first shaft hole 114b is formed in the partition wall portion 114, and the first shaft hole 114b penetrates from the distal end surface of the boss portion 114a to the surface on the side of the second housing chamber 116.

The compressor 100 has a rotating shaft 200 inside a casing 110. In the housing 110, the rotary shaft 200 extends in the horizontal direction (front-rear direction), and an intermediate portion in the axial direction is inserted into the first shaft hole 114b and is rotatably supported. That is, the rotary shaft 200 extends through the partition wall portion 114, and one end (front end) side of the rotary shaft 200 is positioned in the first housing chamber 115, and the other end (rear end) side of the rotary shaft 200 is positioned in the second housing chamber 116. Further, a first minute gap (play) is formed between the inner peripheral surface of the first shaft hole 114b and the outer peripheral surface of the rotary shaft 200. The first small gap is set to be sealable (seal) by the lubricating oil O.

The motor unit 10 for rotating the rotary shaft 200 is accommodated in the first accommodation chamber 115. That is, the motor unit 10 is provided on one end (front end) side of the rotary shaft 200 in the housing 110. The first receiving chamber 115 communicates with (a low-pressure side of) an external refrigerant circuit (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 to the partition wall portion 114 across the motor portion 10 in the axial direction of the rotary shaft 200, and is provided at a position corresponding to the rotary shaft 200 (a position substantially at the same height as the rotary shaft 200) in the height (up-down) direction.

The motor portion 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 the front housing 112 side of the partition wall portion 114 of the intermediate housing 111. The stator 11 has: a stator core 11a, the stator core 11a being formed in a cylindrical shape from a magnetic body; and a stator coil 11b, the stator coil 11b being wound around (the pole teeth of) the stator core 11a, for example, in a concentrated winding manner.

The rotor 12 is disposed with a predetermined gap between the stator 11 and the radial direction inner side of the stator 11. Permanent magnets are incorporated in the rotor 12. The rotor 12 is formed in a cylindrical shape, and is fixed to the rotating shaft 200 in a state where one end (tip) side of the rotating shaft 200 is inserted into a hollow portion of the rotor 12.

The motor unit 10 is configured to rotate the rotary shaft 200 by supplying electric power to the stator 11 (stator coil 11 b) via the airtight terminal portion 20 provided in the front housing 112 to rotate the rotor 12.

The second housing chamber 116 houses the rotary compression mechanism 30 driven by the rotary shaft 200. That is, the compression mechanism 30 is provided on the other end (rear end) side of the rotary shaft 200 in the housing 110. The second receiving chamber 116 communicates with (the high-pressure side of) the external refrigerant circuit 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 portion 114 than a discharge hole 52a described later in the axial direction of the rotary shaft 200, and is provided at a position corresponding to the rotary shaft 200 in the height direction, similarly to the refrigerant inlet hole 117.

In the present embodiment, the compression mechanism unit 30 is configured as a so-called "double-rotary compression mechanism". The compression mechanism 30 includes a first compression mechanism 30A and a second compression mechanism 30B arranged in the horizontal direction, 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 section 30A and the second compression mechanism section 30B are disposed on both sides thereof with the intermediate partition plate 50 interposed therebetween. The first compression mechanism section 30A is disposed on the partition wall section 114 side (i.e., the front side) of the intermediate partition plate 50, and the second compression mechanism section 30B is disposed on the opposite side (i.e., the rear side) of the partition wall section 114 side of the intermediate partition plate 50. An insertion hole through which the rotary shaft 200 is inserted is formed in a radial center portion of the intermediate partition plate 50.

Fig. 2 shows the compression mechanism portion 30 and its periphery. Fig. 2 (a) is an enlarged view of a main portion of fig. 1, fig. 2 (b) is an enlarged view of a portion X of fig. 2 (a), and fig. 2 (c) is an enlarged view of a portion Y of fig. 2 (a). Fig. 3 isbase:Sub>A sectional view (partially omitted) taken along linebase:Sub>A-base:Sub>A of fig. 1, and mainly shows the structure of the first compression mechanism section 30base:Sub>A. Fig. 4 is a sectional view taken along line B-B of fig. 1 (with a part thereof omitted), and mainly shows the structure of the second compression mechanism section 30B.

As shown in fig. 2 and 3, the first compression mechanism portion 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 peripheral portion of the first cylinder 31A and the inner peripheral portion of the housing 110. As shown in fig. 3, the first cylinder 31A has a first diameter-enlarged portion 32A with a partially enlarged diameter on the lower side, and the outer peripheral portion of the first diameter-enlarged portion 32A is close to the inner peripheral portion of the housing 110. Therefore, a gap space narrower than the other space in the first annular space is formed between the outer peripheral portion of the first diameter-enlarged portion 32A and the inner peripheral portion of the housing 110. In the first annular space, a space (gap space) formed between the outer peripheral portion of the first enlarged diameter portion 32A and the inner peripheral portion of the housing 110 is hereinafter referred to as a "first gap portion G1".

One surface (front surface) of the first cylinder 31A is in close contact with the surface of the partition wall portion 114 on the side of the second housing chamber 116, 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 has a first cylinder chamber 33A having a circular cross section at a radial center portion.

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

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 at a lower portion of the inner peripheral surface of the first cylinder chamber 33A and has a predetermined depth at a lower portion. The first vane 35A is accommodated in the first vane groove 36A so as to be movable in a direction of entering the first cylinder chamber 33A and a direction of exiting from the first cylinder chamber 33A.

The first vane 35A is elastically biased toward the first piston member 34A in a direction of entering the first cylinder chamber 33A, in other words, toward the first biasing member 37A housed in the first vane groove 36A. In the present 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 end of the first vane 35A contacts the outer peripheral surface of the first piston member 34A, and divides the interior of the first cylinder chamber 33A into a suction chamber (low-pressure chamber) in which the first suction port 42A opens and a compression chamber (high-pressure chamber) in which the first discharge port 43A opens (see fig. 3). In the present embodiment, the first suction port 42A and the first discharge port 43A are provided below the rotation shaft 200.

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

As shown in fig. 2, in the present embodiment, a first concave portion 114c is formed on the surface of the partition wall portion 114 on the side of the first housing 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 which is in close contact with the surface of the partition wall portion 114 on the first storage chamber 115 side, thereby forming a first discharge muffling chamber 41A partitioned from the first storage chamber 115. That is, in the present embodiment, the first discharge muffling chamber 41A is provided in the partition wall portion 114. The first closing plate 121 has an outer diameter substantially equal to the inner diameter of the housing 110, and an insertion hole through which the boss portion 114a is inserted is formed in the center portion of the first closing plate 121. The first discharge muffling chamber 41A communicates with a first discharge port 43A (see fig. 3) that opens to the compression chamber in the first cylinder chamber 33A via a first communication hole 114d formed in the partition wall portion 114.

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

Similarly to the first cylinder 31A, the second cylinder 31B has an outer diameter smaller than the inner diameter of the housing 110, and a second annular space is formed between the outer peripheral portion of the second cylinder 31B and the inner peripheral portion of the housing 110. As shown in fig. 4, the second cylinder 31B has a second diameter-enlarged portion 32B that is partially enlarged in diameter on the lower side. The outer peripheral portion of the second diameter-enlarged portion 32B is close to the inner peripheral portion of the housing 110, and a gap space narrower than the other space in the second annular space is formed between the outer peripheral portion of the second diameter-enlarged portion 32B and the inner peripheral portion of the housing 110. In addition, similarly to the case of the first compression mechanism section 30A, a space (gap space) formed between the outer peripheral portion of the second diameter-enlarged section 32B and the inner peripheral portion of the housing 110 in the second annular space is hereinafter referred to as a "second gap section G2".

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 muffling chamber forming member 51. The second cylinder 31B has a second cylinder chamber 33B having a circular cross section at a radial center portion.

The second piston member 34B is formed in an annular shape and is attached to the outer peripheral surface of the second eccentric portion 202 of the rotary shaft 200 in the second cylinder chamber 33B of the second cylinder 31B. The second piston member 34B eccentrically rotates in the second cylinder chamber 33B with the rotation of the rotary shaft 200. Here, the second eccentric portion 202 is provided offset by 180 ° (having a phase difference of 180 °) about the axis of the rotary shaft 200 with respect to the first eccentric portion 201, and the first piston member 34A and the second piston member 34B eccentrically rotate 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 at a lower portion of the inner peripheral surface of the second cylinder chamber 33B and has a predetermined depth at a lower portion. The second vane 35B is housed in the second vane groove 36B so as to be movable in a direction of entering the second cylinder chamber 33B and a direction of exiting from the second cylinder chamber 33B.

The second vane 35B is elastically biased toward the second piston member 34B in a direction of entering the second cylinder chamber 33B by a second biasing member 37B accommodated in the second vane groove 36B. The second biasing member 37B is a compression coil spring, and is disposed between the second vane 35B and the bottom of the second vane groove 36B, as in the first biasing member 37A. Specifically, one end (lower end) of the compression coil spring as the second biasing member 37B is fitted into a 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 end of the second vane 35B abuts against the outer peripheral surface of the second piston member 34B, and divides the interior of the second cylinder chamber 33B into a suction chamber (low-pressure chamber) in which the second suction port 42B opens and a compression chamber (high-pressure chamber) in which the second discharge port 43B opens (see fig. 4). In the present embodiment, the second suction port 42B and the second discharge port 43B are provided at positions lower than the rotation shaft 200, similarly to the first suction port 42A and the first discharge port 43A.

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

The second back pressure chamber 39B communicates with the first back pressure chamber 39A via a communication hole 50a formed in the intermediate partition plate 50. That is, in the present 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 communicate with each other via the communication hole 50A formed in the intermediate partition plate 50. Here, the opening area (flow passage cross-sectional area) of the communication hole 50a is set larger than the flow passage cross-sectional area of the first gap portion G1 and the flow passage cross-sectional area of the second gap portion G2.

As shown in fig. 2, a second axial hole 51a is formed in a radially central portion of the discharge muffling chamber forming member 51. The rear end portion of the rotary shaft 200 and the vicinity thereof are inserted into the second shaft hole 51a so as to be rotatable. That is, the rotary shaft 200 is rotatably supported by a first shaft hole 114b formed in the partition wall portion 114 and a second shaft hole 51a formed in the discharge muffling chamber forming member 51, and the first shaft hole 114b and the second shaft hole 51a constitute bearing portions of the rotary shaft 200. Further, as in the case of the first shaft hole 114b, a second minute gap (play) is formed between the inner peripheral surface of the second shaft hole 51a and the outer peripheral surface of the rotary shaft 200.

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

Fig. 5 is a cross-sectional view C-C of fig. 1. As shown in fig. 5, the discharge muffling 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 peripheral portion of the discharge muffling chamber forming member 51 and the inner peripheral portion of the housing 110. Further, the discharge muffling chamber forming member 51 has a third enlarged diameter portion 51d, which is partially enlarged in diameter, on the lower portion side, as in the first cylinder 31A and the second cylinder 31B. The outer peripheral portion of the third diameter-enlarged portion 51d is close to the inner peripheral portion of the housing 110, and a gap space narrower than the other space in the third annular space is formed between the outer peripheral portion of the third diameter-enlarged portion 51d and the inner peripheral portion 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 such that the upper end portion thereof is positioned above the liquid surface of the lubricant oil O stored in the inner bottom portion of the housing 110 (the lower portion of the second housing chamber 116). The third enlarged diameter portion 51d may be formed by attaching a partition member or the like to the discharge sound-deadening chamber forming member 51.

Here, in the present embodiment, the first closing plate 121, the first cylinder 31A, the intermediate partition plate 50, the second cylinder 31B, the discharge muffling chamber forming member 51, and the second closing plate 52 are fastened by a plurality of fastening members (for example, through bolts) 60 and fixed to the partition wall portion 114. That is, in the present embodiment, the compression mechanism portion 30 (the first compression mechanism portion 30A, the second compression mechanism portion 30B) is attached and fixed to the partition wall portion 114.

Fig. 6 is a sectional view taken along line D-D of fig. 3, and fig. 7 is a sectional view taken along line E-E of fig. 1.

As shown in fig. 6, the first discharge muffling chamber 41A and the second discharge muffling chamber 41B communicate via a discharge communication path 61. In the present embodiment, the discharge communication path 61 is provided above the rotary shaft 200, and is formed as a passage that penetrates the bottom of the first concave portion 114c forming the first discharge muffling chamber 41A, the first cylinder 31A, the intermediate partition plate 50, the second cylinder 31B, and the bottom of the second concave portion 51B forming the second discharge muffling chamber 41B. The second discharge muffling chamber 41B communicates with the second housing chamber 116 through a discharge hole 52a formed in the second closing plate 52.

As shown in fig. 6, the first intake port 42A, which opens into the intake chamber in the first cylinder chamber 33A of the first cylinder 31A, communicates with the first storage chamber 115 via the first intake passage 62. In the present embodiment, the first suction passage 62 is provided below the rotation shaft 200. As shown in fig. 2, 3, 6, and 7, the first suction passage 62 is formed as a passage that penetrates through a portion of the first cylinder 31A adjacent to the first suction port 42A, the partition wall portion 114, and the first closing plate 121. Here, as shown in fig. 7, the first suction path 62 is bent inside the first closing plate 121, and an opening end 62a opened to a surface of the first closing plate 121 opposite to the surface on the partition wall portion 114 side, that is, an inlet-side opening end 62a of the first suction path 62 opened to the first housing chamber 115 is positioned below the first housing chamber 115 and below the plumb of the first shaft hole 114b.

As shown in fig. 3 and 6, the second suction port 42B, which is open in the second cylinder chamber 33B of the second cylinder 31B, penetrates the intermediate partition plate 50 and communicates with the first housing chamber 115 via the second suction passage 63 and the first suction passage 62, and the second suction passage 63 communicates the first suction port 42A with the second suction port 42B.

Here, the lubricant reservoir 150 will be explained. As described above, in the present embodiment, the lubricant reservoir 150 is provided at the inner bottom of the housing 110, more specifically, at the lower portion of the second housing chamber 116. As shown in fig. 1 and 2, the lubricant reservoir 150 includes a main reservoir 151, an auxiliary reservoir 152, and a lubricant passage 153 communicating the main reservoir 151 and the auxiliary reservoir 152.

The main reservoir 151 stores most of the lubricating oil O. In other words, the main reservoir 151 is a primary reservoir that primarily stores the lubricating oil O. Although the size, position, and the like of the main reservoir 151 are not particularly limited, in the present embodiment, the main reservoir 151 is provided between the second housing end wall portion 110c and the component of the compression mechanism portion 30 (here, the second closing plate 52) located closest to the second housing end wall portion 110c, and a space portion is formed above the main reservoir 151. In other words, the main reservoir 151 is located below a relatively large space in the housing 110.

The sub reservoir 152 reserves 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 sub reservoir 15 mainly stores the lubricant oil O that has moved from the main reservoir 151 through the lubricant oil flow passage 153. In other words, the sub-reservoir 152 is a secondary reservoir that secondarily stores the lubricating oil O. As shown in fig. 1 to 4, the sub reservoir 152 is formed between the outer peripheral portion of the lower portion of the compression mechanism section 30 and the inner peripheral portion of the lower portion of the housing 110, and includes a first gap portion G1 and a second gap portion G2, the first gap portion G1 being formed between the outer peripheral portion of the first enlarged diameter portion 32A of the first cylinder 31A and the inner peripheral portion of the housing 110, and the second gap portion G2 being formed between the outer peripheral portion of the second enlarged diameter portion 32B of the second cylinder 31B and the inner peripheral surface 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 sectional view F-F of fig. 1. As shown in fig. 1, 2, 5, and 8, in the present embodiment, the lubricating oil flow passage 153 is constituted by a first flow passage portion 153a and a second flow passage portion 153b, the first flow passage portion 153a being formed by the outer peripheral portion of the lower portion side of the second closing plate 52 and the inner peripheral portion of the housing 110, and the second flow passage portion 153b being formed by the outer peripheral portion of the third enlarged diameter portion 51d of the discharge muffling chamber forming member 51 and the inner peripheral portion of the lower portion side of the housing 110.

In the present embodiment, the flow passage cross-sectional area of the second flow passage portion 153b of the lubricant flow passage 153 (see fig. 5) is set to be much smaller (narrower) than the flow passage cross-sectional area of the sub reservoir portion 152 (see fig. 3 and 4) and the flow passage cross-sectional area of the first flow passage portion 153a of the lubricant flow passage 153 (see fig. 8).

Returning to fig. 1, the compressor 100 includes an oil supply passage 70 for supplying the lubricating oil O to the bearing portions (the first shaft hole 114B and the second shaft hole 51 a) of the rotary shaft 200 and the sliding portions of the compression mechanism 30 (the first compression mechanism 30A and the second compression mechanism 30B). As shown in fig. 2, the oil supply passage 70 includes: a first oil passage 71 formed inside the second closing plate 52; a second oil passage 72 extending in the axial direction of the rotary shaft 200 inside the rotary shaft 200; and first to fourth oil guide holes 73 to 76 extending in the radial direction inside the rotary shaft 200.

The first oil passage 71 is a passage having one end (lower end) opened to the bottom of the second closing plate 52, extending upward, and then bent toward the rear end surface of the rotary shaft 200, and having the other end (upper end) opened to the second shaft hole 51a. Specifically, the first oil passage 71 is constituted by a vertical hole extending vertically from the bottom of the second closing plate 52 to a position corresponding to the rotation shaft 200, and a horizontal hole extending horizontally from a portion of the surface of the second closing plate 52 on the discharge muffling chamber forming member 51 side corresponding to the second shaft hole 51a and connected 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 an upper suction port of the oil supply passage 70 for sucking up the lubricating oil O from the lubricating oil reservoir 150.

The second oil passage 72 is formed as a passage having one end (rear end) opening at the rear end surface of the rotary shaft 200 and extending along the axis of the rotary shaft 200 to a position beyond the first cylinder 31A (in the first shaft hole 114 b) in the rotary shaft 200. 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 one passage.

One end of the first oil guide hole 73 opens in the second oil passage 72 and extends in the radial direction inside the rotary shaft 200, and the other end opens in the outer peripheral surface of the rotary shaft 200 located inside the second shaft hole 51a. More specifically, the other end of the first oil guide hole 73 opens to the outer peripheral surface of the rotary shaft 200 at a portion adjacent to the second cylinder 31B in the second shaft hole 51a. That is, the first oil guide hole 73 communicates the second oil passage 72 with the second minute gap formed between the outer peripheral surface of the rotary shaft 200 and the inner peripheral surface of the second shaft hole 51a. Here, a portion of the outer peripheral surface of the rotary shaft 200 located in the second shaft hole 51a, at which the other end of the first oil guide hole 73 is opened, is slightly reduced in diameter compared to other portions, and functions as a lubricant reservoir.

One end of the second oil guide hole 74 opens in the second oil passage 72 and extends in the radial direction inside the rotary shaft 200, and the other end opens in the outer peripheral surface of the second eccentric portion 202 of the rotary shaft 200 (see fig. 2 and 4). Here, a portion of the outer peripheral 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 peripheral surface of the second eccentric portion 202 and the inner peripheral surface of the second piston member 34B. That is, the second oil guide hole 74 communicates the second oil passage 72 with the third minute gap formed between the outer peripheral surface of the second eccentric portion 202 and the inner peripheral surface of the second piston member 34B.

One end of the third oil guide hole 75 opens in the second oil passage 72 and extends in the radial direction inside the rotary shaft 200, and the other end opens in the outer peripheral surface of the first eccentric portion 201 of the rotary shaft 200. Here, as in the case of the second eccentric portion 202, a portion of the outer peripheral 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 peripheral surface of the first eccentric portion 201 and the inner peripheral surface of the first piston member 34A. That is, the third oil guide hole 75 communicates the second oil passage 72 with the fourth minute gap formed between the outer peripheral surface of the second eccentric portion 201 and the inner peripheral surface of the first piston member 34A.

One end of the fourth oil guide hole 76 opens in the second oil passage 72 and extends in the radial direction inside the rotary shaft 200, and the other end opens in the outer peripheral surface of the rotary shaft 200 located inside the first shaft hole 114b. More specifically, the other end of the fourth oil guide hole 76 opens to the outer peripheral surface of the rotary shaft 200 located in a portion adjacent to the first cylinder 31A in the first shaft hole 114b. That is, the fourth oil guide hole 76 communicates the second oil passage 72 with the first minute gap formed between the outer peripheral surface of the rotary shaft 200 and the inner peripheral surface of the first shaft hole 114b. Here, a portion of the outer peripheral surface of the rotary shaft 200 located in the first shaft hole 114b, at which the other end of the fourth oil guide hole 76 opens, is slightly reduced in diameter compared to other portions, and functions as a lubricant reservoir.

Next, the operation of the compressor 100 will be described with reference to fig. 9 and 10. Fig. 9 is a view corresponding to fig. 6, and shows the flow of the refrigerant (gas) in the compressor 100 by arrows. Fig. 10 is a view corresponding to fig. 1, and shows the flow of lubricating oil O in compressor 100 by arrows.

As shown in fig. 9, first, the refrigerant on the low-pressure side of the external refrigerant circuit to be compressed in the compressor 100 of the present embodiment (low-pressure refrigerant) flows into the first receiving chamber 115 through the refrigerant inlet hole 117. Therefore, the pressure of the first accommodation chamber 115 is substantially 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 flowing into the first accommodation chamber 115 passes through the motor unit 10 (a gap between the stator 11 and the rotor 12), is then drawn into the first cylinder chamber 33A of the first compression mechanism 30A through the first suction passage 62 and the first suction port 42A, and is drawn into the second cylinder chamber 33B of the second compression mechanism 30B through the first suction passage 62, the second suction passage 63, and the second suction port 42B. The motor portion 10 is cooled by passing a low-pressure refrigerant through the motor portion 10. As described above, when the inlet-side opening end 62a of the first suction passage 62 is positioned at the lower portion of the first housing chamber 115 and the lubricating oil O is stored in the lower portion of the first housing chamber 115, a part 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, and becomes a high-pressure refrigerant. The high-pressure refrigerant is discharged from the first cylinder chamber 33A to the first discharge muffling chamber 41A through the first discharge port 43A (see fig. 3) and the first communication hole 114d (see fig. 2), and then flows into the second discharge muffling chamber 41B through the discharge communication path 61.

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, and becomes a high-pressure refrigerant. The high-pressure refrigerant is discharged from the second cylinder chamber 33B to the second discharge muffling chamber 41B through the second discharge port 43B (see fig. 4) and the second communication hole 51c (see fig. 2).

The high-pressure refrigerant discharged from the first cylinder chamber 33A and the high-pressure refrigerant discharged from the second cylinder chamber 33B merge together in the second discharge muffling chamber 41B, and the merged high-pressure refrigerant is discharged to the second receiving chamber 116 through the discharge hole 52 a. That is, the second accommodation chamber 116 constitutes a "discharge chamber" from which the high-pressure refrigerant compressed by the compression mechanism 30 is discharged. Therefore, the pressure of the second receiving chamber 116 is substantially 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 to the second receiving chamber 116 contacts and/or collides with the second housing end wall portion 110c and the like, whereby the lubricating oil O contained therein is separated from the high-pressure refrigerant. Thereafter, the high-pressure refrigerant from which the lubricating oil O is separated flows out to the high-pressure side of the external refrigerant circuit via the refrigerant outlet hole 118. On the other hand, the lubricant oil O separated from the high-pressure refrigerant moves downward by gravity and is stored in the lubricant oil storage portion 150 (mainly, the main storage portion 151).

As described above, in the lubricant reservoir 150, the sub reservoir 152 communicates with the main reservoir 151 via the lubricant flow path 153. Therefore, as shown in fig. 10, a part of the lubricant oil O stored in the main reservoir 151 moves to the sub reservoir 152 through the lubricant oil flow passage 153 and is stored in the sub reservoir 152.

The lubricating oil O stored in the sub reservoir 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 is introduced 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, oil supply passage 70 for supplying lubricating oil O to the bearing portion of rotary shaft 200 and the sliding portion of compression mechanism 30 includes: a first oil passage 71 formed inside the second closing plate 52; a second oil passage 72 extending in the axial direction of the rotary shaft 200 inside the rotary shaft 200; and first to fourth oil guide holes 73 to 76 extending in the radial direction inside the rotary shaft 200.

One end side of the oil supply passage 70 (one end (lower end) of the first oil passage 71) is positioned in the second housing chamber 116. Further, the other end side (fourth oil guide hole 76) of the oil supply passage 70 communicates with the first housing chamber 115 via the first shaft hole 114b, more specifically, via the above-described first minute gap formed between the outer peripheral surface of the rotary shaft 200 and the inner peripheral surface of the first shaft hole 114b. The pressure of the first receiving chamber 115 is equal to the pressure of the low-pressure refrigerant, and the pressure of the second receiving chamber 116 is equal to the pressure of the high-pressure refrigerant. That is, the pressure of the second housing chamber 116 is higher than the pressure of the first housing chamber 115.

Therefore, the lubricant oil O in the lubricant oil reservoir 150 is sucked up to the oil supply passage 70 by the pressure difference between the second housing chamber 116 and the first housing chamber 115. Specifically, the lubricant oil O in the lubricant oil reservoir 150 flows into the first oil passage 71 from the one end (lower end) of the first oil passage 71 and is introduced into the second oil passage 72.

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

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

According to the compressor 100 of the present embodiment, the following effects can be obtained.

The lubricant oil reservoir 150 is provided at a lower portion of the high-pressure second housing chamber 116. In the first compression mechanism section 30A, the high-pressure lubricating oil O reserved in the sub-reservoir 152 of the lubricating oil reservoir 150 is introduced into the first back pressure chamber 39A via the first lubricating oil introduction hole 40A. Therefore, a differential pressure between the pressure of the first back pressure chamber 39A (the pressure of the high-pressure lubricating oil O) and the pressure of the first cylinder chamber 33A acts on the first vane 35A as the back pressure, and the first vane 35A is pressed against the first piston member 34A. That is, 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 section 30B, the high-pressure lubricating oil O reserved in the sub reservoir 152 of the lubricating oil reservoir 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 urging force of the second urging 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 blade 35A is pressed against the first piston member 34A with a sufficient pressing force, and separation of the first blade 35A from the first piston member 34A is suppressed. Similarly, the second vane 35B is pressed against the second piston member 34B with a sufficient pressing force, thereby suppressing separation of the second vane 35B and the second piston member 34B.

The first vane 35A reciprocates in the first vane groove 36A in accordance with eccentric rotation of the first piston member 34A. That is, the first vane 35A repeatedly enters 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 exit from the first cylinder chamber 33A (pushed back by the first piston member 34A). When the first vane 35A reciprocates, the volume of the first backpressure chamber 39A changes. Similarly, the second vane 35B reciprocates in the second vane groove 36B in accordance with the eccentric rotation of the second piston member 34B, and the volume of the second back pressure chamber 39B changes in accordance with the reciprocation of the second vane 35B. On the other hand, since the viscosity of the lubricating oil O is relatively high, the following phenomenon may occur particularly at the time of high-speed rotation, that is, at the time of high-speed reciprocation of the first vane 35A and the second vane 35B.

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

In the present 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 communicate with each other via a communication hole 50A formed in the intermediate partition plate 50. In addition, the first piston member 34A and the second piston member 34B eccentrically rotate with a phase difference of 180 °. Therefore, when the first vane 35A is pushed back by the first piston member 34A to decrease the volume of the first back pressure chamber 39A, the high-pressure lubricating oil O in the first back pressure chamber 39A moves to the second back pressure chamber 39B, the volume of which increases, through the communication hole 50 a. Similarly, when the second vane 35B is pressed back by the second piston member 34B to decrease the volume of the second back pressure chamber 39B, the high-pressure lubricating oil O in the second back pressure chamber 39B moves to the first back pressure chamber 39A whose volume increases through the communication hole 50 a. That is, the high-pressure lubricating oil O is directly transferred between the first back pressure chamber 39A and the second back pressure chamber 39B.

Therefore, the lubricating oil O is introduced into the first back pressure chamber 39A having an increased volume and the lubricating oil O is introduced into the second back pressure chamber 39B having an increased volume, thereby suppressing the occurrence of the above phenomenon.

In particular, in the present embodiment, the first back pressure chamber 39A communicates with the first gap portion G1 of the sub sump 152 via the first lubricating oil introduction hole 40A, and the second back pressure chamber 39B communicates with the second gap portion G2 of the sub sump 152 via the second lubricating oil introduction hole 40B. The flow passage sectional area of the first gap portion G1 and the flow passage sectional area of the second gap portion G2 are smaller than the opening area (flow passage sectional area) of the communication hole 50 a. Therefore, the lubricating oil O can be suppressed from flowing out to the sub reservoir 152 from the first back pressure chamber 39A with a decreased volume and from flowing out to the sub reservoir 152 from the second back pressure chamber 39B with a decreased volume.

Therefore, the high-pressure lubricating oil O is effectively transferred between the first back pressure chamber 39A and the second back pressure chamber 39B, and the occurrence of the above phenomenon is effectively suppressed.

The lubricant 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 lubricant 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. Therefore, it is necessary to introduce more lubricant oil O into the first back pressure chamber 39A and the second back pressure chamber 39B at the time of high speed rotation than at the time of low speed rotation.

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

Therefore, for example, even when the compressor 100 is tilted at the time of high-speed rotation, the shortage of the lubricant oil O in the sub reservoir 152, and further, the shortage of the lubricant oil O introduced into the first back pressure chamber 39A and the second back pressure chamber 39B can be suppressed. In the present embodiment, the second flow path portion 153b corresponds to the "constriction portion" of the present invention.

Further, since the lubricant oil flow path 153 has the second flow path portion 153B (i.e., a narrow portion) having a flow path cross-sectional area smaller than that of the sub reservoir 152, the lubricant oil O in the main reservoir 151 is hardly affected by the reciprocating motion of the first vane 35A and the reciprocating motion of the second vane 35B. That is, the lubricating oil O in the main reservoir 151 is hardly stirred by the reciprocating motion of the first blade 35A and the reciprocating motion of the second blade 35B. Therefore, the lubricating oil O flowing out from the refrigerant outlet hole 118 together with the high-pressure refrigerant decreases.

In the present embodiment, the one end (lower end) of the first oil passage, which functions as an upper suction port for sucking up the lubricating oil O from the lubricating oil reservoir 150, is open at the bottom of the second closing plate 52. That is, the oil supply passage 70 sucks up the lubricating oil O on the main reservoir 151 side of the second flow passage portion 153B in the lubricating oil reservoir 150, that is, the lubricating oil O which is hardly affected by the reciprocating motion of the first blade 35A and the reciprocating motion of the second blade 35B (which is hardly stirred). Therefore, the lubricant oil O is sucked up by the oil supply passage 70, and the lubricant oil O is stably supplied to the bearing portion of the rotary shaft 200 and the sliding portions of the compression mechanism portion 30.

In the above embodiment, the compressor 100 includes the rotary shaft 200, the motor unit 10 that rotates the rotary shaft 200, and the compression mechanism unit 30 that is driven by the rotary shaft 200, inside the casing 110. However, it is not limited thereto. For example, the compressor 100 may be configured to rotate the rotary shaft 200 by a drive source located outside the casing 110, instead of having the motor unit 10 inside the casing 110. In the case of the compressor 100 configured as described above, a part of the rotary shaft 200 may protrude to the outside of the casing 110, but this case is also included in the case where the compressor has a rotary shaft inside the casing.

Although the embodiments and the modifications of the present invention have been described above, it is needless to say that the present invention is not limited to the above embodiments and the modifications, and further modifications and changes can be made based on the technical idea of the present invention.

Description of the symbols

10 motor portion, 11 stator, 12 rotor, 30 compression mechanism portion, 30A first compression mechanism portion, 30B second compression mechanism portion, 31A first cylinder, 31B second cylinder, 33A first cylinder chamber, 33B second cylinder chamber, 34A first piston member, 34B second piston member, 35A first blade, 35B second blade, 37A first biasing member, 37B second biasing member, 39A first back pressure chamber, 39B second back pressure chamber, 40A first lubricant introduction hole, 40B second lubricant 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 lubricant storage portion, main storage portion, 151 sub-storage portion, 152 lubricant storage portion, 153A first flow passage portion, 153B, 153 first flow passage portion, 200G gap portion, and second flow passage portion, 200G gap portion.

Claims (4)

1. A horizontal rotary compressor having a horizontally extending rotary shaft rotatably supported by a bearing portion and a rotary compression mechanism driven by the rotary shaft, the compression mechanism including a first compression mechanism and a second compression mechanism disposed on both sides of a partition member, and a lubricant oil reservoir for storing lubricant oil provided in an inner bottom of a housing,

each of the first compression mechanism portion and the second compression mechanism portion includes: a cylinder chamber; a piston member that eccentrically rotates within the cylinder chamber in accordance with rotation of the rotary shaft; a vane having a tip portion contacting 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 for introducing a lubricating oil to apply a pressure to the back surface of the vane,

the back pressure chamber of the first compression mechanism communicates with the back pressure chamber of the second compression mechanism via a communication hole formed in the partition member,

the lubricating oil reservoir includes: a main reservoir that stores most of the lubricating oil; a sub reservoir portion that is formed between an outer peripheral portion of the compression mechanism portion and an inner peripheral portion of the housing and that reserves the lubricating oil introduced into the back pressure chamber of the first compression mechanism portion and the back pressure chamber of the second compression mechanism portion; and a lubricating oil flow path that communicates the main reservoir and the sub reservoir,

the lubricating oil flow passage includes a narrowed portion having a flow passage cross-sectional area smaller than a flow passage cross-sectional area of the sub reservoir.

2. The horizontal type rotary compressor of claim 1,

the sub reservoir includes a first gap portion formed between an outer peripheral portion of the first compression mechanism portion and an inner peripheral portion of the housing and having a flow passage sectional area smaller than a flow passage sectional area of the communication hole; and a second gap portion that is formed between an outer peripheral portion of the second compression mechanism portion and an inner peripheral portion of the housing and has a flow passage sectional area smaller than a flow passage sectional area of the communication hole,

the back pressure chamber of the first compression mechanism communicates with the first gap portion of the sub reservoir via a first lubricating oil introduction hole, and the back pressure chamber of the second compression mechanism communicates with the second gap portion of the sub reservoir via a second lubricating oil introduction hole.

3. The horizontal type rotary compressor of claim 1 or 2,

has an oil supply passage for sucking up the lubricating oil in the lubricating oil reservoir and supplying the lubricating oil to at least one of the sliding portions of the bearing portion and the compression mechanism portion,

the oil supply passage is configured to suck up the lubricating oil on the main storage portion side of the lubricating oil storage portion with respect to the narrow portion.

4. The horizontal type rotary compressor as claimed in any one of claims 1 to 3,

a motor unit for rotating the rotating shaft is provided in the housing,

the interior of the housing is divided by a partition wall into a first housing chamber that houses the motor unit and a second housing chamber that houses the compression mechanism unit and is higher in pressure than the first housing chamber, and the lubricant oil reservoir unit is provided in the second housing chamber.

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