JP7470567B2 - Compressor and refrigeration cycle device - Google Patents

Description

The present invention relates to a compressor, etc.

For example, the technology described in Patent Document 1 is known as a technology for improving the lubrication and sealing of rotary compressors. That is, Patent Document 1 describes a rotary compressor in which an oil reservoir recess is provided at a position that defines three sections: a section in which at least one inner surface of the bearing plate communicates with the space inside the cylinder as the piston rotates, a section that is closed by the end face of the piston, and a section that communicates with the inside of the piston.

Japanese Patent Application Laid-Open No. 6-74170

Although Patent Document 1 describes the provision of the oil reservoir recess, it does not disclose the specific arrangement or configuration of the oil reservoir recess. Depending on the position of the oil reservoir recess, the amount of oil supplied to the space inside the cylinder may be too little or too much, which may lead to a decrease in the performance and reliability of the rotary compressor.

Therefore, the objective of the present invention is to provide a compressor etc. with high performance and reliability.

In order to solve the above-mentioned problems, the present invention provides a compressor comprising: an electric motor having a stator and a rotor; a drive shaft that rotates integrally with the rotor; a compression mechanism that compresses a refrigerant as the drive shaft rotates; and a sealed container that houses at least the electric motor, the drive shaft, and the compression mechanism and in which lubricating oil is sealed, the compression mechanism having an annular cylinder, an annular roller that revolves within the cylinder as the electric motor is driven, a first bearing that is provided on one side of the cylinder in the axial direction and supports the drive shaft, and a second bearing that is provided on the other side of the cylinder in the axial direction and supports the drive shaft, and a plate-shaped vane whose tip contacts an outer peripheral surface of the roller and divides a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber, and a plate-shaped vane that communicates with the compression chamber. and a discharge valve provided in a discharge flow passage through which the roller is driven, the space radially inward of the roller is connected to an oil supply passage of the drive shaft, at least one of the first bearing and the second bearing is provided with a recess on a surface facing the cylinder chamber, and when the rotation angle of the roller is 0° and the roller is positioned at top dead center in the cylinder, the recess is located radially inward of the roller when the rotation angle of the roller is 0°, the recess is located between the roller and the cylinder when the rotation angle of the roller is 180°, and when the rotation angle of the roller is 180°, lubricating oil in the recess is directly released into the compression chamber , and the recess is entirely blocked by the roller as the rotation angle of the roller changes from 0° to 180° .

Further, the present invention provides a compressor comprising: an electric motor having a stator and a rotor; a drive shaft rotating integrally with the rotor; two compression mechanism parts which compress a refrigerant as the drive shaft rotates; a partition plate which separates the two compression mechanism parts in the axial direction; and an airtight container which houses at least the electric motor, the drive shaft, the two compression mechanism parts, and the partition plate and in which lubricating oil is sealed, each of the compression mechanism parts having an annular cylinder, an annular roller which revolves within the cylinder as the electric motor is driven, and a bearing which supports the drive shaft, a plate-shaped vane whose tip is in contact with an outer circumferential surface of the roller and which separates a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber, and a discharge valve provided in a discharge flow path which communicates with the compression chamber, the bearing being provided on one axial side of the cylinder, and the discharge valve being provided in a discharge flow path which communicates with the compression chamber, A cutting plate is provided on the other axial side of the cylinder, and a space radially inside the roller is connected to an oil supply passage of the drive shaft. In each of the compression mechanisms, at least one of the bearing and the partition plate has a recess on a surface facing the cylinder chamber. If the rotation angle of the roller is 0° when the roller is located at top dead center in the cylinder, when the rotation angle of the roller is 0°, the recess is located radially inside the roller, when the rotation angle of the roller is 180°, the recess is located between the roller and the cylinder, and when the rotation angle of the roller is 180°, lubricating oil in the recess is released directly into the compression chamber , and the recess is entirely blocked by the roller as the rotation angle of the roller changes from 0° to 180° .

The present invention can provide compressors and other devices with high performance and reliability.

1 is a vertical sectional view of a compressor according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1 in the compressor according to the first embodiment of the present invention. 2 is a partially enlarged vertical cross-sectional view of a compression mechanism portion of the compressor according to the first embodiment of the present invention. FIG. FIG. 2 is an explanatory diagram showing an arrangement of oil pockets in a compression mechanism of the compressor according to the first embodiment of the present invention. 5A to 5C are explanatory diagrams illustrating a process in which a roller moves within a cylinder of the compressor according to the first embodiment of the present invention. FIG. 2 is an explanatory diagram of an oil intake section, a blocking section, and an oil discharge section in an oil pocket of the compressor according to the first embodiment of the present invention. FIG. 11 is a diagram showing experimental results of APF at various oil pocket volume ratios in the compressor according to the first embodiment of the present invention. FIG. 5 is a vertical sectional view of a compressor according to a second embodiment of the present invention. 9 is a cross-sectional view taken along line III-III of FIG. 8 in a compressor according to a second embodiment of the present invention. 4A and 4B are a plan view and a cross-sectional view taken along line IV-IV of a partition plate provided in a compressor according to a second embodiment of the present invention. FIG. 9 is a partial enlarged view of a vertical cross section of an oil pocket of a partition plate provided in a compressor according to a second embodiment of the present invention. FIG. 10 is a partial enlarged view of a vertical cross section of an oil pocket of a partition plate provided in a compressor according to a modified example of the second embodiment of the present invention. FIG. 10 is a vertical sectional view of a compressor according to a third embodiment of the present invention. FIG. 10 is a configuration diagram of an air conditioner according to a fourth embodiment of the present invention.

First Embodiment
<Compressor configuration>
FIG. 1 is a vertical cross-sectional view of a compressor 100 according to the first embodiment.
The compressor 100 is a rotary compressor that compresses a gaseous refrigerant. As shown in Fig. 1, the compressor 100 includes a sealed container 1, an electric motor 2, balance weights 31 and 32, a crankshaft 4 (drive shaft), a compression mechanism 5, and a sound-absorbing cover 6.

The sealed container 1 is a shell-shaped container that houses the electric motor 2, crankshaft 4, compression mechanism 5, etc., and is substantially sealed. The sealed container 1 comprises a cylindrical tube chamber 1a, a lid chamber 1b welded to the upper end of the tube chamber 1a, and a bottom chamber 1c welded to the lower end of the tube chamber 1a. Lubricating oil is sealed in the sealed container 1 to improve the lubricity and sealing properties of the compressor 100, and is stored as an oil reservoir U at the bottom of the sealed container 1.

As shown in FIG. 1, a suction pipe Pi is inserted and fixed into the cylinder chamber 1a of the sealed container 1. The suction pipe Pi is a tube that guides the refrigerant to the cylinder chamber Cy (see FIG. 2) of the compression mechanism 5. In addition, a discharge pipe Po is inserted and fixed into the lid chamber 1b of the sealed container 1. The discharge pipe Po is a tube that guides the refrigerant compressed by the compression mechanism 5 to the outside of the compressor 100.

The electric motor 2 is a driving source that rotates the crankshaft 4, and is installed inside the sealed container 1. As shown in FIG. 1, the electric motor 2 includes a stator 2a, a rotor 2b, and windings 2c. The stator 2a is a cylindrical member made of laminated electromagnetic steel sheets, and is fixed to the inner peripheral wall of the cylindrical chamber 1a. The rotor 2b is a cylindrical member made of laminated electromagnetic steel sheets, and is disposed radially inside the stator 2a. The crankshaft 4 is fixed to the rotor 2b by press-fitting or the like. The windings 2c are wiring through which current flows, and are wound in a predetermined manner and installed on the stator 2a.

The crankshaft 4 is a shaft that rotates together with the rotor 2b as the electric motor 2 is driven. The crankshaft 4 extends in the vertical direction and is rotatably supported by an upper bearing 5c and a lower bearing 5d. As shown in FIG. 1, the crankshaft 4 includes a main shaft 4a and an eccentric portion 4b.

The main shaft 4a is fixed coaxially to the rotor 2b of the electric motor 2. The eccentric portion 4b is a shaft that rotates eccentrically relative to the main shaft 4a and is formed integrally with the main shaft 4a. The eccentric portion 4b is disposed at the bottom of the crankshaft 4, radially inward of the cylinder 5a.

A specific oil supply passage 4c is provided in the axial direction at the bottom of the crankshaft 4. The oil supply passage 4c is a flow path that guides the lubricating oil stored in the sealed container 1 as an oil reservoir U to the compression mechanism 5, etc., and opens at the lower end of the crankshaft 4. A thin metal piece (not shown) that is twisted in a specific manner is provided near the upstream end of the oil supply passage 4c (i.e., near the lower end of the crankshaft 4) as an oil pump. The metal piece rotates together with the crankshaft 4, so that the lubricating oil is pumped up through the oil supply passage 4c.

In addition, multiple horizontal holes h1, h2, and h3 are provided that communicate with the oil supply passage 4c. The sliding surface of the upper bearing 5c is lubricated by the lubricating oil supplied through the horizontal hole h1. The sliding surface of the lower bearing 5d is lubricated by the lubricating oil supplied through the horizontal hole h2. Lubricating oil is also supplied to the radially inner side of the roller 5b through the vertically elongated horizontal hole h3 provided in the eccentric portion 4b. In this way, the space G (see FIG. 3) on the radially inner side of the roller 5b communicates with the oil supply passage 4c of the crankshaft 4.

The compression mechanism 5 is a mechanism that compresses the refrigerant as the crankshaft 4 rotates. That is, the compression mechanism 5 is a mechanism that compresses the refrigerant sucked in through the suction pipe Pi in the compression chamber Com and discharges the compressed refrigerant, and is disposed below the electric motor 2. As shown in FIG. 1, the compression mechanism 5 includes a cylinder 5a, a roller 5b, an upper bearing 5c (first bearing), a lower bearing 5d (second bearing), a vane 5e, a discharge valve 5f, and a vane spring 5g.

FIG. 2 is a cross-sectional view taken along line II-II of FIG.
The cylinder 5a shown in Fig. 2 is an annular (cylindrical) member that forms a cylinder chamber Cy together with the roller 5b, upper bearing 5c, and lower bearing 5d. The cylinder chamber Cy is the space between the cylinder 5a and the roller 5b. The cylinder chamber Cy includes a compression chamber Com and a suction chamber In (see also Fig. 5), but in Fig. 2, the roller 5b has retracted the tip of the vane 5e to the inner peripheral surface of the cylinder 5a, and the entire cylinder chamber Cy becomes the compression chamber Com.

The roller 5b is a member that revolves within the cylinder 5a as the electric motor 2 (see FIG. 1) is driven, and has an annular (cylindrical) shape. The roller 5b revolves inside the cylinder 5a while sliding against the inner peripheral surface of the cylinder 5a. The inner peripheral surface of the roller 5b is in sliding contact with the outer peripheral surface of the eccentric portion 4b.

The vane 5e is a plate-shaped member whose tip (i.e., the tip of the vane 5e on the roller 5b side) contacts the outer peripheral surface of the roller 5b and divides the cylinder chamber Cy between the cylinder 5a and the roller 5b into a suction chamber In and a compression chamber Com (see also Figure 5).

As shown in FIG. 2, an arc-shaped base end 5k is disposed approximately integrally with the cylinder 5a within a predetermined range of the outer circumferential surface of the cylinder 5a. An intake pipe Pi is inserted and fixed into the intake passage h4 that penetrates the base end 5k and the cylinder 5a in the radial direction. Gaseous refrigerant is then guided to the cylinder chamber Cy through the intake pipe Pi and the intake passage h4 in sequence.

A vane spring mounting hole h5 is provided in a predetermined position of the base end 5k in the radial direction up to the vicinity of the outer circumferential surface of the cylinder 5a. The vane spring mounting hole h5 is a hole into which a vane spring 5g (see FIG. 1) described later is mounted.
A radial slit (not shown in FIG. 2) is provided in the cylinder 5a to connect the vane spring mounting hole h5 with the space inside the cylinder 5a in the radial direction. This slit is a space for allowing the vane 5e to reciprocate in the radial direction, and is provided to be slightly wider than the thickness of the vane 5e.

FIG. 3 is a partially enlarged vertical cross-sectional view of the compression mechanism 5 of the compressor.
The vane spring 5g shown in Fig. 3 is a spring that urges the vane 5e radially inward, and is installed in the vane spring mounting hole h5. The pressure difference between the inside and outside of the compression mechanism 5 and the urging force of the vane spring 5g press the tip of the vane 5e against the outer circumferential surface of the roller 5b (see also Fig. 2). As a result, the cylinder chamber Cy, which is the space between the cylinder 5a and the roller 5b, is divided into the suction chamber In and the compression chamber Com (see also Fig. 5). In addition, a discharge notch h6 is provided at a predetermined location on the inner circumferential edge of the upper surface of the cylinder 5a.

This discharge notch h6 is a notch that guides the compressed refrigerant to the discharge valve 5f, and as shown in FIG. 2, its edge is arc-shaped. In addition, the discharge notch h6 and the opening of the suction passage h4 are both close to the vane 5e in the circumferential direction. Specifically, the discharge notch h6 is provided on one side of the vane 5e in the circumferential direction. In addition, the suction passage h4 opens on the other side of the vane 5e in the circumferential direction.

The upper bearing 5c (first bearing) shown in FIG. 3 is a sliding bearing that supports the crankshaft 4 and is provided on the upper side (one axial side) of the cylinder 5a. This upper bearing 5c is fastened together with the cylinder 5a and the lower bearing 5d by a number of bolts T (see FIG. 2), and is further fixed to the inner peripheral wall of the cylindrical chamber 1a (see FIG. 1). In the example of FIG. 3, a predetermined annular groove h7 is provided on the end face of the upper bearing 5c on the cylinder 5a side to reduce localized one-sided contact between the crankshaft 4 and the upper bearing 5c.

In the upper bearing 5c, a predetermined hole is provided as a discharge port h8 at a position corresponding to the discharge notch h6 of the cylinder 5a. The "discharge flow passage" that communicates with the compression chamber Com is composed of the discharge notch h6 and the discharge port h8.

The discharge valve 5f shown in FIG. 3 is a valve for discharging the compressed refrigerant into the space inside the sealed container 1 (see FIG. 1), and is provided in the "discharge flow path" described above. In the example of FIG. 3, the discharge valve 5f is installed in the upper bearing 5c so as to block the discharge port h8. When the discharge pressure of the compressed refrigerant overcomes the elastic force of the discharge valve 5f, which is a leaf spring, the discharge valve 5f opens.

The lower bearing 5d (second bearing) is a sliding bearing that supports the crankshaft 4, and is provided below the cylinder 5a (the other axial side). In the example of Fig. 3, a predetermined annular groove h9 is provided in the end face of the lower bearing 5d on the cylinder 5a side to reduce localized one-sided contact between the crankshaft 4 and the lower bearing 5d.
The lower bearing 5d is provided with a concave oil pocket h10 (recess) on the surface facing the cylinder chamber Cy (see also FIG. 5). Details will be described later, but while the roller 5b revolves within the cylinder 5a, lubricating oil is taken into the oil pocket h10 in the space G on the radial inside of the roller 5b, and this lubricating oil is then supplied to the cylinder chamber Cy, and this cycle is repeated periodically. The arrangement of the oil pocket h10, etc., is one of the main features of this embodiment.

The sound-absorbing cover 6 (see also FIG. 1) is a cover for suppressing noise caused by the compression of the refrigerant, and is fixed to the upper bearing 5c while covering the upper surface of the upper bearing 5c. The sound-absorbing cover 6 is provided with multiple holes (not shown in FIG. 1) for releasing the compressed refrigerant into the space inside the sealed container 1.

FIG. 4 is an explanatory diagram showing the arrangement of the oil pocket h10 in the compression mechanism 5.
The Y-axis shown in Fig. 4 is perpendicular to the central axis Z (see also Fig. 1), parallel to the side surface of the vane 5e, and is a predetermined axis passing through the vane 5e as well as the cylinder 5a and the roller 5b. The axis perpendicular to both the central axis Z and the Y-axis is defined as the X-axis.

In the example of FIG. 4, the oil pocket h10 is provided near the vane 5e as a circular hole with a relatively shallow bottom. To explain in more detail, the oil pocket h10 is provided at a position a distance L1 away from the vane 5e toward the discharge notch h6 in the X-axis direction so as not to overlap with the vane 5e reciprocating in the radial direction (so that the oil pocket h10 is not blocked by the vane 5e). The distance L1 is preferably within a range of 0.5 mm to 2.0 mm, for example, but is not limited to this. By providing the oil pocket h10 near the vane 5e in this way, the lubricating oil discharged from the oil pocket h10 into the cylinder chamber Cy is more likely to adhere to the side and tip of the vane 5e. Therefore, the sliding surfaces of the vane 5e, the cylinder 5a, and the roller 5b can be sufficiently lubricated.

Furthermore, the oil pocket h10 is located in a position in the Y-axis direction where the oil intake section Δθ _in (see FIG. 6) and the oil discharge section Δθ _out (see FIG. 6) are approximately equal. The oil intake section Δθ _in is the range of the rotation angle of the roller 5b when lubricating oil is taken into the oil pocket h10. More specifically, the oil intake section Δθ in is the range of the rotation angle of the roller 5b when the oil pocket h10 (recess) is located radially _inward of the roller 5b.

On the other hand, the oil release section Δθ _out is the range of the rotation angle of the roller 5b when the lubricating oil is released from the oil pocket h10. More specifically, the range of the rotation angle of the roller 5b when the oil pocket h10 (recess) is located between the roller 5b and the cylinder 5a is the oil release section Δθ _out . By making the oil intake section Δθ _in and the oil release section Δθ _out approximately equal, the amount of lubricating oil taken into the oil pocket h10 per unit time and the amount of lubricating oil released from the oil pocket h10 become approximately equal. Therefore, the volumetric efficiency when the lubricating oil is intermittently supplied to the compression chamber Com using the oil pocket h10 can be improved.

The diameter of the oil pocket h10 is smaller than the radial thickness of the roller 5b. More specifically, the diameter of the oil pocket h10 is shorter than the radial length of the seal surface (annular lower surface) of the roller 5b. This allows the oil pocket h10 to be temporarily blocked by the seal surface of the roller 5b in the blockage section Δθ _occ (see FIG. 6) between the oil intake section Δθ _in and the oil discharge section Δθ _out .

FIG. 5 is an explanatory diagram of the process in which the roller 5b moves inside the cylinder 5a.
The rotation angle θ shown in Fig. 5 is the rotation angle of the roller 5b moving (revolving) in the cylinder 5a. The rotation angle of the roller 5b when the roller 5b is located at the "top dead center" (TDC) in the cylinder 5a is set to 0°. The "top dead center" refers to the position of the roller 5b when the compression of the refrigerant starts in the compression chamber Com. In other words, the "top dead center" refers to the position of the roller 5b when the center of the roller 5b is closest to the tip of the vane 5e (when the vane 5e is most retracted) in the direction in which the vane 5e extends in a plan view (Y-axis direction in Fig. 4).

As shown in FIG. 4, when the rotation angle of the roller 5b is 0°, the oil pocket h10 (recess) is located on the radial inside of the roller 5b. Therefore, the lubricating oil supplied to the space G on the radial inside of the roller 5b via the oil supply passage 4c (see FIG. 3) and the horizontal hole h3 (see FIG. 3) in sequence is taken into the oil pocket h10.

In addition, when the rotation angle of the roller 5b is 90°, the oil pocket h10 (recess) is blocked by the roller 5b. This prevents the radially inner and outer spaces of the roller 5b from communicating with each other through the oil pocket h10. Therefore, even if the oil pocket h10 is provided, there is almost no risk of a decrease in the efficiency of compressing the refrigerant in the compression mechanism 5.

When the rotation angle of the roller 5b is 180°, an oil pocket h10 (recess) is located between the roller 5b and the cylinder 5a. As a result, the lubricating oil in the oil pocket h10 is released into the compression chamber Com. Meanwhile, gaseous refrigerant enters the oil pocket h10 to replace the lubricating oil.

The space G on the radial inside of the roller 5b is connected to the space inside the sealed container 1 (but outside the compression mechanism 5: see FIG. 1) through the horizontal hole h3 (see FIG. 3) and the oil supply passage 4c (see FIG. 3). Therefore, when the oil pocket h10 is blocked by the roller 5b at θ=90°, the pressure of the lubricating oil in the oil pocket h10 is approximately equal to the refrigerant pressure (discharge pressure 9) in the sealed container 1. On the other hand, the pressure of the refrigerant in the compression chamber Com at θ=180° is lower than the specified discharge pressure because it is in the middle of compression. Therefore, at θ=180°, the lubricating oil in the oil pocket h10 is diffused into the compression chamber Com, which is at a relatively low pressure.

In addition, when the rotation angle of the roller 5b is 270°, the oil pocket h10 (recess) is blocked by the roller 5b. This prevents the radially inner and outer spaces of the roller 5b from communicating with each other via the oil pocket h10.

When the rotation angle of roller 5b returns to 0° (i.e., top dead center), the high-pressure lubricating oil present on the radial inside of roller 5b re-enters oil pocket h10. In this way, lubricating oil is intermittently supplied to compression chamber Com.

The oil pocket h10 (recess) is provided on the "discharge flow path" side of the vane 5e in the circumferential direction. As described above, the "discharge flow path" is a flow path that includes the discharge notch h6 (see FIG. 4) and the discharge port h8 (see FIG. 4). As a result, the refrigerant that has been diffused into the compression chamber Com (for example, "θ = 180°" in FIG. 5) naturally collects near the tip of the vane 5e as the compression chamber Com shrinks with the movement of the roller 5b (for example, "θ = 270°" in FIG. 5).

As a result, lubricating oil is more likely to adhere to the tip of the vane 5e shown in FIG. 4 as well as to the side of the vane 5e facing the compression chamber Com. The tip and side of the vane 5e are particularly prone to sliding friction within the compression mechanism 5. The lubricating oil diffused into the compressor Com also sufficiently lubricates the vane 5e as well as the sliding surfaces of the cylinder 5 and roller 5b.

In addition, the pressure difference between the suction chamber In (see FIG. 5) and the compression chamber Com (see FIG. 5) creates a force that presses the vane 5e toward the suction pipe Pi (i.e., toward the suction passage h4: see FIG. 3). As a result, lubricating oil enters the tiny gap between the side of the vane 5e on the discharge notch h6 side and the wall surface of the cylinder 5a, and the sliding surfaces of the cylinder 5a and the vane 5e are sufficiently lubricated by the lubricating oil from the oil pocket h10.

The rear end of the vane 5e on the vane spring 5g side faces the space inside the sealed container 1 (see Figure 1). Therefore, the mist-like lubricating oil inside the sealed container 1 also adheres to the rear end of the vane 5e. As a result, as the vane 5e reciprocates, the lubricating oil also flows onto the side of the vane 5e on the suction chamber In side, lubricating the sliding surfaces of the cylinder 5a and the vane 5e.

FIG. 6 is an explanatory diagram of an oil intake section Δθ _in , a blocking section Δθ _occ , and an oil discharge section Δθ _out in an oil pocket (see FIG. 5 as appropriate).
6 is the rotation angle of the roller 5b moving (revolving) inside the cylinder 5a, as described above, and the rotation angle at the top dead center is θ = 0°. As the roller 5b moves, the intake of lubricating oil into the oil pocket h10 (oil intake section Δθ _in ), the blocking of the oil pocket h10 (blocking section Δθ _occ ), the release of lubricating oil into the compression chamber Com (oil release section Δθ _out ), and the blocking of the oil pocket h10 (blocking section Δθ _occ ) are sequentially repeated.

As shown in Fig. 6, it is preferable that the oil intake section Δθ _in and the oil discharge section Δθ _out are approximately equal. More specifically, it is preferable that the oil intake section Δθ _in and the oil discharge section Δθ _out are each 140° or more and 165° or less. This allows the lubricating oil taken into the oil pocket h10 in the oil intake section Δθ _in to be discharged to the compression chamber Com in the oil discharge section Δθ _out without waste. Therefore, it is possible to improve the volumetric efficiency when the lubricating oil is intermittently supplied from the oil pocket h10 to the compression chamber Com.

The magnitude relationship between the oil intake section Δθ _in and the oil discharge section Δθ _out is not particularly limited. For example, the oil intake section Δθ _in =150°, while the oil discharge section Δθ _out =160°. Also, for example, the oil intake section Δθ _in =165°, while the oil discharge section Δθ _out =140°.

FIG. 7 is a diagram showing the experimental results of APF in terms of oil pocket volume ratio (see FIG. 2 where appropriate).
The horizontal axis of Fig. 7 is the oil pocket volume ratio (hereinafter referred to as the oil pocket volume ratio Vpr), and the vertical axis is the APF (Annual Performance Factor) of the air conditioner using the compressor 100 (see Fig. 1) of this embodiment. The oil pocket volume ratio Vpr is the ratio of the volume Vp of the oil pocket h10 (recess) to the stroke volume of the cylinder 5a, and is calculated based on the following formula (1). The "stroke volume" mentioned above is the volume of the cylinder chamber Cy (see Fig. 2) when the roller rotation angle θ = 0°.

Vpr = Vp/Vth x 100 ... (1)

Then, while the diameter of the oil pocket h10 is set to a predetermined constant value, the depth dimension of the oil pocket h10 is appropriately changed, and the APF is calculated for each of the multiple cases with different oil pocket volume ratios, and plotted as points indicated by black circles in Figure 7. According to the results of this experiment, the oil pocket volume ratio Vpr, which is the ratio of the volume of the oil pocket h10 to the stroke volume, is preferably 0.001% or more and 0.019% or less. This is because if the oil pocket volume ratio Vpr is within the above-mentioned range, the APF will be higher than when no oil pocket h10 is provided (when the oil pocket volume ratio Vpr = 0).

In particular, when the oil pocket volume ratio Vpr was 0.01%, the increase in APF compared to when no oil pocket h10 was provided (when Vpr = 0) was 0.36%, which was the highest APF.

The open circle indicated by the symbol J is the experimental result when an oil pocket (not shown) is provided in the same position as that shown in Figure 2 of the prior art document mentioned above. In this case, the oil pocket is far from the vane 5e, so the area around the vane 5e, where sliding friction is large, is not sufficiently lubricated, and the APF is lower than when no oil pocket is provided (oil pocket volume ratio Vpr = 0). In contrast, according to the first embodiment, as mentioned above, the area around the vane 5e is well lubricated and the sealing property of the compression chamber Com is maintained, so the APF can be significantly higher than before.

For example, when the stroke volume Vth = 9.5 ml/rev, if the diameter of the oil pocket h10 is 3 mm, and the depth of the oil pocket h10 is 0.13 mm, the oil pocket volume ratio Vpr will be approximately 0.01%. In this way, by providing a very small oil pocket h10 on the upper surface of the lower bearing 5d, the performance and reliability of the compressor 100 can be improved.

＜Effects＞
According to the first embodiment, the lubricating oil is intermittently supplied to the compression chamber Com from the oil pocket h10 of the lower bearing 5d, so that the sealing property of the compression chamber Com can be improved. In addition, by providing the oil pocket h10 near the vane 5e, each sliding surface of the vane 5e and the cylinder 5a can be sufficiently lubricated. In particular, by providing the oil pocket h10 on the discharge notch h6 side (see FIG. 4) from the vane 5e, the lubricating oil is easily attached to the tip and side of the vane 5e. Therefore, even during low-speed rotation where an oil film is difficult to form, the lubrication and sealing property of the compression mechanism 5 (see FIG. 4) can be improved. In addition, even when using the refrigerant R32, which is likely to become high temperature and high pressure, the compressor 100 with high performance and reliability can be provided.

Furthermore, by making the oil intake section Δθ _in and the oil discharge section Δθ _out approximately equal (see FIG. 6 ), almost all of the lubricating oil that has entered the oil pocket h10 is discharged to the compression chamber Com. This ensures sufficient lubrication and sealing of the compression mechanism 5 even if the volume of the oil pocket h10 is relatively small. If the volume of the oil pocket h10 is too large, the amount of refrigerant that enters the oil pocket h10 in the oil discharge section Δθ _out (the amount of refrigerant at a relatively low pressure in the middle of compression) increases, and this refrigerant is discharged into the sealed container 1 at a pressure approximately equal to the discharge pressure. Therefore, in consideration of high efficiency in refrigerant compression, it is desirable for the volume of the oil pocket h10 to be small.

Second Embodiment
The second embodiment differs from the first embodiment (see FIG. 1) in that the compressor 100A (see FIG. 8) is provided with two compression mechanism units 51, 52 (see FIG. 8). The second embodiment also differs from the first embodiment in that oil pockets h11, h12 (see FIG. 8) are provided on a partition plate 50 (see FIG. 8) that separates the compression mechanism units 51, 52. The second embodiment is similar to the first embodiment in other respects. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

FIG. 8 is a vertical cross-sectional view of a compressor 100A according to the second embodiment.
As shown in FIG. 8, the compressor 100A includes a sealed container 1, an electric motor 2, a crankshaft 4A (drive shaft), two compression mechanisms 51 and 52, a partition plate 50, and sound-absorbing covers 61 and 62.

The sealed container 1 contains the electric motor 2, the crankshaft 4A, two compression mechanisms 51, 52, a partition plate 50, etc., and is filled with lubricating oil.
The crankshaft 4A is a shaft that rotates integrally with the rotor 2b, and includes a main shaft 4a and eccentric portions 41b and 42b. One eccentric portion 41b is eccentric to the opposite side in plan view relative to the other eccentric portion 42b. This allows the rotational imbalance caused by the movement of one eccentric portion 41b to be counteracted by the other eccentric portion 42b, suppressing vibration of the compressor 100A. The inner peripheral surface of the upper roller 51b is in sliding contact with one eccentric portion 41b, and the inner peripheral surface of the lower roller 52b is in sliding contact with the other eccentric portion 42b.

The two compression mechanisms 51, 52 shown in FIG. 8 are mechanisms that compress the refrigerant as the crankshaft 4 rotates. These compression mechanisms 51, 52 are fastened together with a partition plate 50, which will be described later, by a number of bolts T (see FIG. 9). The upper compression mechanism 51 compresses the gaseous refrigerant introduced through the suction pipe P1i. The refrigerant compressed by the compression mechanism 51 in this manner is released into the space within the sealed container 1 through the discharge valve 51f and the holes (not shown) in the sound-absorbing cover 61 in sequence.

Meanwhile, the lower compression mechanism 52 compresses the gaseous refrigerant introduced through the suction pipe P2i. The refrigerant compressed in this manner by the compression mechanism 52 is released into the space within the sealed container 1 through the discharge valve 52f and the holes (not shown) in the sound-absorbing cover 62 in sequence. The sound-absorbing cover 62 is fixed to the lower bearing 5d while covering the lower surface of the lower bearing 5d.

As shown in FIG. 8, the upper compression mechanism 51 includes a cylinder 51a, a roller 51b, an upper bearing 5c (bearing), a vane 51e, a discharge valve 51f, and a vane spring 51g. Note that each configuration of the compression mechanism 51 is similar to that of the compression mechanism 5 of the first embodiment (see FIG. 1), so a description thereof will be omitted.

The lower compression mechanism 52 includes a cylinder 52a, a roller 52b, a lower bearing 5d (bearing), a vane 52e, a discharge valve 52f, and a vane spring 52g. The configuration of the compression mechanism 52 is similar to that of the compression mechanism 5 of the first embodiment (see FIG. 1), so a description thereof will be omitted.

The partition plate 50 shown in FIG. 8 is a plate that separates the two compression mechanism parts 51, 52 in the axial direction of the rotor 2b, and has an annular shape (see also FIG. 10). If the upper bearing 5c (or the lower bearing 5d) is provided on "one axial side" of the cylinder 51a, the partition plate 50 is provided on "the other axial side" of the cylinder 51a.

An oil pocket h11 (recess) is provided on the surface (upper surface) of the partition plate 50 facing the cylinder chamber (not shown) of the upper compression mechanism section 51. Another oil pocket h12 (recess) is provided on the surface (lower surface) of the partition plate 50 facing the cylinder chamber (see FIG. 9) of the lower compression mechanism section 52. In this way, in the second embodiment, the partition plate 50 is provided with the oil pockets h11, h12.
The oil pocket h12 is provided on the lower surface of the partition plate 50, and lubricating oil also adheres to this oil pocket h12. Therefore, as the rotor 52b moves, lubricating oil is intermittently supplied from the oil pocket h12 to the compression chamber Com2.

FIG. 9 is a cross-sectional view taken along line III-III of FIG.
As shown in Fig. 9, the oil pocket h12 (recess) is provided closer to the discharge notch h26 (discharge flow path side) than the vane 52e in the circumferential direction. This allows the lubricating oil to spread to each sliding surface of the vane 52e, the cylinder 52a, and the roller 52b. Similarly, the other oil pocket h11 (recess: see Fig. 8) is also provided closer to the discharge notch (discharge flow path side: no reference symbol is shown) than the vane 51e (see Fig. 8) in the circumferential direction.

Also, although not shown in the figure, if the rotation angle of roller 52b when roller 52b is located at the top dead center within cylinder 52a is set to 0°, when the rotation angle of roller 52b is 0°, an oil pocket h12 (recess) is located radially inward of roller 52b.
When the rotation angle of the roller 52b is 180°, an oil pocket h12 (recess) is located between the roller 52b and the cylinder 52a, which allows the sliding surfaces of the vane 52e, the cylinder 52a, and the roller 52b to be appropriately lubricated.
Furthermore, when the rotation angle of the roller 52b is 90° and when the rotation angle of the roller 52b is 270°, the oil pocket h12 (recess) is blocked by the roller 52b, which prevents the spaces on the radial inside and outside of the roller 52b from communicating with each other via the oil pocket h12.
The same can be said about the rotation angle of the roller 51b in the upper compression mechanism 51 (see FIG. 8).

In addition, it is preferable that the range of the rotation angle of the roller 52b when the oil pocket h12 (recess) is located radially inside the roller 52b, and the range of the rotation angle of the roller 52b when the oil pocket h12 is located between the roller 52b and the cylinder 52a are 140° or more and 165° or less. This allows almost all of the lubricating oil that has entered the oil pocket h12 to be released into the compression chamber Com, thereby ensuring sufficient lubrication and sealing properties of the compression mechanism 52. The same can be said for the upper compression mechanism 51 (see FIG. 8).

FIG. 10 is a plan view and a cross-sectional view taken along line IV-IV of the partition plate 50. As shown in FIG.
As shown in Fig. 10, the partition plate 50 is provided with a hole h15 for passing the crankshaft 4A (see Fig. 8) therethrough. In addition, the partition plate 50 is provided with three holes h14 for silencing, as well as four holes h16 for passing the bolts T (see Fig. 9) therethrough.

A pair of oil pockets h11, h12 are provided in the partition plate 50 at approximately the same position in a plan view. The radial and circumferential positions of the oil pockets h11, h12 in a plan view may be approximately the same as in FIG. 10, or may be different.

The oil pockets h11, h12 may be formed during a sintering process of the partition plate 50 using a specified metal material. Alternatively, the oil pockets h11, h12 may be formed by cutting using an end mill (not shown). This reduces the processing costs involved in forming the oil pockets h11, h12.

FIG. 11A is a partially enlarged vertical cross-sectional view of the oil pocket h11 of the partition plate 50. FIG.
In the example shown in FIG. 11A, the diameter of the oil pocket h11 (see also FIG. 10) which is circular in plan view is length L2, and the depth from the upper surface of the partition plate 50 to the bottom surface of the oil pocket h11 is length L3. When designing such an oil pocket h11, it is preferable that the ratio of the volume of the oil pocket h11 (recess) to the stroke volume of the cylinder 51a (see FIG. 8) is 0.001% or more and 0.019% or less. This makes it possible to increase the APF of the air conditioner equipped with the compressor 100A (see FIG. 8) more than when the oil pocket h11 is not provided. The same can be said about the other oil pocket h12 (see FIG. 10) of the partition plate 50.

FIG. 11B is a partial enlarged view of a vertical cross section of an oil pocket h11s of a partition plate 50B according to a modified example of the second embodiment.
As shown in Fig. 11B, for example, the oil pocket h11s may be cut using a drill (not shown) so that it has a predetermined volume. That is, an oil pocket h12s may be provided whose surface has a V-shape in cross section so that its diameter is length L4 and its depth is length L5. With this configuration, the same effect as in Fig. 11A can be achieved.

Third Embodiment
The third embodiment differs from the first embodiment in that a compressor 100C (see FIG. 12) has a predetermined recessed portion h17 in a vane 5Ce in addition to an oil pocket h10 provided in a lower bearing 5d. The other configurations are the same as those of the first embodiment (see FIG. 1). Therefore, only the parts that are different from the first embodiment will be described, and the description of the overlapping parts will be omitted.

FIG. 12 is a vertical cross-sectional view of a compressor 100C according to the third embodiment.
12, the compression mechanism 5C includes a vane 5Ce having a recessed portion h17 on its side surface. The recessed portion h17 is a recess for taking in lubricating oil when the vane 5Ce retreats and for supplying lubricating oil to the compression chamber Com (or a cylinder chamber including the compression chamber Com) when the vane 5Ce advances toward the central axis Z.

For example, when the rotation angle of the roller 5b is 0°, at least a part of the recessed portion h17 is present on the radial outside of the cylinder 5a, and when the rotation angle of the roller 5b is 180°, at least a part of the recessed portion h17 is present between the roller 5b and the cylinder 5a. This allows lubricating oil to be intermittently supplied to the compression chamber Com, etc. Therefore, combined with the supply of lubricating oil via the oil pocket h10, it is possible to sufficiently supply lubricating oil to each sliding surface of the cylinder 5a and the vane 5Ce. The recessed portion h17 may be provided only on one side of the vane 5Ce, which has a thin plate shape, or may be provided on both side surfaces.

＜Effects＞
According to the third embodiment, by providing the recessed portion h17 on the side surface of the vane 5Ce, it is possible to sufficiently supply lubricating oil to each sliding surface of the cylinder 5a and the vane 5Ce.

Fourth Embodiment
In the fourth embodiment, a configuration of an air conditioner W (see FIG. 13) including the compressor 100 (see FIG. 1) described in the first embodiment will be described. Note that the configuration of the compressor 100 is similar to that described in the first embodiment (see FIG. 1), and therefore a description thereof will be omitted.

FIG. 13 is a configuration diagram of an air conditioner W according to the fourth embodiment.
The solid arrows in FIG. 13 indicate the flow of the refrigerant during heating operation.
The dashed arrows in FIG. 13 indicate the flow of refrigerant during cooling operation.
The air conditioner W (refrigeration cycle device) is a device that performs air conditioning such as cooling and heating. As shown in Fig. 13, the air conditioner W includes a compressor 100, a condenser E1, an expansion valve V, an evaporator E2, an accumulator M, a first fan F1, and a second fan F2.

The compressor 100 is a device that compresses a gaseous refrigerant, and has a configuration similar to that of the first embodiment (see FIG. 1 ). Note that, as the refrigerant, for example, refrigerant R32 is used, but the refrigerant is not limited thereto.
The condenser E1 is a heat exchanger in which heat is exchanged between a refrigerant flowing through a heat transfer tube (not shown) thereof and air sent from the first fan F1.
The first fan F1 is a fan that sends air into the condenser E1, and is installed near the condenser E1.

The evaporator E2 is a heat exchanger in which heat is exchanged between the refrigerant flowing through its heat transfer tubes (not shown) and the air sent from the second fan F2.
The second fan F2 is a fan that sends air to the evaporator E2, and is installed near the evaporator E2.

The expansion valve V has the function of reducing the pressure of the refrigerant condensed in the condenser E1. The refrigerant reduced in pressure by the expansion valve V is then guided to the evaporator E2. In this way, in the refrigerant circuit Q shown in FIG. 13, the refrigerant circulates through the compressor 100, the condenser E1, the expansion valve V, and the evaporator E2 in sequence. The refrigerant evaporated in the evaporator E2 is separated into gas and liquid in the accumulator M, and the gaseous refrigerant is then guided to the compressor 100.

When the air conditioning operation mode is switched from one of cooling operation and heating operation to the other, a four-way valve (not shown) may be provided as appropriate to switch the refrigerant flow path.

＜Effects＞
According to the fourth embodiment, sufficient lubricating oil is supplied to the compression chamber Com (see FIG. 1) of the compression mechanism 5 (see FIG. 1) of the compressor 100, so that the sealing performance of the compression chamber Com is well maintained, and the lubrication of each sliding surface of the vane 5e (see FIG. 1), the cylinder 5a (see FIG. 1), and the roller 5b (see FIG. 1) is also maintained. Therefore, according to the fourth embodiment, it is possible to provide an air conditioner W with high performance and reliability.

<<Variations>>
Although the compressor 100 according to the present invention has been described in each embodiment, the present invention is not limited to these descriptions and various modifications can be made.
For example, in the first embodiment (see FIG. 1), a configuration in which the oil pocket h10 is provided on the upper surface of the lower bearing 5d has been described, but this is not limited thereto. That is, an oil pocket may be provided on the lower surface of the upper bearing 5c, or an oil pocket may be provided on both the upper bearing 5c and the lower bearing 5d. In other words, in the compressor 100, an oil pocket (recess) may be provided on the surface facing the cylinder chamber Cy of at least one of the upper bearing 5c (first bearing) and the lower bearing 5d (second bearing).

In the second embodiment (see FIG. 8), the partition plate 50 is provided with oil pockets h11 and h12, but the present invention is not limited to this. That is, in the compression mechanism 51, at least one of the upper bearing 5c (bearing) and the partition plate 50 may be provided with an oil pocket (recess) on the surface facing the cylinder chamber. In addition, in the compression mechanism 52, at least one of the lower bearing 5d (bearing) and the partition plate 50 may be provided with an oil pocket (recess) on the surface facing the cylinder chamber.

In the second embodiment (see FIG. 8), the compressor 100A is described as having two compression mechanism parts 51 and 52, but the present invention is not limited to this. That is, the compressor may be configured to have three or more compression mechanism parts (not shown). In this configuration, the top compression mechanism part (not shown) is provided with an oil pocket on at least one of the surfaces of the upper bearing and the partition plate facing the cylinder chamber, and the bottom compression mechanism part (not shown) is provided with an oil pocket on at least one of the surfaces of the lower bearing and the partition plate facing the cylinder chamber. In addition, each of the remaining compression mechanism parts (not shown) other than the top and bottom compression mechanism parts is provided with an oil pocket on at least one of the surfaces of the pair of partition plates sandwiching the rotor and the cylinder facing the cylinder chamber. Even with this configuration, the same effects as those of each embodiment are achieved. It is also possible to provide an oil pocket in at least one of the multiple compression mechanism parts described above, and not provide an oil pocket in the remaining parts.

In addition, the embodiments may be combined as appropriate. For example, the second embodiment may be combined with the fourth embodiment. That is, the air conditioner W (see FIG. 13) may be configured to include a compressor 100A in which oil pockets h11 and h12 are provided in the partition plate 50 (see FIG. 8).
Also, the oil pocket h10 of the lower bearing 5d may be omitted from the compressor 100C of the third embodiment (see FIG. 12), and the recessed portion h17 of the vane 5e may be left. Even with this configuration, the sealing and lubrication properties of the compression mechanism 5C are maintained excellent.

In addition, in each embodiment, the compressor 100 is vertically disposed, but this is not limiting. That is, each embodiment can be applied to a case where the compressor 100 is horizontally or obliquely disposed.
Moreover, the air conditioner W (see FIG. 13) described in the fourth embodiment can be applied to various types of air conditioners, such as room air conditioners, packaged air conditioners, and multi-air conditioners for buildings.

In the fourth embodiment, the case where the "refrigeration cycle apparatus" including the compressor 100 is the air conditioner W (see FIG. 13) has been described, but the present invention is not limited thereto. That is, the "refrigeration cycle apparatus" including the compressor 100 may be a refrigerator, a hot water heater, an air conditioning and hot water supply system, or the like.
Furthermore, the refrigerant used in the air conditioner W is not limited to refrigerant R32, and various types of refrigerants can be used, such as refrigerant R410A, refrigerant R600a, and refrigerants whose main component is propane.

In addition, each embodiment has been described in detail to clearly explain the present invention, and is not necessarily limited to having all of the configurations described. In addition, it is possible to add, delete, or replace part of the configuration of each embodiment with other configurations.
Furthermore, the mechanisms and configurations described above are those considered necessary for the explanation, and do not necessarily show all mechanisms and configurations of the product.

100, 100A, 100C Compressor 1 Sealed container 2 Electric motor 2a Stator 2b Rotor 4, 4A Crankshaft (drive shaft)
4c Oil supply passage 5, 51, 52, 5C Compression mechanism 5c Upper bearing (first bearing, bearing)
5d Lower bearing (second bearing, bearing)
5a, 51a, 52a Cylinder 5b, 51b, 52b Roller
5e, 51e, 52e, 5Ce Vane 5f, 51f, 52f Discharge valve 50, 50B Partition plate
Com, Com2 compression chamber Cy, Cy2 cylinder chamber E1 condenser E2 evaporator G space h6, h26 discharge notch (discharge flow path)
h8 Discharge port (discharge flow path)
h10, h11, h11s, h12, h12s Oil pocket (recess)
h17 Depression
In: suction chamber Q: refrigerant circuit V: expansion valve W: air conditioner (refrigeration cycle device)
Z central axis

Claims (10)

an electric motor having a stator and a rotor;
A drive shaft that rotates integrally with the rotor;
a compression mechanism that compresses a refrigerant as the drive shaft rotates;
a sealed container that houses at least the electric motor, the drive shaft, and the compression mechanism and in which lubricating oil is sealed;
The compression mechanism includes:
An annular cylinder;
an annular roller that revolves within the cylinder as the electric motor is driven;
a first bearing provided on one side of the cylinder in the axial direction and supporting the drive shaft;
a second bearing provided on the other axial side of the cylinder and supporting the drive shaft;
a plate-like vane whose tip contacts an outer peripheral surface of the roller and divides a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber;
a discharge valve provided in a discharge flow passage communicating with the compression chamber,
A space on the radially inner side of the roller communicates with an oil supply passage of the drive shaft,
At least one of the first bearing and the second bearing has a recess on a surface facing the cylinder chamber,
When the rotation angle of the roller is 0° when the roller is located at the top dead center in the cylinder, the recess is located on the radially inner side of the roller when the rotation angle of the roller is 0°, and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180°,
When the rotation angle of the roller is 180°, the lubricating oil in the recess is directly discharged into the compression chamber ,
a compressor , wherein the entire recess is blocked by the roller as the rotation angle of the roller changes from 0° to 180°. an electric motor having a stator and a rotor;
A drive shaft that rotates integrally with the rotor;
two compression mechanisms for compressing a refrigerant as the drive shaft rotates;
a partition plate that axially separates the two compression mechanism units;
a sealed container that houses at least the electric motor, the drive shaft, the two compression mechanism parts, and the partition plate and in which lubricating oil is sealed,
Each of the compression mechanism units is
An annular cylinder;
an annular roller that revolves within the cylinder as the electric motor is driven;
a bearing for supporting the drive shaft;
a plate-like vane whose tip contacts an outer peripheral surface of the roller and divides a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber;
a discharge valve provided in a discharge flow passage communicating with the compression chamber,
The bearing is provided on one side of the cylinder in the axial direction,
The partition plate is provided on the other side of the cylinder in the axial direction,
A space on the radially inner side of the roller communicates with an oil supply passage of the drive shaft,
In each of the compression mechanisms, at least one of the bearing and the partition plate is provided with a recess on a surface facing the cylinder chamber,
When the rotation angle of the roller is 0° when the roller is located at the top dead center in the cylinder, the recess is located on the radially inner side of the roller when the rotation angle of the roller is 0°, and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180°,
When the rotation angle of the roller is 180°, the lubricating oil in the recess is directly discharged into the compression chamber ,
a compressor , wherein the entire recess is blocked by the roller as the rotation angle of the roller changes from 0° to 180°. 3. The compressor according to claim 1, wherein the recess is closed by the roller when the rotation angle of the roller is 90 degrees and when the rotation angle of the roller is 270 degrees. 3. The compressor according to claim 1, wherein the range of the rotation angle of the roller when the recess is located radially inside the roller, and the range of the rotation angle of the roller when the recess is located between the roller and the cylinder are each 140° or more and 165° or less. The compressor according to claim 1 or 2, wherein the recess is provided closer to the discharge flow passage than the vane in the circumferential direction. 3. The compressor according to claim 1, wherein a ratio of a volume of the recess to a stroke volume, which is a volume of the cylinder chamber when the rotation angle of the roller is 0°, is 0.001% or more and 0.019% or less. A recess is provided on a side surface of the vane,
3. The compressor according to claim 1, wherein when the rotation angle of the roller is 0°, at least a part of the recess is present on a radially outer side of the cylinder, and when the rotation angle of the roller is 180°, at least a part of the recess is present between the roller and the cylinder. The compressor includes a condenser, an expansion valve, and an evaporator.
The compressor includes:
an electric motor having a stator and a rotor;
A drive shaft that rotates integrally with the rotor;
a compression mechanism that compresses a refrigerant as the drive shaft rotates;
a sealed container that houses at least the electric motor, the drive shaft, and the compression mechanism and in which lubricating oil is sealed;
The compression mechanism includes:
An annular cylinder;
an annular roller that revolves within the cylinder as the electric motor is driven;
a first bearing provided on one side of the cylinder in the axial direction and supporting the drive shaft;
a second bearing provided on the other axial side of the cylinder and supporting the drive shaft;
a plate-like vane whose tip contacts an outer peripheral surface of the roller and divides a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber;
a discharge valve provided in a discharge flow passage communicating with the compression chamber,
A space on the radially inner side of the roller communicates with an oil supply passage of the drive shaft,
At least one of the first bearing and the second bearing has a recess on a surface facing the cylinder chamber,
When the rotation angle of the roller is 0° when the roller is located at the top dead center in the cylinder, the recess is located on the radially inner side of the roller when the rotation angle of the roller is 0°, and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180°,
When the rotation angle of the roller is 180°, the lubricating oil in the recess is directly discharged into the compression chamber ,
a refrigeration cycle device , wherein the recess is entirely blocked by the roller while the rotation angle of the roller is changing from 0° to 180°. The compressor includes a condenser, an expansion valve, and an evaporator.
The compressor includes:
an electric motor having a stator and a rotor;
A drive shaft that rotates integrally with the rotor;
two compression mechanisms for compressing a refrigerant as the drive shaft rotates;
a partition plate that axially separates the two compression mechanism units;
a sealed container that houses at least the electric motor, the drive shaft, the two compression mechanism parts, and the partition plate and in which lubricating oil is sealed,
Each of the compression mechanism units is
An annular cylinder;
an annular roller that revolves within the cylinder as the electric motor is driven;
a bearing for supporting the drive shaft;
a plate-like vane whose tip contacts an outer peripheral surface of the roller and divides a cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber;
a discharge valve provided in a discharge flow passage communicating with the compression chamber,
The bearing is provided on one side of the cylinder in the axial direction,
The partition plate is provided on the other side of the cylinder in the axial direction,
A space on the radially inner side of the roller communicates with an oil supply passage of the drive shaft,
In each of the compression mechanisms, at least one of the bearing and the partition plate is provided with a recess on a surface facing the cylinder chamber,
When the rotation angle of the roller is 0° when the roller is located at the top dead center in the cylinder, the recess is located on the radially inner side of the roller when the rotation angle of the roller is 0°, and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180°,
When the rotation angle of the roller is 180°, the lubricating oil in the recess is directly discharged into the compression chamber ,
a refrigeration cycle device , wherein the recess is entirely blocked by the roller while the rotation angle of the roller is changing from 0° to 180°. The refrigeration cycle device according to claim 8 or 9, wherein refrigerant R32 is used as the refrigerant.

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