JPWO2021079477A1 - Compressor and refrigeration cycle equipment - Google Patents

Abstract

We provide compressors with high performance and reliability. At least one of the upper bearing (5c) and the lower bearing (5d) included in the compressor (100) is provided with an oil pocket (h10) on the surface facing the cylinder chamber. When the rotation angle of the roller (5b) is 0 ° when the roller (5b) is located at the top dead point in the cylinder (5a), the rotation angle of the roller (5b) is 0 °. When the oil pocket (h10) is located radially inside (5b) and the rotation angle of the roller (5b) is 180 °, the oil pocket (h10) is located between the roller (5b) and the cylinder (5a). positioned.

Description

The present invention relates to a compressor or the like.

As a technique for improving the lubricity and sealing property of a rotary compressor, for example, the technique described in Patent Document 1 is known. That is, Patent Document 1 describes three sections: a section in which at least one inner surface of the bearing plate communicates with the cylinder inner space, a section blocked by the end face of the piston, and a section communicating with the inside of the piston due to the rotation of the piston. It describes a rotary compressor in which an oil reservoir recess is provided at a position where the oil is stored.

Japanese Unexamined Patent Publication No. 6-74170

Although Patent Document 1 describes that the above-mentioned oil reservoir recess is provided, the specific arrangement and configuration of the oil reservoir recess are not disclosed. Depending on the position of the oil reservoir recess, the amount of oil supplied to the space inside the cylinder may be too small or excessive, which may lead to deterioration in the performance and reliability of the rotary compressor.

Therefore, it is an object of the present invention to provide a compressor or the like having high performance and reliability.

In order to solve the above-mentioned problems, in the present invention, at least one of the first bearing and the second bearing of the compressor is provided with a recess on the surface facing the cylinder chamber, and the roller is positioned at the top blind point in the cylinder. When the rotation angle of the roller is 0 °, the recess is located inside the roller in the radial direction when the rotation angle of the roller is 0 °, and the rotation angle of the roller is set to 0 °. In the state of 180 °, it was assumed that the recess was located between the roller and the cylinder.

Further, in the present invention, at least one of the bearing and the partition plate of the compressor is provided with a recess on the surface facing the cylinder chamber, and the rotation angle of the roller when the roller is located at the top dead point in the cylinder. When the angle of rotation of the roller is 0 °, the recess is located inside the roller in the radial direction, and when the angle of rotation of the roller is 180 °, the roller and the roller are located. It was decided that the recess was located between the cylinder and the cylinder.

According to the present invention, it is possible to provide a compressor or the like having high performance and reliability.

It is a vertical sectional view of the compressor which concerns on 1st Embodiment of this invention. FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1 in the compressor according to the first embodiment of the present invention. It is a partially enlarged view of the vertical cross section of the compression mechanism part provided in the compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing which shows the arrangement of the oil pocket in the compression mechanism part of the compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing of the process of the roller moving in the cylinder of the compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing of the oil intake section, the blockage section, and the oil discharge section in the oil pocket of the compressor which concerns on 1st Embodiment of this invention. It is a figure which shows the experimental result of APF in the oil pocket volume ratio in the compressor which concerns on 1st Embodiment of this invention. It is a vertical sectional view of the compressor which concerns on 2nd Embodiment of this invention. FIG. 8 is a cross-sectional view taken along the line III-III of FIG. 8 in the compressor according to the second embodiment of the present invention. FIG. 3 is a plan view and a sectional view taken along line IV-IV of a partition plate included in the compressor according to the second embodiment of the present invention. It is a partially enlarged view of the vertical cross section of the oil pocket of the partition plate provided in the compressor which concerns on 2nd Embodiment of this invention. It is a partially enlarged view of the vertical cross section of the oil pocket of the partition plate provided in the compressor which concerns on the modification of 2nd Embodiment of this invention. It is a vertical sectional view of the compressor which concerns on 3rd Embodiment of this invention. It is a block diagram of the air conditioner which concerns on 4th Embodiment of this invention.

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

The closed container 1 is a shell-shaped container that houses the electric motor 2, the crank shaft 4, the compression mechanism portion 5, and the like, and is substantially sealed. The closed container 1 includes a cylindrical tubular chamber 1a, a lid chamber 1b welded to the upper end of the tubular chamber 1a, and a bottom chamber 1c welded to the lower end of the tubular chamber 1a. .. Lubricating oil for improving the lubricity and sealing property of the compressor 100 is sealed in the closed container 1, and is stored as an oil sump U at the bottom of the closed container 1.

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

The electric motor 2 is a drive source for rotating the crank shaft 4, and is installed inside the closed container 1. As shown in FIG. 1, the electric motor 2 includes a stator 2a, a rotor 2b, and a winding 2c. The stator 2a is a cylindrical member formed by laminating electromagnetic steel sheets, and is fixed to the inner peripheral wall of the tubular chamber 1a. The rotor 2b is a cylindrical member formed by laminating electromagnetic steel sheets, and is arranged inside the stator 2a in the radial direction. The crank shaft 4 is fixed to the rotor 2b by press fitting or the like. The winding 2c is a wiring through which a current flows, is wound in a predetermined manner, and is installed in the stator 2a.

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

The spindle 4a is coaxially fixed to the rotor 2b of the motor 2. The eccentric portion 4b is a shaft that rotates while being eccentric with respect to the main shaft 4a, and is integrally formed with the main shaft 4a. The eccentric portion 4b is arranged radially inside the cylinder 5a at the lower part of the crank shaft 4.

Further, a predetermined oil supply passage 4c is provided in the axial direction at the lower portion of the crank shaft 4. The oil supply passage 4c is a flow path that guides the lubricating oil stored as the oil sump U in the closed container 1 to the compression mechanism portion 5 and the like, and is open at the lower end of the crank shaft 4. A thin plate-shaped metal piece (not shown) twisted and bent in a predetermined manner is provided as an oil pump near the upstream end of the oil supply passage 4c (that is, near the lower end of the crank shaft 4). Then, the metal piece is rotated integrally with the crank shaft 4, so that the lubricating oil is pumped up through the oil supply passage 4c.

Further, a plurality of lateral holes h1, h2, h3 communicating with the refueling passage 4c are provided. The sliding surface of the upper bearing 5c is lubricated by the lubricating oil supplied through the lateral hole h1. Further, the sliding surface of the lower bearing 5d is lubricated by the lubricating oil supplied through the lateral hole h2. Further, the lubricating oil is supplied to the inside of the roller 5b in the radial direction through the vertically elongated horizontal hole h3 provided in the eccentric portion 4b. In this way, the space G (see FIG. 3) inside the roller 5b in the radial direction communicates with the oil supply passage 4c of the crank shaft 4.

The compression mechanism unit 5 is a mechanism that compresses the refrigerant as the crank shaft 4 rotates. That is, the compression mechanism unit 5 is a mechanism that compresses the refrigerant sucked through the suction pipe Pi in the compression chamber Com and discharges the compressed refrigerant, and is arranged under the electric motor 2. As shown in FIG. 1, the compression mechanism portion 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 the like. It is equipped with a vane spring of 5 g.

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

The roller 5b is a member that revolves in the cylinder 5a when the electric motor 2 (see FIG. 1) is driven, and has an annular shape (cylindrical shape). Then, the roller 5b revolves inside the cylinder 5a while sliding in contact with 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 described above.

The tip of the vane 5e comes into contact with the outer peripheral surface of the roller 5b (that is, the tip of the vane 5e on the roller 5b side), and the cylinder chamber Cy between the cylinder 5a and the roller 5b is brought into the suction chamber In and the compression chamber Com (FIG. It is a plate-shaped member that divides into 5).

As shown in FIG. 2, an arcuate base end portion 5k is installed substantially integrally with the cylinder 5a in a predetermined range on the outer peripheral surface of the cylinder 5a. The suction pipe Pi is inserted and fixed in the suction passage h4 that radially penetrates the base end portion 5k and the cylinder 5a. Then, the gaseous refrigerant is guided to the cylinder chamber Cy through the suction pipe Pi and the suction passage h4 in sequence.

Further, at a predetermined position of the base end portion 5k, a vane spring mounting hole h5 is provided in the radial direction up to the vicinity of the outer peripheral surface of the cylinder 5a. The vane spring mounting hole h5 is a hole in which the vane spring 5g (see FIG. 1) described later is mounted.
Further, a radial slit (not shown by a reference numeral in FIG. 2) is provided in the cylinder 5a so as to communicate the vane spring mounting hole h5 and the space inside the cylinder 5a in the radial direction. This slit is a space for reciprocating the vane 5e in the radial direction, and is provided slightly wider than the wall thickness of the vane 5e.

FIG. 3 is a partially enlarged view of a vertical cross section of the compression mechanism portion 5 included in the compressor.
The vane spring 5g shown in FIG. 3 is a spring that urges the vane 5e inward in the radial direction, and is installed in the vane spring mounting hole h5. The tip of the vane 5e is pressed against the outer peripheral surface of the roller 5b by the pressure difference between the inside and outside of the compression mechanism portion 5 and the urging force of the vane spring 5g (see also FIG. 2). As a result, the cylinder chamber Cy, which is the space between the cylinder 5a and the roller 5b, is partitioned into the suction chamber In and the compression chamber Com (see also FIG. 5). Further, a discharge notch h6 is provided at a predetermined position on the inner peripheral edge of the upper surface of the cylinder 5a.

The discharge notch h6 is a notch that guides the compressed refrigerant to the discharge valve 5f, and as shown in FIG. 2, the edge thereof has an arc shape. Further, 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. Further, the suction passage h4 is open on the other side of the vane 5e in the circumferential direction.

The upper bearing 5c (first bearing) shown in FIG. 3 is a slide bearing that pivotally supports the crank shaft 4, and is provided on the upper side (one side in the axial direction) of the cylinder 5a. The upper bearing 5c is fastened together with the cylinder 5a and the lower bearing 5d with a plurality of bolts T (see FIG. 2), and is further fixed to the inner peripheral wall of the cylinder chamber 1a (see FIG. 1). In the example of FIG. 3, a predetermined annular groove h7 is provided on the end surface of the upper bearing 5c on the cylinder 5a side in order to alleviate the local 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 path" communicating with the compression chamber Com includes a discharge notch h6 and a discharge port h8.

The discharge valve 5f shown in FIG. 3 is a valve for discharging the compressed refrigerant into the space inside the closed container 1 (see FIG. 1), and is provided in the above-mentioned “discharge flow path”. In the example of FIG. 3, the discharge valve 5f is installed in the upper bearing 5c so as to close the discharge port h8. Then, 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 slide bearing that pivotally supports the crank shaft 4, and is provided on the lower side (the other side in the axial direction) of the cylinder 5a. In the example of FIG. 3, a predetermined annular groove h9 is provided on the end surface of the lower bearing 5d on the cylinder 5a side in order to alleviate the local one-sided contact between the crankshaft 4 and the lower bearing 5d.
Further, 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). The details will be described later, but during the revolution of the roller 5b in the cylinder 5a, the lubricating oil is taken into the oil pocket h10 in the space G inside the radial direction of the roller 5b, and the lubricating oil is further supplied to the cylinder chamber Cy. The cycle of "lubrication" is repeated periodically. The arrangement of the oil pocket h10 and the like is one of the main features of the present embodiment.

The muffling cover 6 (see also FIG. 1) is a cover for suppressing noise caused by compression of the refrigerant, and is fixed to the upper bearing 5c with the upper surface of the upper bearing 5c covered. The sound deadening cover 6 is provided with a plurality of holes (not shown in FIG. 1) for discharging the compressed refrigerant into the space inside the closed container 1.

FIG. 4 is an explanatory diagram showing the arrangement of the oil pocket h10 in the compression mechanism portion 5.
The Y-axis shown in FIG. 4 is perpendicular to the central axis Z (see also FIG. 1), is parallel to the side surface of the vane 5e, and passes through the cylinder 5a, the roller 5b, and the vane 5e. It is an axis. Further, 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 in the vicinity of the vane 5e as a circular hole having a relatively shallow bottom. More specifically, the oil pocket h10 is separated from the vane 5e in the X-axis direction by a distance L1 toward the discharge notch h6 so as not to overlap the vane 5e that reciprocates in the radial direction (so that the oil pocket h10 is not blocked by the vane 5e). An oil pocket h10 is provided at the above position. The above-mentioned distance L1 is preferably, for example, in the range of 0.5 mm to 2.0 mm, but is not limited thereto. By providing the oil pocket h10 in the vicinity of the vane 5e in this way, the lubricating oil discharged from the oil pocket h10 into the cylinder chamber Cy easily adheres to the side surface or the vicinity of the tip of the vane 5e. Therefore, the sliding surfaces of the vane 5e, the cylinder 5a, and the roller 5b can be sufficiently lubricated.

Further, regarding the position of the oil pocket h10 in the Y-axis direction, the oil pocket h10 is provided at a position where the oil intake section Δθ _in (see FIG. 6) and the oil discharge section Δθ _out (see FIG. 6) are substantially equal to each other. There is. The oil intake section Δθ _in described above is the range of the rotation angle of the roller 5b when the lubricating oil is taken into the oil pocket h10. More specifically, the range of the rotation angle of the roller 5b in the state where the oil pocket h10 (recess) is located inside the roller 5b in the radial direction is the oil intake section Δθ _in .

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

Further, 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 sealing surface (annular lower surface) of the roller 5b. As a result, the blockage section Δθ _{occ (see FIG. 6) between the oil intake section Δθ in} and the oil discharge section Δθ _out and the oil pocket h10 are temporarily blocked by the sealing surface of the roller 5b. There is.

FIG. 5 is an explanatory diagram of a process in which the roller 5b moves in the cylinder 5a.
The rotation angle θ shown in FIG. 5 is the rotation angle of the roller 5b that moves (revolves) in the cylinder 5a. Further, the rotation angle of the roller 5b when the roller 5b is located at the "top dead center" (TDC: Top Dead Center) in the cylinder 5a is set to 0 °. The above-mentioned "top dead center" means the position of the roller 5b when the compression of the refrigerant is started in the compression chamber Com. In other words, the "top dead center" is when the center of the roller 5b is closest to the tip of the vane 5e in the direction in which the vane 5e extends in a plan view (Y-axis direction in FIG. 4) (the vane 5e is the closest). It means the position of the roller 5b (when retracted).

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

Further, when the rotation angle of the roller 5b is 90 °, the oil pocket h10 (recess) is closed by the roller 5b. This makes it possible to prevent the radial inner and outer spaces of the roller 5b from communicating with each other via the oil pocket h10. Therefore, even if the oil pocket h10 is provided, there is almost no possibility that the efficiency of compressing the refrigerant by the compression mechanism portion 5 will decrease.

Further, when the rotation angle of the roller 5b is 180 °, the 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. On the other hand, the gaseous refrigerant enters the oil pocket h10 so as to replace the above-mentioned lubricating oil.

The space G inside the roller 5b in the radial direction is sequentially passed through the lateral hole h3 (see FIG. 3) and the oil supply passage 4c (see FIG. 3) in the closed container 1 (however, the outside of the compression mechanism portion 5: It communicates with the space shown in Fig. 1). Therefore, in a state where the oil pocket h10 is closed by the roller 5b at θ = 90 °, the pressure of the lubricating oil in the oil pocket h10 is substantially equal to the pressure of the refrigerant in the closed container 1 (discharge pressure 9). On the other hand, the pressure of the refrigerant in the compression chamber Com at θ = 180 ° is lower than the predetermined discharge pressure because it is in the middle of compression. Therefore, at θ = 180 °, the lubricating oil in the oil pocket h10 is relative. It is diffused into the compression chamber Com, which is a low pressure.

Further, when the rotation angle of the roller 5b is 270 °, the oil pocket h10 (recess) is closed by the roller 5b. This makes it possible to prevent the radial inner and outer spaces of the roller 5b from communicating with each other via the oil pocket h10.

Then, when the rotation angle of the roller 5b returns to the state of 0 ° (that is, the top dead center), the high-pressure lubricating oil existing inside the roller 5b in the radial direction re-enters the oil pocket h10. In this way, the lubricating oil is intermittently supplied to the compression chamber Com.

Further, 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 including the discharge notch h6 (see FIG. 4) and the discharge port h8 (see FIG. 4). As a result, the refrigerant diffused into the compression chamber Com (for example, “θ = 180 °” in FIG. 5) is reduced due to the movement of the roller 5b (for example, “θ = 270 °” in FIG. 5). ”), It is naturally collected near the tip of the vane 5e.

As a result, in addition to the tip of the vane 5e shown in FIG. 4, the lubricating oil easily adheres to the side surface of the vane 5e on the compression chamber Com side. The tip and side surfaces of the vane 5e are particularly prone to sliding friction in the compression mechanism portion 5. Further, the lubricating oil diffused in the compressor Com sufficiently lubricates each sliding surface of the cylinder 5 and the roller 5b in addition to the vane 5e.

Further, due to the pressure difference between the suction chamber In (see FIG. 5) and the compression chamber Com (see FIG. 5), a force that presses the vane 5e on the suction pipe Pi side (that is, the suction passage h4 side: see FIG. 3) acts. do. As a result, the lubricating oil enters the minute gap between the side surface of the vane 5e on the discharge notch h6 side and the wall surface of the cylinder 5a, so that the lubricating oil from the oil pocket h10 causes each of the cylinder 5a and the vane 5e. The sliding surface is sufficiently lubricated.

Incidentally, the rear end portion of the vane 5e on the vane spring 5g side faces the space inside the closed container 1 (see FIG. 1). Therefore, the mist-like lubricating oil in the closed container 1 also adheres to the rear end portion of the vane 5e. As a result, with the reciprocating movement of the vane 5e, the side surface of the vane 5e on the suction chamber In side is also lubricated, and the sliding surfaces of the cylinder 5a and the vane 5e are lubricated.

FIG. 6 is _{an explanatory diagram of an oil intake section Δθ in} , a blockage section Δθ _occ , and an oil discharge section Δθ _out in an oil pocket (see FIG. 5 as appropriate).
As described above, the rotation angle θ shown in FIG. 6 is the rotation angle of the roller 5b that moves (revolves) in the cylinder 5a, and the rotation angle at top dead center is θ = 0 °. Then, as the roller 5b moves, the lubricating oil is taken into the oil pocket h10 (oil uptake section Δθ _in ), the oil pocket h10 is closed (closed section Δθ _occ ), and the lubricating oil is released to the compression chamber Com (oil). The discharge section Δθ _out ) and the blockage of the oil pocket h10 (blockage section Δθ _occ ) are sequentially repeated.

Further, as shown in FIG. 6, _{it is preferable that the oil intake section Δθ in} and the oil release section Δθ _out are substantially equal to each other. More specifically, it is preferable that the oil intake section Δθ _in and the oil release section Δθ _out are 140 ° or more and 165 ° or less, respectively. As a result, the lubricating oil taken into the oil pocket h10 _in the oil intake section Δθ in is discharged to the compression chamber Com without waste in the _{oil discharge section Δθ out.} Therefore, it is possible to increase 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 release section Δθ _out is not particularly limited. For example, the oil intake section Δθ _in = 150 ° may be set, while the oil release section Δθ _out = 160 ° may be set. Further, for example, the oil intake section Δθ _in = 165 ° may be set, while the oil release section Δθ _out = 140 ° may be set.

FIG. 7 is a diagram showing the experimental results of APF at the oil pocket volume ratio (see FIG. 2 as appropriate).
The horizontal axis of FIG. 7 is the oil pocket volume ratio (hereinafter referred to as oil pocket volume ratio Vpr), and the vertical axis is the APF (Annual) of the air conditioner using the compressor 100 (see FIG. 1) of the present embodiment. Performance Factor). 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 above-mentioned “stroke volume” is the volume of the cylinder chamber Cy (see FIG. 2) when the rotation angle θ of the roller is θ = 0 °.

Vpr = Vp / Vth × 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 APF is calculated for each of a plurality of cases where the oil pocket volume ratios are different, and the black circle in FIG. Plotted as points indicated by. According to this experimental result, 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 range, the APF is higher than when the oil pocket h10 is not provided (when the oil pocket volume ratio Vpr = 0).

In particular, when the oil pocket volume ratio Vpr is 0.01%, the increase range of APF based on the case where the oil pocket h10 is not provided (when Vpr = 0) is 0.36%, and the APF is the highest. rice field.

The white circles indicated by reference numerals J are experimental results when an oil pocket (not shown) is provided at the same position as that shown in FIG. 2 of the above-mentioned prior art document. In this case, since the oil pocket is separated from the vane 5e, the vicinity of the vane 5e, which has a large sliding friction, is not sufficiently lubricated, and the APF is lower than when the oil pocket is not provided (oil pocket volume ratio Vpr = 0). There is. On the other hand, according to the first embodiment, as described above, the vicinity of the vane 5e is well lubricated and the sealing property of the compression chamber Com is maintained, so that the APF is significantly higher than before. be able to.

Further, for example, in the case of the stroke volume Vth = 9.5 [ml / rev], when the diameter of the oil pocket h10 is 3 [mm], the depth of the oil pocket h10 is 0.13 [mm]. , Oil pocket volume ratio Vpr is about 0.01%. As described above, by providing the 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.

<Effect>
According to the first embodiment, since the lubricating oil is intermittently supplied from the oil pocket h10 of the lower bearing 5d to the compression chamber Com, the sealing property of the compression chamber Com can be improved. Further, by providing the oil pocket h10 in the vicinity of 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) with respect to the vane 5e, the lubricating oil is likely to adhere to the tip and the side surface of the vane 5e. Therefore, in particular, the lubricity and sealing property of the compression mechanism portion 5 (see FIG. 4) can be improved even during low-speed rotation in which an oil film is difficult to form. Further, even when the refrigerant R32, which tends to have high temperature and high pressure, is used, the compressor 100 having high performance and reliability can be provided.

Further, by making the oil intake section Δθ _in and the oil release section Δθ _out substantially equal (see FIG. 6), almost all of the lubricating oil that has entered the oil pocket h10 is discharged to the compression chamber Com. As a result, even if the volume of the oil pocket h10 is relatively small, the lubricity and sealing property of the compression mechanism portion 5 can be sufficiently ensured. If the volume of the oil pocket h10 is too large, the amount of the refrigerant entering the oil pocket h10 (the amount of the relatively low-pressure refrigerant in the middle of compression) increases in _{the oil discharge section Δθ out, and this refrigerant is substantially reduced to the discharge pressure.} It is discharged into the same closed container 1. Therefore, it is desirable that the volume of the oil pocket h10 is small in consideration of high efficiency in the compression of the refrigerant.

<< Second Embodiment >>
The second embodiment is different from the first embodiment (see FIG. 1) in that the compressor 100A (see FIG. 8) includes two compression mechanism units 51 and 52 (see FIG. 8). The second embodiment is different from the first embodiment in that the partition plates 50 (see FIG. 8) that partition the compression mechanism portions 51 and 52 are provided with oil pockets h11 and h12 (see FIG. 8). ing. The other points are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.

FIG. 8 is a vertical sectional view of the compressor 100A according to the second embodiment.
As shown in FIG. 8, the compressor 100A includes a closed container 1, an electric motor 2, a crank shaft 4A (drive shaft), two compression mechanism portions 51 and 52, a partition plate 50, and muffling covers 61 and 62. And have.

In addition to the electric motor 2 and the crank shaft 4A, the closed container 1 contains two compression mechanism portions 51 and 52, a partition plate 50, and the like, and is also filled with lubricating oil.
The crank shaft 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 a plan view with respect to the other eccentric portion 42b. As a result, the rotational imbalance caused by the movement of one eccentric portion 41b is canceled by the other eccentric portion 42b, and the vibration of the compressor 100A is suppressed. The inner peripheral surface of the upper roller 51b is in sliding contact with one of the eccentric portions 41b, and the inner peripheral surface of the lower roller 52b is in sliding contact with the other eccentric portion 42b.

The two compression mechanism units 51 and 52 shown in FIG. 8 are mechanisms for compressing the refrigerant with the rotation of the crank shaft 4, respectively. These compression mechanism portions 51 and 52 are fastened with a plurality of bolts T (see FIG. 9) together with the partition plate 50 described later. The upper compression mechanism portion 51 compresses the gaseous refrigerant guided through the suction pipe P1i. The refrigerant compressed by the compression mechanism portion 51 in this way is sequentially discharged into the space inside the closed container 1 through the holes (not shown) of the discharge valve 51f and the sound deadening cover 61.

On the other hand, the lower compression mechanism portion 52 compresses the gaseous refrigerant guided through the suction pipe P2i. The refrigerant compressed by the compression mechanism portion 52 in this way is sequentially discharged into the space inside the closed container 1 through the holes (not shown) of the discharge valve 52f and the sound deadening cover 62. The muffling 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 portion 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. Since each configuration of the compression mechanism unit 51 is the same as that of the compression mechanism unit 5 (see FIG. 1) of the first embodiment, the description thereof will be omitted.

The lower compression mechanism portion 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. Since each configuration of the compression mechanism unit 52 is the same as that of the compression mechanism unit 5 (see FIG. 1) of the first embodiment, the description thereof will be omitted.

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

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

FIG. 9 is a cross-sectional view taken along the line III-III of FIG.
As shown in FIG. 9, the oil pocket h12 (recess) is provided on the discharge notch h26 side (discharge flow path side) with respect to the vane 52e in the circumferential direction. As a result, the lubricating oil is distributed to the sliding surfaces of the vane 52e, the cylinder 52a, and the roller 52b. Similarly, the other oil pocket h11 (recessed portion: see FIG. 8) is also provided on the discharge notch side (discharge flow path side: reference numeral not shown) with respect to the vane 51e (see FIG. 8) in the circumferential direction.

Although not shown, when the rotation angle of the roller 52b is 0 ° when the roller 52b is located at the top dead point in the cylinder 52a, the roller 52b is in a state where the rotation angle of the roller 52b is 0 °. The oil pocket h12 (recess) is located on the inner side in the radial direction of the oil pocket h12.
Further, when the rotation angle of the roller 52b is 180 °, the oil pocket h12 (recess) is located between the roller 52b and the cylinder 52a. As a result, the sliding surfaces of the vane 52e, the cylinder 52a, and the roller 52b can be appropriately lubricated.
Further, when the rotation angle of the roller 52b is 90 ° and the rotation angle of the roller 52b is 270 °, the oil pocket h12 (recess) is closed by the roller 52b. This makes it possible to prevent the radial inner and outer spaces of the roller 52b from communicating with each other via the oil pocket h12.
The same can be said for the rotation angle of the roller 51b in the upper compression mechanism portion 51 (see FIG. 8).

Further, the range of the rotation angle of the roller 52b in the state where the oil pocket h12 (recess) is located inside the roller 52b in the radial direction, and the oil pocket h12 is located between the roller 52b and the cylinder 52a. It is preferable that the range of the rotation angle of the roller 52b in the state is 140 ° or more and 165 ° or less, respectively. As a result, almost all of the lubricating oil that has entered the oil pocket h12 is discharged to the compression chamber Com, so that the lubricity and sealing properties of the compression mechanism portion 52 can be sufficiently ensured. The same can be said for the upper compression mechanism portion 51 (see FIG. 8).

FIG. 10 is a plan view and a sectional view taken along line IV-IV of the partition plate 50.
As shown in FIG. 10, the partition plate 50 is provided with a hole h15 for passing the crank shaft 4A (see FIG. 8). In addition, the partition plate 50 is provided with three holes h14 for muffling, four holes h16 for passing the bolt T (see FIG. 9), and the like.

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

The oil pockets h11 and h12 described above may be formed in the sintering step of the partition plate 50 using a predetermined metal material. In addition, oil pockets h11 and h12 may be formed by cutting using an end mill (not shown). This makes it possible to reduce the processing cost when forming the oil pockets h11 and h12.

FIG. 11A is a partially enlarged view of a vertical cross section of the oil pocket h11 of the partition plate 50.
In the example shown in FIG. 11A, the diameter of the oil pocket h11 (see also FIG. 10) having a circular shape in a plan view is the length L2, and the depth from the upper surface of the partition plate 50 to the bottom surface of the oil pocket h11 is long. It is L3. When designing such an oil pocket h11, 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. It is preferable to have. As a result, the APF of the air conditioner equipped with the compressor 100A (see FIG. 8) can be increased as compared with the case where the oil pocket h11 is not provided. The same can be said for the other oil pocket h12 (see FIG. 10) of the partition plate 50.

FIG. 11B is a partially enlarged view of a vertical cross section of the oil pocket h11s of the partition plate 50B according to the modified example of the second embodiment.
As shown in FIG. 11B, for example, cutting may be performed using a drill (not shown) so that the oil pocket h11s has a predetermined volume. That is, oil pockets h12s whose surface has a V-shape in cross-sectional view may be provided so that the diameter is L4 in length and L5 in depth. Even with such a configuration, the same effect as in the case of FIG. 11A is obtained.

<< Third Embodiment >>
In the third embodiment, the compressor 100C (see FIG. 12) is provided with a predetermined recess h17 in the vane 5Ce in addition to the oil pocket h10 provided in the lower bearing 5d. Is different. The other configurations are the same as those of the first embodiment (see FIG. 1). Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.

FIG. 12 is a vertical sectional view of the compressor 100C according to the third embodiment.
As shown in FIG. 12, the compression mechanism portion 5C includes a vane 5Ce provided with a recessed portion h17 on the side surface thereof. The recessed portion h17 takes in the lubricating oil when the vane 5Ce retracts, and supplies the lubricating oil to the compression chamber Com (or the cylinder chamber including the compression chamber Com) when the vane 5Ce advances to the central axis Z side. It is a depression for.

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 outer side of the cylinder 5a, and when the rotation angle of the roller 5b is 180 °, the roller 5b and the cylinder 5a At least a part of the recessed portion h17 is present between the two. As a result, the lubricating oil is intermittently supplied to the compression chamber Com and the like. Therefore, coupled with the supply of the lubricating oil through the oil pocket h10, the lubricating oil can be sufficiently supplied to each sliding surface of the cylinder 5a and the vane 5Ce. The recessed portion h17 may be provided only on one side surface of the vane 5Ce having a thin plate shape, or may be provided on both side surfaces.

<Effect>
According to the third embodiment, by providing the recessed portion h17 on the side surface of the vane 5Ce, the lubricating oil can be sufficiently supplied to each sliding surface of the cylinder 5a and the vane 5Ce.

<< Fourth Embodiment >>
In the fourth embodiment, the configuration of the air conditioner W (see FIG. 13) including the compressor 100 (see FIG. 1) described in the first embodiment will be described. Since the configuration of the compressor 100 is the same as that described in the first embodiment (see FIG. 1), the description thereof will be omitted.

FIG. 13 is a configuration diagram of the air conditioner W according to the fourth embodiment.
The solid line arrow in FIG. 13 indicates the flow of the refrigerant during the heating operation.
Further, the broken line arrow in FIG. 13 indicates the flow of the refrigerant during the 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. I have.

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

The evaporator E2 is a heat exchanger in which heat exchange is performed between the refrigerant passing through the heat transfer tube (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 in the vicinity of the evaporator E2.

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

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

<Effect>
According to the fourth embodiment, since sufficient lubricating oil is supplied to the compression chamber Com (see FIG. 1) of the compression mechanism unit 5 (see FIG. 1) included in the compressor 100, the sealing property of the compression chamber Com is good. In addition, the lubricity 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 the air conditioner W having high performance and reliability.

≪Variation example≫
Although the compressor 100 and the like according to the present invention have been described above 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), the configuration in which the oil pocket h10 is provided on the upper surface of the lower bearing 5d has been described, but the present invention is not limited to this. 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 at least one of the upper bearing 5c (first bearing) and the lower bearing 5d (second bearing) on the surface facing the cylinder chamber Cy. ..

Further, in the second embodiment (see FIG. 8), the configuration in which the oil pockets h11 and h12 are provided on the partition plate 50 has been described, but the present invention is not limited to this. That is, in the compression mechanism portion 51, oil pockets (recesses) may be provided on the surface facing the cylinder chamber on at least one of the upper bearing 5c (bearing) and the partition plate 50. Further, in the compression mechanism portion 52, oil pockets (recesses) may be provided on the surface facing the cylinder chamber on at least one of the lower bearing 5d (bearing) and the partition plate 50.

Further, in the second embodiment (see FIG. 8), the configuration in which the compressor 100A includes two compression mechanism units 51 and 52 has been described, but the present invention is not limited to this. That is, the compressor may be configured to include three or more compression mechanism units (not shown). In such a configuration, the uppermost compression mechanism portion (not shown) is provided with an oil pocket on the surface of the upper bearing and the partition plate facing at least one cylinder chamber, and the lowermost compression mechanism portion (not shown). (Not shown) is provided with an oil pocket on the surface of the lower bearing and the partition plate facing at least one of the cylinder chambers. Further, the remaining compression mechanism portions (not shown) other than the uppermost stage and the lowermost stage are provided with oil pockets on the surface facing the cylinder chamber of at least one of the pair of partition plates sandwiching the rotor and the cylinder. Even with such a configuration, the same effect as that of each embodiment is obtained. It should be noted that oil pockets may be provided in at least one of the plurality of compression mechanism portions described above, and no oil pockets may be provided in the rest.

In addition, each embodiment can be appropriately combined. For example, the second embodiment and the fourth embodiment may be combined. That is, the air conditioner W (see FIG. 13) may be configured so as to include the compressor 100A provided with the oil pockets h11 and h12 on the partition plate 50 (see FIG. 8).
Further, the oil pocket h10 of the lower bearing 5d may be omitted from the compressor 100C (see FIG. 12) of the third embodiment, and the recessed portion h17 of the vane 5e may be left. Even with such a configuration, the sealing property and lubricity of the compression mechanism portion 5C are kept good.

Further, in each embodiment, the case where the compressor 100 is installed vertically has been described, but the present invention is not limited to this. That is, each embodiment can be applied even when the compressor 100 is arranged horizontally or diagonally.
Further, 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, package air conditioners, and multi air conditioners for buildings.

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

Further, each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the configurations described. Further, it is possible to add / delete / replace a part of the configuration of each embodiment with another configuration.
In addition, the above-mentioned mechanism and configuration show what is considered necessary for explanation, and do not necessarily show all the mechanisms and configurations in the product.

100, 100A, 100C Compressor 1 Sealed container 2 Motor 2a Stator 2b Rotor 4,4A Crank shaft (drive shaft)
4c Refueling path 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 dent
In suction chamber Q Refrigerant circuit V Expansion valve W Air conditioner (refrigerant cycle device)
Z center axis

In order to solve the above-mentioned problems, in the present invention, at least one of the first bearing and the second bearing of the compressor is provided with a recess on the surface facing the cylinder chamber, and the roller is positioned at the top dead point in the cylinder. When the rotation angle of the roller is 0 °, the recess is located inside the roller in the radial direction when the rotation angle of the roller is 0 °, and the rotation angle of the roller is set to 0 °. In the 180 ° state, the recess is located between the roller and the cylinder, the recess is provided on the discharge flow path side of the vane in the circumferential direction, and the central axis of the drive shaft is the Z axis. When the straight line perpendicular to the Z-axis and parallel to the side surface of the vane is the Y-axis and the straight line perpendicular to both the Y-axis and the Z-axis is the X-axis, the direction of the X-axis. In the above, it is determined that the recess is provided at a position separated from the vane on the discharge flow path side by a predetermined distance .

Further, in the present invention, at least one of the bearing and the partition plate of the compressor is provided with a recess on the surface facing the cylinder chamber, and the rotation angle of the roller when the roller is located at the top dead point in the cylinder. Is 0 °, the recess is located inside the roller in the radial direction when the rotation angle of the roller is 0 °, and the roller and the roller are in a state where the rotation angle of the roller is 180 °. The recess is located between the cylinder and the recess, the recess is provided on the discharge flow path side of the vane in the circumferential direction, the central axis of the drive shaft is the Z axis, and the recess is perpendicular to the Z axis. When the straight line parallel to the side surface of the vane is the Y axis and the straight line perpendicular to both the Y axis and the Z axis is the X axis, from the vane to the discharge flow path side in the direction of the X axis. It was decided that the recess was provided at a position separated by a predetermined distance.

In order to solve the above-mentioned problems, in the present invention, at least one of the first bearing and the second bearing of the compressor is provided with a recess on the surface facing the cylinder chamber, and the roller is positioned at the top dead point in the cylinder. When the rotation angle of the roller is 0 °, the recess is located inside the roller in the radial direction when the rotation angle of the roller is 0 °, and the rotation angle of the roller is set to 0 °. In the 180 ° state, the recess is located between the roller and the cylinder, the recess is provided on the discharge flow path side of the vane in the circumferential direction, and the central axis of the drive shaft is the Z axis. When the straight line perpendicular to the Z-axis and parallel to the side surface of the vane is the Y-axis and the straight line perpendicular to both the Y-axis and the Z-axis is the X-axis, the direction of the X-axis. The recess is provided at a position separated from the vane on the discharge flow path side by a predetermined distance, and the space inside the roller in the radial direction and the space between the roller and the cylinder are directly connected to each other. I decided not to communicate.

Further, in the present invention, at least one of the bearing and the partition plate of the compressor is provided with a recess on the surface facing the cylinder chamber, and the rotation angle of the roller when the roller is located at the top dead point in the cylinder. When is 0 °, the recess is located inside the roller in the radial direction when the rotation angle of the roller is 0 °, and the roller and the roller are in a state where the rotation angle of the roller is 180 °. The recess is located between the cylinder and the recess, the recess is provided on the discharge flow path side of the vane in the circumferential direction, the central axis of the drive shaft is the Z axis, and the recess is perpendicular to the Z axis. When the straight line parallel to the side surface of the vane is the Y axis and the straight line perpendicular to both the Y axis and the Z axis is the X axis, in the direction of the X axis, from the vane to the discharge flow path side. The recess is provided at a position separated by a predetermined distance, and the space inside the roller in the radial direction and the space between the roller and the cylinder are not directly communicated with each other.

Claims (10)

Motors with stators and rotors,
A drive shaft that rotates integrally with the rotor,
A compression mechanism that compresses the refrigerant as the drive shaft rotates,
A closed container that houses at least the motor, the drive shaft, and the compression mechanism and is filled with lubricating oil.
The compression mechanism unit
An annular cylinder and
An annular roller that revolves in the cylinder as the motor is driven,
A first bearing provided on one side of the cylinder in the axial direction and supporting the drive shaft,
It has a second bearing provided on the other side in the axial direction of the cylinder and supporting the drive shaft, and also has.
A plate-shaped vane whose tip comes into contact with the outer peripheral surface of the roller and partitions the cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber.
It has a discharge valve provided in a discharge flow path communicating with the compression chamber, and has.
The space inside the roller in the radial direction communicates with the oil supply passage of the drive shaft.
At least one of the first bearing and the second bearing is provided with a recess on the surface facing the cylinder chamber.
When the rotation angle of the roller is 0 ° when the roller is located at the top dead point in the cylinder, when the rotation angle of the roller is 0 °, the roller is radially inside the roller. A compressor in which the recess is located and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180 °. Motors with stators and rotors,
A drive shaft that rotates integrally with the rotor,
Two compression mechanism units that compress the refrigerant as the drive shaft rotates,
A partition plate that partitions the two compression mechanisms in the axial direction,
It comprises the motor, the drive shaft, the two compression mechanisms, and a closed container that houses at least the partition plate and is filled with lubricating oil.
Each of the compression mechanism units
An annular cylinder and
An annular roller that revolves in the cylinder as the motor is driven,
It has a bearing that supports the drive shaft, and
A plate-shaped vane whose tip comes into contact with the outer peripheral surface of the roller and partitions the cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber.
It has a discharge valve provided in a discharge flow path communicating with the compression chamber, and has.
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.
The space inside the roller in the radial direction communicates with the oil supply passage of the drive shaft.
In each of the compression mechanism portions, at least one of the bearing and the partition plate is provided with a recess on the surface facing the cylinder chamber.
When the rotation angle of the roller is 0 ° when the roller is located at the top dead point in the cylinder, when the rotation angle of the roller is 0 °, the roller is radially inside the roller. A compressor in which the recess is located and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180 °. According to claim 1 or 2, the recess is closed by the roller when the rotation angle of the roller is 90 ° and the rotation angle of the roller is 270 °. The compressor described. The range of the angle of rotation of the roller when the recess is located radially inside the roller, and the roller of the roller when the recess is located between the roller and the cylinder. The compressor according to claim 1 or 2, wherein the range of the angle of rotation is 140 ° or more and 165 ° or less, respectively. The compressor according to claim 1 or 2, wherein the recess is provided on the discharge flow path side of the vane in the circumferential direction. The ratio of the volume of the recess to the stroke volume, which is the volume of the cylinder chamber when the rotation angle of the roller is 0 °, is 0.001% or more and 0.019% or less. The compressor according to claim 1 or claim 2, wherein the compressor is characterized by the above. A recess is provided on the side surface of the vane.
When the rotation angle of the roller is 0 °, at least a part of the recess is present on the radial outer side of the cylinder, and when the rotation angle of the roller is 180 °, the roller and the cylinder The compressor according to claim 1 or 2, wherein at least a part of the recess is present between the two. Includes a refrigerant circuit in which the refrigerant circulates sequentially through the compressor, condenser, expansion valve, and evaporator.
The compressor
Motors with stators and rotors,
A drive shaft that rotates integrally with the rotor,
A compression mechanism that compresses the refrigerant as the drive shaft rotates,
A closed container that houses at least the motor, the drive shaft, and the compression mechanism and is filled with lubricating oil.
The compression mechanism unit
An annular cylinder and
An annular roller that revolves in the cylinder as the motor is driven,
A first bearing provided on one side of the cylinder in the axial direction and supporting the drive shaft,
It has a second bearing provided on the other side in the axial direction of the cylinder and supporting the drive shaft, and also has.
A plate-shaped vane whose tip comes into contact with the outer peripheral surface of the roller and partitions the cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber.
It has a discharge valve provided in a discharge flow path communicating with the compression chamber, and has.
The space inside the roller in the radial direction communicates with the oil supply passage of the drive shaft.
At least one of the first bearing and the second bearing is provided with a recess on the surface facing the cylinder chamber.
When the rotation angle of the roller is 0 ° when the roller is located at the top dead point in the cylinder, when the rotation angle of the roller is 0 °, the roller is radially inside the roller. A refrigeration cycle device in which the recess is located and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180 °. Includes a refrigerant circuit in which the refrigerant circulates sequentially through the compressor, condenser, expansion valve, and evaporator.
The compressor
Motors with stators and rotors,
A drive shaft that rotates integrally with the rotor,
Two compression mechanism units that compress the refrigerant as the drive shaft rotates,
A partition plate that partitions the two compression mechanisms in the axial direction,
It comprises the motor, the drive shaft, the two compression mechanisms, and a closed container that houses at least the partition plate and is filled with lubricating oil.
Each of the compression mechanism units
An annular cylinder and
An annular roller that revolves in the cylinder as the motor is driven,
It has a bearing that supports the drive shaft, and
A plate-shaped vane whose tip comes into contact with the outer peripheral surface of the roller and partitions the cylinder chamber between the cylinder and the roller into a suction chamber and a compression chamber.
It has a discharge valve provided in a discharge flow path communicating with the compression chamber, and has.
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.
The space inside the roller in the radial direction communicates with the oil supply passage of the drive shaft.
In each of the compression mechanism portions, at least one of the bearing and the partition plate is provided with a recess on the surface facing the cylinder chamber.
When the rotation angle of the roller is 0 ° when the roller is located at the top dead point in the cylinder, when the rotation angle of the roller is 0 °, the roller is radially inside the roller. A refrigeration cycle device in which the recess is located and the recess is located between the roller and the cylinder when the rotation angle of the roller is 180 °. The refrigerating cycle apparatus according to claim 8 or 9, wherein the refrigerant R32 is used as the refrigerant.

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