CN114555948B - Compressor and refrigeration cycle device - Google Patents
Compressor and refrigeration cycle device Download PDFInfo
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- CN114555948B CN114555948B CN201980101163.XA CN201980101163A CN114555948B CN 114555948 B CN114555948 B CN 114555948B CN 201980101163 A CN201980101163 A CN 201980101163A CN 114555948 B CN114555948 B CN 114555948B
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- roller
- cylinder
- axis
- drive shaft
- vane
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Abstract
The invention provides a compressor with high performance and reliability. An oil groove (h 10) is provided on the surface facing the cylinder chamber of at least one of an upper bearing (5 c) and a lower bearing (5 d) provided in the compressor (100). When the rotation angle of the roller (5 b) when the roller (5 b) in the cylinder (5 a) is positioned at the top dead center is set to 0 DEG, the oil groove (h 10) is positioned radially inside the roller (5 b) when the rotation angle of the roller (5 b) is 0 DEG, and the oil groove (h 10) is positioned between the roller (5 b) and the cylinder (5 a) when the rotation angle of the roller (5 b) is 180 deg.
Description
Technical Field
The present invention relates to a compressor and the like.
Background
As a technique for improving the lubricity and the sealing property of the rotary compressor, for example, a technique described in patent document 1 is known. That is, patent document 1 describes a rotary compressor in which an oil reservoir is provided in at least one inner surface of a bearing plate at three positions, namely, a section communicating with a cylinder space, a section closed by an end surface of a piston, and a section communicating with the inside of the piston, by rotation of the piston.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 6-74170
Disclosure of Invention
Problems to be solved by the invention
Accordingly, an object of the present invention is to provide a compressor and the like having high performance and reliability.
Means for solving the problems
In order to solve the above problem, according to the compressor of the present invention, a concave portion is provided on a surface of at least one of a first bearing and a second bearing facing a cylinder chamber, and when a rotation angle of the roller when the roller is positioned at a top dead center in a cylinder is 0 °, the concave portion is positioned radially inward of the roller when the rotation angle of the roller is 0 °, and the concave portion is positioned between the roller and the cylinder when the rotation angle of the roller is 180 °.
In the present invention, a concave portion is provided on a surface of at least one of a bearing and a partition plate of a compressor facing a cylinder chamber, and when a rotation angle of the roller when the roller is positioned at a top dead center in a cylinder is 0 °, the concave portion is positioned radially inward of the roller when the rotation angle of the roller is 0 °, and the concave portion is positioned between the roller and the cylinder when the rotation angle of the roller is 180 °.
Effects of the invention
According to the present invention, a compressor and the like having high performance and reliability can be provided.
Drawings
Fig. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention.
Fig. 2 is a sectional view of the line II-II of fig. 1 in the compressor according to the first embodiment of the present invention.
Fig. 3 is a partially enlarged vertical cross-sectional view of a compression mechanism section provided in a compressor according to a first embodiment of the present invention.
Fig. 4 is an explanatory diagram showing the arrangement of the oil groove in the compression mechanism of the compressor according to the first embodiment of the present invention.
Fig. 5 is an explanatory diagram of a process in which the roller moves in the cylinder of the compressor according to the first embodiment of the present invention.
Fig. 6 is an explanatory diagram of an oil suction section, a closed section, and an oil discharge section in an oil sump of the compressor according to the first embodiment of the present invention.
Fig. 7 is a graph showing the result of an APF experiment of the oil groove volume ratio in the compressor according to the first embodiment of the present invention.
Fig. 8 is a longitudinal sectional view of a compressor according to a second embodiment of the present invention.
Fig. 9 is a sectional view of the line III-III of fig. 8 in the compressor according to the second embodiment of the present invention.
Fig. 10 is a plan view and a sectional view along line IV-IV of a partition plate provided in a compressor according to a second embodiment of the present invention.
Fig. 11A is a partially enlarged vertical cross-sectional view of an oil groove of a partition plate provided in a compressor according to a second embodiment of the present invention.
Fig. 11B is a partially enlarged vertical cross-sectional view of an oil groove of a partition plate provided in a compressor according to a modification of the second embodiment of the present invention.
Fig. 12 is a longitudinal sectional view of a compressor according to a third embodiment of the present invention.
Fig. 13 is a configuration diagram of an air conditioner according to a fourth embodiment of the present invention.
Detailed Description
First embodiment
< Structure of compressor >
Fig. 1 is a longitudinal sectional view of a compressor 100 according to a first embodiment.
The compressor 100 is a rotary compressor that compresses a gaseous refrigerant. As shown in fig. 1, the compressor 100 includes a hermetic container 1, a motor 2, counterweights 31 and 32, a crankshaft 4 (drive shaft), a compression mechanism 5, and a muffler cover 6.
The sealed container 1 is a shell-shaped container that houses the motor 2, the crankshaft 4, the compression mechanism 5, and the like, and is substantially sealed. The closed casing 1 includes a cylindrical tubular chamber 1a, a lid chamber 1b welded to an upper end portion of the tubular chamber 1a, and a bottom chamber 1c welded to a lower end portion of the tubular chamber 1 a. Lubricating oil for improving the lubricity and sealing property of the compressor 100 is enclosed in the closed casing 1 and stored as oil U at the bottom of the closed casing 1.
As shown in fig. 1, a suction pipe Pi is inserted into and fixed to a cylindrical cavity 1a of a closed casing 1. The suction pipe Pi is a pipe for guiding the refrigerant to a cylinder chamber Cy (see fig. 2) of the compression mechanism 5. In addition, a discharge pipe Po is inserted into and fixed to the lid cavity 1b of the closed casing 1. The discharge pipe Po is a pipe for guiding the refrigerant compressed by the compression mechanism 5 to the outside of the compressor 100.
The motor 2 is a driving source for rotating the crankshaft 4, and is provided inside the sealed container 1. As shown in fig. 1, the 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 plates, and is fixed to the inner circumferential wall of the cylindrical cavity 1 a. The rotor 2b is a cylindrical member formed by laminating electromagnetic steel plates, and is disposed radially inward of the stator 2a. The crankshaft 4 is fixed to the rotor 2b by press fitting or the like. The winding 2c is a wiring through which a current flows, and is provided in the stator 2a by winding in a predetermined manner.
The crankshaft 4 is a shaft that rotates integrally with the rotor 2b in accordance with driving of the motor 2. 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 coaxially fixed to the rotor 2b of the motor 2. The eccentric portion 4b is a shaft that rotates eccentrically with respect to the main shaft 4a, and is formed integrally with the main shaft 4 a. The eccentric portion 4b is disposed radially inward of the cylinder 5a at a lower portion of the crankshaft 4.
Further, a predetermined oil supply passage 4c is provided in the lower portion of the crankshaft 4 in the axial direction. The oil supply passage 4c is a flow passage for guiding the lubricating oil stored in the sealed container 1 as the oil reservoir U to the compression mechanism portion 5 and the like, and is open at the lower end of the crankshaft 4. In the vicinity of the upstream end of the oil supply passage 4c (i.e., in the vicinity of the lower end of the crankshaft 4), a thin plate-shaped metal piece (not shown) that is twisted and bent in a predetermined manner is provided as an oil pump. Then, the metal piece rotates integrally with the crankshaft 4, so that the lubricating oil is sucked up through the oil supply passage 4c.
Further, a plurality of lateral holes h1, h2, and h3 communicating with the oil supply passage 4c are provided. The sliding surface of the upper bearing 5c is lubricated by the lubricating oil supplied through the lateral hole h 1. The sliding surface of the lower bearing 5d is lubricated by the lubricating oil supplied through the lateral hole h 2. Further, the lubricating oil is supplied to the radially inner side of the roller 5b via a longitudinally elongated lateral hole h3 provided in the eccentric portion 4b. Thus, the space G (see fig. 3) radially inside the roller 5b communicates with the oil supply passage 4c of the crankshaft 4.
The compression mechanism 5 compresses the refrigerant as the crankshaft 4 rotates. That is, the compression mechanism 5 is a mechanism for compressing the refrigerant sucked through the suction pipe Pi in the compression chamber Com and discharging the compressed refrigerant, and is disposed below the 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 sectional view taken along line II-II of fig. 1.
The cylinder 5a shown in fig. 2 is a member that forms a cylinder chamber Cy together with the roller 5b, the upper bearing 5c, and the lower bearing 5d, and is annular (cylindrical). The cylinder chamber Cy is a space between the cylinder 5a and the roller 5 b. The cylinder chamber Cy includes a compression chamber Com and a suction chamber In (see also fig. 5), and In fig. 2, the tip of the vane 5e is retracted by the roller 5b to the inner circumferential surface of the cylinder 5a, and the entire cylinder chamber Cy becomes the compression chamber Com.
The roller 5b is a member that revolves inside the cylinder 5a in accordance with the driving of the motor 2 (see fig. 1), and is annular (cylindrical). The roller 5b is in sliding contact with the inner circumferential surface of the cylinder 5a, and revolves inside the cylinder 5 a. 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-like member having a tip (i.e., a tip of the vane 5e on the roller 5b side) contacting the outer peripheral surface of the roller 5b and dividing a cylinder chamber Cy between the cylinder 5a and the roller 5b into a suction chamber In and a compression chamber Com (see also fig. 5).
As shown in fig. 2, an arc-shaped base end portion 5k is provided substantially integrally with the cylinder 5a within a predetermined range of the outer peripheral surface of the cylinder 5 a. The suction pipe Pi is inserted into and fixed to a suction passage h4 that radially penetrates the base end portion 5k and the cylinder 5 a. Then, the gaseous refrigerant is introduced into the cylinder chamber Cy through the suction pipe Pi and the suction passage h4 in this order.
Further, at a predetermined portion of the base end portion 5k, a leaf spring attachment hole h5 is provided to the vicinity of the outer peripheral surface of the cylinder 5a in the radial direction. The leaf spring attachment hole h5 is a hole to which a leaf spring 5g (see fig. 1) described later is attached.
Further, a radial slit (reference numeral not shown in fig. 2) is provided in the cylinder 5a so that the leaf spring attachment hole h5 communicates with a space inside the cylinder 5a in the radial direction. The slit is a space for reciprocating the blade 5e in the radial direction, and is provided slightly wider than the wall thickness of the blade 5e.
Fig. 3 is a partially enlarged vertical cross-sectional view of the compression mechanism 5 included in the compressor.
The leaf spring 5g shown in fig. 3 is a spring that biases the leaf 5e radially inward, and is provided in the leaf spring attachment hole h 5. The tip of the blade 5e is pressed against the outer peripheral surface of the roller 5b by the difference in pressure between the inside and the outside of the compression mechanism 5 and the urging force of the blade spring 5g (see also fig. 2). Thereby, a cylinder chamber Cy which is a space between the cylinder 5a and the roller 5b is partitioned into a suction chamber In and a compression chamber Com (see also fig. 5). Further, a discharge slit h6 is provided at a predetermined portion of the inner peripheral edge portion of the upper surface of the cylinder 5 a.
The discharge slit h6 is a slit for guiding the compressed refrigerant to the discharge valve 5f, and has an arc-shaped edge as shown in fig. 2. Further, the discharge slit h6 and the opening of the suction passage h4 are both close to the vane 5e in the circumferential direction. Specifically, the discharge slit h6 is provided on one side of the vane 5e in the circumferential direction. Further, the suction passage h4 opens to 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 pivotally supports the crankshaft 4, and is provided on the upper side (one side in the axial direction) of the cylinder block 5 a. The upper bearing 5c is fastened together with the cylinder 5a and the lower bearing 5d by 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 in the end surface of the upper bearing 5c on the cylinder block 5a side in order to alleviate partial one-side 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 slit h6 of the cylinder 5 a. The "discharge flow path" communicating with the compression chamber Com is configured to include a discharge slit 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 in the closed casing 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 provided 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 plate spring, the discharge valve 5f opens.
The lower bearing 5d (second bearing) is a sliding bearing that pivotally supports the crankshaft 4, and is provided below (on the other side in the axial direction) the cylinder 5 a. In the example of fig. 3, a predetermined annular groove h9 is provided in the end surface of the lower bearing 5d on the cylinder block 5a side in order to alleviate partial one-side contact between the crankshaft 4 and the lower bearing 5d.
In the lower bearing 5d, a concave oil groove h10 (concave portion) is provided on a surface facing the cylinder chamber Cy (see also fig. 5). As will be described in detail later, while the roller 5b in the cylinder 5a revolves, the circulation of the lubricating oil being sucked into the oil groove h10 in the space G radially inside the roller 5b and further supplied to the cylinder chamber Cy is periodically repeated. The arrangement of the oil groove h10 and the like are one of the main features of the present embodiment.
The noise reduction cover 6 (see also fig. 1) is a cover for suppressing noise associated with compression of the refrigerant, and is fixed to the upper bearing 5c in a state of covering the upper surface of the upper bearing 5c. Further, the sound deadening cap 6 is provided with a plurality of holes (not shown in fig. 1) for releasing the compressed refrigerant into the space inside the closed casing 1.
Fig. 4 is an explanatory diagram illustrating the arrangement of the oil groove h10 in the compression mechanism section 5.
The Y axis shown in fig. 4 is perpendicular to the central axis Z (see also fig. 1), and is parallel to the side surface of the blade 5e, and passes through a predetermined axis of the blade 5e in addition to the cylinder 5a and the roller 5 b. An axis perpendicular to both the central axis Z and the Y axis is defined as an X axis.
In the example of fig. 4, the oil groove h10 is provided as a hole having a relatively shallow circular bottom in the vicinity of the vane 5e. To explain in more detail, the oil groove h10 is provided at a position apart from the vane 5e toward the discharge slit h6 side by a distance L1 in the X-axis direction so as not to overlap the vane 5e reciprocating in the radial direction (so that the oil groove h10 is not blocked by the vane 5 e). The distance L1 is preferably in the range of 0.5mm to 2.0mm, for example, but is not limited thereto. By providing the oil groove h10 in the vicinity of the vane 5e in this manner, the lubricating oil discharged from the oil groove h10 to the cylinder chamber Cy is easily attached to the side surface and 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.
In addition, the position of the oil groove h10 in the Y axis direction is within the oil suction interval Δ θ in (refer to FIG. 6) and oil release interval Δ θ out Oil grooves h10 are provided at substantially the same positions (see fig. 6). The oil suction interval Delta theta in Refers to the range of the rotation angle of the roller 5b when the lubricating oil is sucked into the oil groove h10. More specifically, the range of the rotation angle of the roller 5b in a state where the oil groove h10 (concave portion) is located radially inside the roller 5b is the oil suction interval Δ θ in 。
On the other hand, the oil release interval Δ θ out Is the range of the rotation angle of the roller 5b when the lubricating oil is released from the oil groove h10. More specifically, the range of the rotation angle of the roller 5b in a state where the oil groove h10 (concave portion) is located between the roller 5b and the cylinder 5a is the oil release section Δ θ out . By making the oil suction interval delta theta in And oil release interval delta theta out Approximately equal, the amount of lubricating oil sucked into oil groove h10 per unit time is approximately equal to the amount of lubricating oil discharged from oil groove h10. Therefore, the intermittence of the oil groove h10 to the compression chamber Com can be improvedVolumetric efficiency when lubricating oil is supplied.
The oil groove h10 has a diameter smaller than the radial thickness of the roller 5 b. More specifically, the diameter of the oil groove h10 is shorter than the radial length of the seal surface (annular lower surface) of the roller 5 b. Thus, the oil suction interval Δ θ in And oil release interval delta theta out The enclosed area delta theta between occ (see fig. 6) and the oil groove h10 is temporarily closed by the seal surface of the roller 5 b.
Fig. 5 is an explanatory view of a process in which the roller 5b moves in the cylinder 5 a.
The rotation angle θ shown in fig. 5 is a rotation angle of the roller 5b moving (revolving) in the cylinder 5 a. In addition, 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 a position of the roller 5b at the start of compression of the refrigerant in the compression chamber Com. In other words, the "top dead center" is a position of the roller 5b when the center of the roller 5b is closest to the tip of the blade 5e (when the blade 5e is retreated maximally) in the direction in which the blade 5e extends in a plan view (Y-axis direction in fig. 4).
As shown in fig. 4, in a state where the rotation angle of the roller 5b is 0 °, the oil grooves h10 (concave portions) are located radially inward of the roller 5 b. Therefore, the lubricating oil supplied to the space G radially inside the roller 5b sequentially via the oil supply passage 4c (see fig. 3) and the lateral hole h3 (see fig. 3) is sucked into the oil groove h10.
In addition, in a state where the rotation angle of the roller 5b is 90 °, the oil groove h10 (concave portion) is closed by the roller 5 b. This prevents the spaces on the radially inner and outer sides of the roller 5b from communicating with each other through the oil groove h10. Therefore, even if the oil groove h10 is provided, the efficiency when the refrigerant is compressed in the compression mechanism portion 5 is hardly lowered.
In addition, in a state where the rotation angle of the roller 5b is 180 °, the oil groove h10 (concave portion) is positioned between the roller 5b and the cylinder 5 a. As a result, the lubricating oil in the oil groove h10 is discharged to the compression chamber Com. On the other hand, the gaseous refrigerant enters oil groove h10 to replace the lubricating oil.
The space G radially inside the roller 5b communicates with the space inside the sealed container 1 (here, the outside of the compression mechanism 5: see fig. 1) via the horizontal hole h3 (see fig. 3) and the oil supply passage 4c (see fig. 3) in this order. Therefore, in a state where oil groove h10 is closed by roller 5b at θ =90 °, the pressure of the lubricating oil in oil groove h10 is substantially equal to the pressure of the refrigerant (discharge pressure 9) in hermetic container 1. On the other hand, the pressure of the refrigerant in the compression chamber Com of θ =180 ° is lower than the predetermined discharge pressure because it is in the middle of compression. Therefore, when θ =180 °, the lubricating oil in the oil groove h10 is diffused to the compression chamber Com of relatively low pressure.
In addition, in a state where the rotation angle of the roller 5b is 270 °, the oil groove h10 (concave portion) is closed by the roller 5 b. This prevents the spaces on the radially inner and outer sides of the roller 5b from communicating with each other through the oil groove h10.
When the rotation angle of the roller 5b returns to 0 ° (i.e., the top dead center), the high-pressure lubricating oil present on the inner side in the radial direction of the roller 5b enters the oil groove h10 again. In this way, the lubricating oil is intermittently supplied to the compression chamber Com.
The oil groove h10 (concave portion) is provided on the "discharge flow path" side of the vane 5e in the circumferential direction. As described above, the "discharge passage" is a passage including the discharge slit h6 (see fig. 4) and the discharge port h8 (see fig. 4). Thus, the refrigerant (e.g., "θ =180 °" in fig. 5) diffused in the compression chamber Com naturally concentrates in the vicinity of the tip of the blade 5e as the compression chamber Com is reduced in size (e.g., "θ =270 °" in fig. 5) in accordance with the movement of the roller 5 b.
This makes it easy for the lubricating oil to adhere to the side surface of the vane 5e on the compression chamber Com side, in addition to the tip of the vane 5e shown in fig. 4. The tip and side surfaces of the vane 5e are portions where sliding friction is particularly likely to occur in the compression mechanism 5. Further, the lubricating oil diffused in the compression chamber Com sufficiently lubricates the sliding surfaces of the cylinder 5a and the roller 5b in addition to the vane 5e.
Further, a force pressing the vane 5e toward the suction pipe Pi (i.e., the suction passage h4 side: see fig. 3) acts by a pressure difference between the suction chamber In (see fig. 5) and the compression chamber Com (see fig. 5). As a result, the lubricating oil enters a minute gap between the side surface of the vane 5e on the discharge slit h6 side and the wall surface of the cylinder 5a, and thereby the sliding surfaces of the cylinder 5a and the vane 5e are sufficiently lubricated by the lubricating oil from the oil groove h10.
The rear end of the vane 5e on the vane spring 5g side faces the space in the sealed container 1 (see fig. 1). Therefore, the mist of the lubricant oil in the closed casing 1 also adheres to the rear end portion of the vane 5e. As a result, as the vane 5e reciprocates, the lubricating oil is also applied to the side surface of the vane 5e on the suction chamber In side, and the sliding surfaces of the cylinder 5a and the vane 5e are lubricated.
FIG. 6 is an oil suction interval Deltaθ in the oil groove in Delta theta between the closed zones occ And oil release interval Delta theta out Description of the drawings (refer to fig. 5 as appropriate).
As described above, the rotation angle θ shown in fig. 6 is the rotation angle of the roller 5b moving (revolving) in the cylinder 5a, and the rotation angle at the top dead center is set to θ =0 °. Then, as the roller 5b moves, the suction of the lubricating oil into the oil groove h10 is sequentially repeated (oil suction interval Δ θ) in ) Sealing of the oil groove h10 (sealing interval Δ θ) occ ) And release of lubricating oil to compression chamber Com (oil release interval Deltatheta) out ) And sealing of the oil groove h10 (sealing interval Δ θ) occ )。
Further, as shown in fig. 6, the oil intake interval Δ θ is preferably set to be smaller than the oil intake interval Δ θ in And oil release interval delta theta out Are approximately equal. More specifically, the oil suction interval Δ θ in And oil release interval Delta theta out Each of the angles is preferably 140 ° or more and 165 ° or less. Thus, in the oil suction interval Delta theta in The lubricating oil sucked into the oil groove h10 is in the oil release range Δ θ out Is discharged to the compression chamber Com without waste. Therefore, the volumetric efficiency when lubricating oil is intermittently supplied from the oil groove h10 to the compression chamber Com can be improved.
In addition, the oil suction interval Δ θ in And oil release interval delta theta out The relationship of (b) is not particularly limited. For example, the oil suction interval Δ θ may be set to be smaller than the oil suction interval Δ θ in =150 °, on the other hand, the oil release interval Δ θ out =160 °. For example, the oil suction interval Δ θ may be set to be smaller than the oil suction interval Δ θ in =165 °, anotherIn one aspect, the oil release interval Δ θ out ＝140°。
Fig. 7 is a graph showing the result of an APF experiment of the oil groove volume ratio (see fig. 2 as appropriate).
The abscissa of fig. 7 represents the oil tank volume ratio (hereinafter referred to as the oil tank volume ratio Vpr), and the ordinate represents the APF (Annual Performance Factor) of the air conditioner using the compressor 100 (see fig. 1) of the present embodiment. The oil groove volume ratio Vpr is a ratio of the volume Vp of the oil groove h10 (recess) to the stroke volume of the cylinder 5a, and is calculated based on the following equation (1). The "stroke volume" described above refers to the volume of the cylinder chamber Cy (see fig. 2) in a state where the rotation angle θ =0 ° of the roller.
Vpr＝Vp/Vth×100···(1)
Then, the diameter of the oil groove h10 is set to a predetermined fixed value, while the depth dimension of the oil groove h10 is appropriately changed, and APFs are calculated for each of a plurality of cases where the oil groove volume ratios are different, and plotted as dots indicated by black circles in fig. 7. According to the experimental result, the oil groove volume ratio Vpr, which is a ratio of the volume of the oil groove h10 to the stroke volume, is preferably 0.001% or more and 0.019% or less. This is because if the tank volume ratio Vpr is within the above range, the APF becomes higher than the case where the tank h10 is not provided (the case where the tank volume ratio Vpr = 0).
In particular, when the oil groove volume ratio Vpr is 0.01%, the extent of increase in APF based on the case where the oil groove h10 is not provided (the case where Vpr = 0) is 0.36%, and the APF is the highest.
The hollow circle mark indicated by reference sign J is an experimental result in the case where an oil groove (not shown) is provided at the same position as the mark described in fig. 2 of the above-described prior art document. In this case, since the oil groove is distant from the vane 5e, the vicinity of the vane 5e having a large sliding friction is not sufficiently lubricated, and the APF is reduced as compared with a case where the oil groove is not provided (the oil groove volume ratio Vpr = 0). In contrast, according to the first embodiment, as described above, the vicinity of the vane 5e is lubricated well, and the sealing property of the compression chamber Com is maintained, so that the APF can be greatly improved as compared with the conventional case.
For example, in the case where the stroke volume Vth =9.5[ 2 ], [ ml/rev ], if the depth of oil groove h10 is set to 0.13[ 2 ], [ mm ], the oil groove volume ratio Vpr is about 0.01%, when the diameter of oil groove h10 is set to 3[ 2 ], [ mm ]. By providing very small oil groove h10 on the upper surface of lower bearing 5d in this manner, the performance and reliability of compressor 100 can be improved.
< Effect >
According to the first embodiment, since the lubricating oil is intermittently supplied from the oil groove h10 of the lower bearing 5d to the compression chamber Com, the sealing performance of the compression chamber Com can be improved. Further, by providing the oil groove h10 in the vicinity of the vane 5e, the respective sliding surfaces of the vane 5e and the cylinder 5a can be sufficiently lubricated. In particular, by providing the oil groove h10 on the side of the discharge slit h6 (see fig. 4) with respect to the vane 5e, the lubricant oil is easily attached to the tip and side surfaces of the vane 5e. Therefore, the lubricity and the sealing property of the compression mechanism section 5 (see fig. 4) can be improved particularly even in low-speed rotation in which an oil film is difficult to form. Further, even when the refrigerant R32 which is likely to become high-temperature and high-pressure is used, the compressor 100 having high performance and high reliability can be provided.
In addition, the oil suction interval delta theta is set in And oil release interval delta theta out Substantially equally (see fig. 6), almost all of the lubricating oil entering the oil groove h10 is discharged to the compression chamber Com. This ensures sufficient lubricity and sealing performance of the compression mechanism 5 even when the volume of the oil groove h10 is relatively small. If the volume of the oil groove h10 is too large, the oil release interval Δ θ is set to be large out The amount of the refrigerant (the amount of the relatively low-pressure refrigerant during compression) that enters the oil groove h10 increases, and the refrigerant is released into the closed casing 1 having substantially the same discharge pressure. Therefore, considering the high efficiency in compressing the refrigerant, the volume of the oil groove h10 is preferably small.
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 mechanisms 51 and 52 (see fig. 8). The second embodiment is different from the first embodiment in that oil grooves h11 and h12 (see fig. 8) are provided in a partition plate 50 (see fig. 8) that partitions the compression mechanism units 51 and 52. Otherwise, the same points as those in the first embodiment are used. Therefore, portions different from those of the first embodiment will be described, and redundant portions will not be described.
Fig. 8 is a longitudinal sectional view of a compressor 100A according to the second embodiment.
As shown in fig. 8, the compressor 100A includes a closed casing 1, a motor 2, a crankshaft 4A (drive shaft), two compression mechanism units 51 and 52, a partition plate 50, and noise muffling covers 61 and 62.
The sealed container 1 contains two compression mechanism units 51 and 52, a partition plate 50, and the like in addition to the motor 2 and the crankshaft 4A, and further contains 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 other eccentric portion 42b in a plan view. This cancels out the rotational imbalance accompanying the movement of one eccentric portion 41b by the other eccentric portion 42b, and suppresses the vibration of 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 mechanism units 51 and 52 shown in fig. 8 are each a mechanism for compressing the refrigerant as the crankshaft 4 rotates. These compression mechanism portions 51 and 52 are fastened together with a partition plate 50 (described later) by a plurality of bolts T (see fig. 9). The upper compression mechanism 51 compresses the gaseous refrigerant guided through the suction pipe P1 i. The refrigerant compressed by the compression mechanism 51 in this way is released into the space in the closed casing 1 through the discharge valve 51f and the hole (not shown) of the muffler cover 61 in this order.
On the other hand, the lower compression mechanism 52 compresses the gaseous refrigerant guided through the suction pipe P2 i. The refrigerant compressed by the compression mechanism 52 is released into the space in the closed casing 1 through the discharge valve 52f and the hole (not shown) of the muffler cover 62 in this order. The noise reduction cover 62 is fixed to the lower bearing 5d in a state of 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. The respective configurations of the compression mechanism 51 are the same as those of the compression mechanism 5 (see fig. 1) of the first embodiment, and therefore, the description thereof is 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 respective configurations of the compression mechanism 52 are also the same as those of the compression mechanism 5 (see fig. 1) of the first embodiment, and therefore, the description thereof is omitted.
The partition plate 50 shown in fig. 8 is a plate that partitions the two compression mechanism units 51 and 52 in the axial direction of the rotor 2b, and has an annular shape (see also fig. 10). When the upper bearing 5c (or the lower bearing 5 d) is provided on "one axial side" of the cylinder 51a, the partition plate 50 is provided on "the other axial side" of the cylinder 51 a.
In the partition plate 50, an oil groove h11 (concave portion) is provided on a surface (upper surface) of the upper compression mechanism 51 facing a cylinder chamber (not shown). Further, in the partition plate 50, another oil groove h12 (concave portion) is provided on a surface (lower surface) of the lower compression mechanism 52 facing the cylinder chamber (see fig. 9). In this way, in the second embodiment, the oil grooves h11, h12 are provided in the partition plate 50.
Further, the oil groove h12 is provided on the lower surface of the partition plate 50, but the lubricating oil also adheres to the oil groove h12. Therefore, the lubricating oil is intermittently supplied from the oil groove h12 to the compression chamber Com2 as the rotor 2b moves.
Fig. 9 is a sectional view taken along the line III-III of fig. 8.
As shown in fig. 9, the oil groove h12 (concave portion) is provided on the side of the discharge slit h26 (discharge flow path side) with respect to the vane 52e in the circumferential direction. Thereby, the lubricating oil spreads over the sliding surfaces of the vane 52e, the cylinder 52a, and the roller 52 b. Similarly, the other oil groove h11 (concave portion: see fig. 8) is also provided on the discharge opening side (discharge flow path side: not shown) of the vane 51e (see fig. 8) in the circumferential direction.
Further, although not shown, when the rotation angle of the roller 52b when the roller 52b in the cylinder 52a is positioned at the top dead center is set to 0 °, the oil groove h12 (concave portion) is positioned radially inward of the roller 52b in a state where the rotation angle of the roller 52b is 0 °.
In addition, in a state where the rotation angle of the roller 52b is 180 °, the oil groove h12 (concave portion) is positioned between the roller 52b and the cylinder 52 a. This allows the sliding surfaces of the vane 52e, the cylinder 52a, and the roller 52b to be lubricated appropriately.
In addition, the oil groove h12 (concave portion) is closed by the roller 52b in a state where the rotational angle of the roller 52b is 90 ° and a state where the rotational angle of the roller 52b is 270 °. This prevents the radially inner and outer spaces of the roller 52b from communicating with each other via the oil groove h12.
The same can be said for the rotation angle of the roller 51b in the upper compression mechanism 51 (see fig. 8).
Further, the range of the rotation angle of the roller 52b in a state where the oil groove h12 (concave portion) is located radially inside the roller 52b, and the range of the rotation angle of the roller 52b in a state where the oil groove h12 is located between the roller 52b and the cylinder 52a are preferably 140 ° or more and 165 ° or less, respectively. As a result, almost all of the lubricating oil that has entered the oil groove h12 is released to the compression chamber Com, and therefore, the lubricating property and the sealing property of the compression mechanism 52 can be sufficiently ensured. The same applies to the upper compression mechanism 51 (see fig. 8).
Fig. 10 is a plan view and a sectional view 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 penetrating the crankshaft 4A (see fig. 8). The partition plate 50 is provided with four holes h16 for passing through the bolts T (see fig. 9) in addition to the three holes h14 for sound attenuation.
The partition plate 50 is provided with a pair of oil grooves h11 and h12 at substantially the same positions in plan view. The radial and circumferential positions of the oil grooves h11, h12 in plan view may be substantially the same as shown in fig. 10, or may be different.
The oil grooves h11 and h12 may be formed by a sintering process of the partition plate 50 using a predetermined metal material. In addition, the oil grooves h11, h12 may be formed by cutting using an end mill (not shown). This can reduce the processing cost for forming the oil grooves h11 and h12.
Fig. 11A is a partially enlarged longitudinal cross section of the oil groove h11 of the partition plate 50.
In the example shown in fig. 11A, the diameter of the oil groove h11 (see also fig. 10) having a circular shape in plan view is a length L2, and the depth from the upper surface of the partition plate 50 to the bottom surface of the oil groove h11 is a length L3. In designing the oil groove h11, the ratio of the volume of the oil groove h11 (concave portion) to the stroke volume of the cylinder 51a (see fig. 8) is preferably 0.001% to 0.019%. This can improve the APF of the air conditioner including the compressor 100A (see fig. 8) as compared with the case where the oil groove h11 is not provided. The same applies to the other oil groove h12 (see fig. 10) of the partition plate 50.
Fig. 11B is a partially enlarged vertical cross-sectional view of the oil groove h11s of the partition plate 50B according to the modification of the second embodiment.
As shown in fig. 11B, for example, the oil groove h11s may be cut by a drill (not shown) so that the oil groove h11s has a predetermined volume. That is, the oil groove h12s having a V-shaped surface in a cross-sectional view may be provided so that the diameter is a length L4 and the depth is a length L5. Even with such a configuration, the same effect as in the case of fig. 11A can be obtained.
Third embodiment
The third embodiment is different from the first embodiment in that the compressor 100C (see fig. 12) is provided with a predetermined recess portion h17 in the vane 5Ce in addition to the oil groove h10 provided in the lower bearing 5d. The other configurations are the same as those of the first embodiment (see fig. 1). Therefore, portions different from those of the first embodiment will be described, and redundant portions will not be described.
Fig. 12 is a longitudinal sectional view of a compressor 100C according to the third embodiment.
As shown in fig. 12, the compression mechanism 5C includes a vane 5Ce having a recess h17 formed in a side surface thereof. The recessed portion h17 is a recess for sucking the lubricating oil when the vane 5Ce moves backward and supplying the lubricating oil to the compression chamber Com (or a cylinder chamber including the compression chamber Com) when the vane 5Ce moves forward toward the center axis line Z.
For example, in a state where the rotation angle of the roller 5b is 0 °, at least a part of the recessed portion h17 exists radially outside the cylinder 5a, and in a state where the rotation angle of the roller 5b is 180 °, at least a part of the recessed portion h17 exists between the roller 5b and the cylinder 5 a. Thereby, the lubricating oil is intermittently supplied to the compression chamber Com and the like. Therefore, in conjunction with the supply of the lubricating oil through the oil groove h10, the lubricating oil can be sufficiently supplied to the sliding surfaces of the cylinder 5a and the vane 5Ce. The recessed portion h17 may be provided only on one side surface of the blade 5Ce having 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, the lubricating oil can be sufficiently supplied to the respective sliding surfaces 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. The configuration of the compressor 100 is the same as that described in the first embodiment (see fig. 1), and therefore, the description thereof is omitted.
Fig. 13 is a configuration diagram of an air conditioner W according to a fourth embodiment.
In addition, solid arrows in fig. 13 indicate the flow of the refrigerant during the heating operation.
In addition, the broken line arrows in fig. 13 indicate the flow of the refrigerant during the cooling operation.
An 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 for compressing 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 present invention is not limited thereto.
The condenser E1 is a heat exchanger that exchanges heat between the refrigerant flowing through a heat transfer pipe (not shown) thereof and the air sent in from the first fan F1.
The first fan F1 is a fan that sends air to the condenser E1, and is provided in the vicinity of the condenser E1.
The evaporator E2 is a heat exchanger that exchanges heat between the refrigerant flowing through a heat transfer pipe (not shown) thereof and the air sent in from the second fan F2.
The second fan F2 is a fan that sends air to the evaporator E2, and is provided in the vicinity of the evaporator E2.
The expansion valve V has a function of decompressing 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 through the compressor 100, the condenser E1, the expansion valve V, and the evaporator E2 in this order. The refrigerant evaporated in the evaporator E2 is gas-liquid separated in the accumulator M, and the gaseous refrigerant is guided to the compressor 100.
Further, 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.
< effects >
According to the fourth embodiment, since sufficient lubricating oil is supplied to the compression chamber Com (see fig. 1) of the compression mechanism 5 (see fig. 1) provided in the compressor 100, the sealing performance of the compression chamber Com can be maintained well, and the lubricating performance of the sliding surfaces of the vane 5e (see fig. 1), the cylinder 5a (see fig. 1), and the roller 5b (see fig. 1) can be maintained. Therefore, according to the fourth embodiment, the air conditioner W with high performance and high reliability can be provided.
Modifications of the invention
The compressor 100 and the like of the present invention have been described above in the respective embodiments, but the present invention is not limited to these descriptions, and various modifications are possible.
For example, in the first embodiment (see fig. 1), the configuration in which the oil groove h10 is provided on the upper surface of the lower bearing 5d is described, but the present invention is not limited thereto. That is, the oil groove may be provided on the lower surface of the upper bearing 5c, or may be provided on both the upper bearing 5c and the lower bearing 5d. In other words, in the compressor 100, an oil groove (recess) may be provided in a surface facing the cylinder chamber Cy in 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 configuration in which the oil grooves h11 and h12 are provided in the partition plate 50 is described, but the present invention is not limited thereto. That is, in the compression mechanism 51, an oil groove (recess) may be provided in at least one of the upper bearing 5c (bearing) and the partition plate 50 on a surface facing the cylinder chamber. In the compression mechanism 52, an oil groove (recess) may be provided in at least one of the lower bearing 5d (bearing) and the partition plate 50 on a surface facing the cylinder chamber.
In the second embodiment (see fig. 8), the configuration in which the compressor 100A includes the two compression mechanisms 51 and 52 is described, but the present invention is not limited thereto. That is, the compressor may have a configuration in which three or more compression mechanism units (not shown) are provided. In such a configuration, in the uppermost compression mechanism portion (not shown), an oil groove is provided in a surface of at least one of the upper bearing and the partition plate facing the cylinder chamber, and in the lowermost compression mechanism portion (not shown), an oil groove is provided in a surface of at least one of the lower bearing and the partition plate facing the cylinder chamber. In each of the remaining compression mechanism sections (not shown) other than the uppermost and lowermost sections, an oil groove is provided on a surface facing the cylinder chamber of at least one of the pair of partition plates that sandwich the rotor and the cylinder. Such a configuration can also provide the same effects as those of the respective embodiments. Further, an oil groove may be provided in at least one of the plurality of compression mechanism units, and no oil groove may be provided in the remaining portion.
In addition, the embodiments can be appropriately combined. 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 grooves h11 and h12 are provided in the partition plate 50 (see fig. 8).
Further, the oil groove 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 blade 5e may be left. Even with such a configuration, the sealing performance and the lubricity of the compression mechanism section 5C can be maintained satisfactorily.
In the embodiments, the case where the compressor 100 is disposed vertically has been described, but the present invention is not limited thereto. That is, the embodiments can be applied also to the case where the compressor 100 is disposed in a horizontal or inclined manner.
The air conditioner W (see fig. 13) described in the fourth embodiment can be applied to various types of air conditioners such as a multi-air conditioner for a building, in addition to an indoor air conditioner and a combined air conditioner.
In the fourth embodiment, a 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 or the like in addition to a refrigerator, a water heater, an air-conditioning hot water supply system.
The refrigerant used in the air conditioner W is not limited to the refrigerant R32, and various types of refrigerants such as a refrigerant containing propane as a main component, for example, can be used in addition to the refrigerant R410A and the refrigerant R600A.
The embodiments are described in detail to explain the present invention easily and understandably, and are not limited to having all the configurations described. Further, a part of the configuration of each embodiment can be added, deleted, and replaced with another configuration.
The above-described mechanisms and structures are illustrative of the mechanisms and structures necessary for the description, and not necessarily all of the mechanisms and structures are shown in the product.
Description of the symbols
100. 100A, 100C-compressor; 1, sealing a container; 2-an electric motor; 2 a-a stator; 2 b-a rotor; 4. 4A-crankshaft (drive shaft); 4 c-oil supply path; 5. 51, 52, 5C — compression mechanism section; 5c — upper bearing (first bearing, bearing); 5 d-lower bearing (second bearing, bearing); 5a, 51a, 52 a-cylinder; 5b, 51b, 52 b-rollers; 5e, 51e, 52e, 5Ce — blade; 5f, 51f, 52 f-exhaust valve; 50. 50B-a partition plate; com, com 2-compression chamber; cy, cy 2-cylinder chamber; e1-a condenser; e2-an evaporator; g is a space; h6, h26 — discharge slit (discharge flow path); h 8-discharge port (discharge flow path); h10, h11s, h12 s-oil groove (recess); h17 — a recess; in-suction chamber; q-refrigerant circuit; v-expansion valve; w-air conditioner (refrigeration cycle device); z-the central axis.
Claims (9)
1. A compressor is characterized by comprising:
a motor having a stator and a rotor;
a drive shaft that rotates integrally with the rotor;
a compression mechanism unit that compresses a refrigerant in accordance with rotation of the drive shaft; and
a hermetic container which houses at least the motor, the drive shaft, and the compression mechanism part and in which lubricating oil is sealed,
the compression mechanism section includes:
an annular cylinder body;
an annular roller that revolves inside the cylinder in accordance with driving of the motor;
a first bearing provided on one side of the cylinder block in an axial direction and configured to support the drive shaft;
a second bearing provided on the other axial side of the cylinder block and configured to axially support the drive shaft;
a plate-like vane having a tip contacting an outer circumferential surface of the roller and dividing a cylinder chamber between the cylinder block and the roller into a suction chamber and a compression chamber; and
a discharge valve provided in a discharge flow path communicating with the compression chamber,
the space radially inside the roller communicates with the oil supply passage of the drive shaft,
a concave portion is provided on a surface of at least one of the first bearing and the second bearing facing the cylinder chamber,
wherein, when the rotation angle of the roller when the roller is positioned at the top dead center is set to 0 ° in the cylinder, the concave portion is positioned radially inward of the roller when the rotation angle of the roller is 0 °, and the concave portion is positioned between the roller and the cylinder when the rotation angle of the roller is 180 °,
the recess is provided closer to the discharge flow path side than the vane in the circumferential direction,
wherein the concave portion is provided at a position spaced apart from the vane by a predetermined distance in the direction of the X axis in the discharge flow path side when a central axis of the drive shaft is a Z axis, a straight line perpendicular to the Z axis and parallel to a side surface of the vane is a Y axis, and a straight line perpendicular to both the Y axis and the Z axis is an X axis,
the space radially inside the roller is not in direct communication with the space between the roller and the cylinder.
2. A compressor is characterized by comprising:
an electric motor having a stator and a rotor;
a drive shaft that rotates integrally with the rotor;
two compression mechanism units that compress refrigerant in accordance with rotation of the drive shaft;
a partition plate that axially partitions the two compression mechanism sections; and
a closed container that accommodates at least the motor, the drive shaft, the two compression mechanism units, and the partition plate, and that encloses a lubricating oil,
each of the compression mechanism units includes:
an annular cylinder body;
an annular roller that revolves inside the cylinder in accordance with driving of the motor;
a bearing that supports the drive shaft;
a plate-like vane having a tip contacting an outer circumferential surface of the roller and dividing a cylinder chamber between the cylinder block and the roller into a suction chamber and a compression chamber; and
a discharge valve provided in a discharge flow path communicating with the compression chamber,
the bearing is arranged on one axial side of the cylinder body,
the partition plate is arranged at the other side of the cylinder body in the axial direction,
a space radially inside the roller communicates with an oil supply passage of the drive shaft,
in each of the compression mechanism units, a concave portion is provided on a surface facing the cylinder chamber of at least one of the bearing and the partition plate,
wherein the recessed portion is located radially inward of the roller when the rotational angle of the roller at the top dead center in the cylinder is 0 °, and the recessed portion is located between the roller and the cylinder when the rotational angle of the roller at the top dead center in the cylinder is 180 °,
the recess is provided closer to the discharge flow path side than the vane in the circumferential direction,
in a case where a central axis of the drive shaft is a Z axis, a straight line perpendicular to the Z axis and parallel to a side surface of the vane is a Y axis, and a straight line perpendicular to both the Y axis and the Z axis is an X axis, the concave portion is provided at a position separated by a predetermined distance from the vane toward the discharge flow path side in the direction of the X axis,
the space radially inside the roller is not in direct communication with the space between the roller and the cylinder.
3. Compressor according to claim 1 or 2,
the recessed portion is closed by the roller in a state where the rotation angle of the roller is 90 ° and a state where the rotation angle of the roller is 270 °.
4. Compressor according to claim 1 or 2,
the range of the rotation angle of the roller in a state where the recessed portion is located on the radially inner side of the roller and the range of the rotation angle of the roller in a state where the recessed portion is located between the roller and the cylinder are 140 ° or more and 165 ° or less, respectively.
5. Compressor according to claim 1 or 2,
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% to 0.019%.
6. Compressor according to claim 1 or 2,
a concave part is arranged on the side surface of the blade,
at least a part of the recessed portion is present on the radially outer side of the cylinder in a state where the rotation angle of the roller is 0 °, and at least a part of the recessed portion is present between the roller and the cylinder in a state where the rotation angle of the roller is 180 °.
7. A refrigeration cycle apparatus is characterized in that,
comprising a refrigerant circuit in which a refrigerant circulates through a compressor, a condenser, an expansion valve, and an evaporator in this order,
the compressor is provided with:
an electric motor having a stator and a rotor;
a drive shaft that rotates integrally with the rotor;
a compression mechanism unit that compresses a refrigerant in accordance with rotation of the drive shaft; and
a closed container that accommodates at least the motor, the drive shaft, and the compression mechanism and that encloses a lubricating oil,
the compression mechanism section includes:
an annular cylinder body;
an annular roller that revolves inside the cylinder in accordance with driving of the motor;
a first bearing provided on one side of the cylinder block in an axial direction and configured to support the drive shaft;
a second bearing provided on the other axial side of the cylinder block and configured to axially support the drive shaft;
a plate-like vane having a tip contacting an outer circumferential surface of the roller and dividing a cylinder chamber between the cylinder block and the roller into a suction chamber and a compression chamber; and
a discharge valve provided in a discharge flow path communicating with the compression chamber,
a space radially inside the roller communicates with an oil supply passage of the drive shaft,
a concave portion is provided on a surface of at least one of the first bearing and the second bearing facing the cylinder chamber,
wherein the recessed portion is located radially inward of the roller when the rotational angle of the roller at the top dead center in the cylinder is 0 °, and the recessed portion is located between the roller and the cylinder when the rotational angle of the roller at the top dead center in the cylinder is 180 °,
the recess is provided closer to the discharge flow path side than the vane in the circumferential direction,
wherein the concave portion is provided at a position spaced apart from the vane by a predetermined distance in the direction of the X axis in the discharge flow path side when a central axis of the drive shaft is a Z axis, a straight line perpendicular to the Z axis and parallel to a side surface of the vane is a Y axis, and a straight line perpendicular to both the Y axis and the Z axis is an X axis,
the space radially inside the roller is not in direct communication with the space between the roller and the cylinder.
8. A refrigeration cycle apparatus is characterized in that,
comprising a refrigerant circuit in which a refrigerant circulates through a compressor, a condenser, an expansion valve, and an evaporator in this order,
the compressor is provided with:
an electric motor having a stator and a rotor;
a drive shaft that rotates integrally with the rotor;
two compression mechanism units that compress refrigerant in accordance with rotation of the drive shaft;
a partition plate that axially partitions the two compression mechanism sections; and
a sealed container that houses at least the motor, the drive shaft, the two compression mechanism units, and the partition plate, and that encloses a lubricating oil,
each of the compression mechanism units has:
an annular cylinder body;
an annular roller that revolves within the cylinder in accordance with driving of the motor;
a bearing that supports the drive shaft;
a plate-like vane having a tip contacting an outer circumferential surface of the roller and dividing a cylinder chamber between the cylinder block and the roller into a suction chamber and a compression chamber; and
a discharge valve provided in a discharge flow path communicating with the compression chamber,
the bearing is arranged on one axial side of the cylinder body,
the partition plate is arranged on the other axial side of the cylinder body,
a space radially inside the roller communicates with an oil supply passage of the drive shaft,
in each of the compression mechanism units, a concave portion is provided on a surface facing the cylinder chamber of at least one of the bearing and the partition plate,
wherein, when the rotation angle of the roller when the roller is positioned at the top dead center is set to 0 ° in the cylinder, the concave portion is positioned radially inward of the roller when the rotation angle of the roller is 0 °, and the concave portion is positioned between the roller and the cylinder when the rotation angle of the roller is 180 °,
the recess is provided closer to the discharge flow path side than the vane in the circumferential direction,
in a case where a central axis of the drive shaft is a Z axis, a straight line perpendicular to the Z axis and parallel to a side surface of the vane is a Y axis, and a straight line perpendicular to both the Y axis and the Z axis is an X axis, the concave portion is provided at a position separated by a predetermined distance from the vane toward the discharge flow path side in the direction of the X axis,
the space radially inside the roller is not in direct communication with the space between the roller and the cylinder.
9. The refrigeration cycle apparatus according to claim 7 or 8,
the refrigerant is a refrigerant R32.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/041776 WO2021079477A1 (en) | 2019-10-24 | 2019-10-24 | Compressor and refrigeration cycle device |
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| Publication Number | Publication Date |
|---|---|
| CN114555948A CN114555948A (en) | 2022-05-27 |
| CN114555948B true CN114555948B (en) | 2023-01-10 |
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| CN201980101163.XA Active CN114555948B (en) | 2019-10-24 | 2019-10-24 | Compressor and refrigeration cycle device |
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|---|---|
| JP (1) | JP6704555B1 (en) |
| CN (1) | CN114555948B (en) |
| WO (1) | WO2021079477A1 (en) |
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| CN113494456B (en) * | 2020-04-07 | 2023-10-24 | 广东美芝制冷设备有限公司 | Bearing for compressor and compressor |
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| JPH07301190A (en) * | 1994-05-06 | 1995-11-14 | Hitachi Ltd | Rotary compressor |
| JPH08159070A (en) * | 1994-12-07 | 1996-06-18 | Daikin Ind Ltd | Rotary compressor |
| CN101779039A (en) * | 2008-05-23 | 2010-07-14 | 松下电器产业株式会社 | Fluid machine and refrigeration cycle device |
| CN108240332A (en) * | 2016-12-27 | 2018-07-03 | 日立江森自控空调有限公司 | Closed rotating compressor and refrigerating air-conditioning |
-
2019
- 2019-10-24 WO PCT/JP2019/041776 patent/WO2021079477A1/en active Application Filing
- 2019-10-24 JP JP2020509128A patent/JP6704555B1/en active Active
- 2019-10-24 CN CN201980101163.XA patent/CN114555948B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6157187U (en) * | 1984-09-20 | 1986-04-17 | ||
| JPS6338689U (en) * | 1986-08-30 | 1988-03-12 | ||
| JPH02286892A (en) * | 1989-04-26 | 1990-11-27 | Mitsubishi Electric Corp | Compressor with rolling piston |
| JPH07301190A (en) * | 1994-05-06 | 1995-11-14 | Hitachi Ltd | Rotary compressor |
| JPH08159070A (en) * | 1994-12-07 | 1996-06-18 | Daikin Ind Ltd | Rotary compressor |
| CN101779039A (en) * | 2008-05-23 | 2010-07-14 | 松下电器产业株式会社 | Fluid machine and refrigeration cycle device |
| CN108240332A (en) * | 2016-12-27 | 2018-07-03 | 日立江森自控空调有限公司 | Closed rotating compressor and refrigerating air-conditioning |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2021079477A1 (en) | 2021-04-29 |
| CN114555948A (en) | 2022-05-27 |
| JPWO2021079477A1 (en) | 2021-11-18 |
| JP6704555B1 (en) | 2020-06-03 |
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