CN108240332B - Closed rotary compressor and refrigerating air conditioner - Google Patents
Closed rotary compressor and refrigerating air conditioner Download PDFInfo
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- CN108240332B CN108240332B CN201711192662.3A CN201711192662A CN108240332B CN 108240332 B CN108240332 B CN 108240332B CN 201711192662 A CN201711192662 A CN 201711192662A CN 108240332 B CN108240332 B CN 108240332B
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- bearing
- pressure equalizing
- roller
- rotary compressor
- cylinder
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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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and 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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
Abstract
The invention provides a hermetic rotary compressor, which can equalize the pressure of the upper and lower end surfaces of a roller, equalize the gap between the end surfaces, reduce the supply amount of lubricating oil to the working space in a cylinder, and improve the performance and reliability. The hermetic rotary compressor includes a plurality of rotary compression units, a rotary shaft, a main bearing, a sub bearing, and a partition plate, wherein the rotary compression unit includes a cylinder having a cylinder chamber and a roller accommodated in the cylinder chamber, the rotary shaft has an eccentric portion, the roller is fitted in the eccentric portion, discharge valve devices are provided in the main bearing and the sub bearing, respectively, and a pressure equalizing groove is provided in at least one of an end surface of the main bearing and an end surface of the sub bearing which are in sliding contact with an end surface of the roller, and an end surface of the partition plate which is in sliding contact with an end surface of the roller.
Description
Technical Field
The present invention relates to a hermetic rotary compressor and a refrigerating and air-conditioning apparatus.
Background
In recent years, as the range of application capacity of hermetic rotary compressors has expanded, a double-cylinder rotary compressor including two sets of rotary compression elements, i.e., cylinders, has been standardized. In this type of compressor, the Performance under the rated condition (100% load) and the Performance under the intermediate condition (50% load) which becomes a partial load are important, and APF (Annual energy consumption efficiency) which takes the Performance under the intermediate condition into consideration becomes an evaluation index for energy saving.
In recent years, there has been a movement to change to an APF having a performance at a load of 25% in order to become an energy saving evaluation standard more suitable for practical use. Therefore, high efficiency at low load is an important issue.
On the other hand, in recent years, from the viewpoint of global warming prevention, attention has been given to an R32 refrigerant having a small warming potential as a refrigerant of a refrigeration and air-conditioning system, instead of the conventional R410A refrigerant.
Documents of the prior art
Patent document
Patent document 1: japanese patent No. 4953974
Disclosure of Invention
Problems to be solved by the invention
In the rotary compressor disclosed in patent document 1, both the low-stage side bearing load adjusting portion and the high-stage side bearing load adjusting portion are provided on the inner periphery in an annular recess so as to open the outer periphery of the shaft portion. Therefore, when the thrust load acting on the shaft portion (the weight of the shaft portion and the rotor, the magnetic thrust acting on the rotor, and the like) is axially supported by the lower end of the low-stage side eccentric portion of the shaft portion, the thrust load of the shaft portion is hardly received. In this case, for example, a thrust bearing for axially supporting the thrust load must be newly provided on the lower end surface of the shaft portion, and there is a problem of cost increase. In patent document 1, no mention is made of a thrust load acting on the shaft portion.
In patent document 1, pressure imbalance between the upper and lower end surfaces of the rolling piston due to the insertion hole of the intermediate plate can be eliminated by the low-stage-side bearing load adjusting portion and the high-stage-side bearing load adjusting portion. However, the discharge port of the discharge valve device, which is another cause of the pressure imbalance between the upper and lower end surfaces of the rolling piston, is not mentioned at all, and is not a problem as a factor of the pressure imbalance.
In a hermetic rotary compressor, a discharge valve device in the form of a reed valve is generally disposed in an end plate of a bearing that closes an opening end of a cylinder, and compressed working gas is discharged through a discharge port of the discharge valve device. The discharge port is provided at a position where a part thereof protrudes into the cylinder in a shape of engaging with a discharge notch formed in the cylinder in order to reduce the outflow resistance. Therefore, the discharge port is attached to the end face of the rolling piston at a shaft rotation angle position near the end of the discharge stroke. On the other hand, since there is no discharge port on the intermediate plate side abutting on the end face on the opposite side, this causes pressure imbalance. On the inner peripheral side of the rolling piston, high-pressure lubricating oil is present, and this lubricating oil leaks into the low-pressure cylinder working space due to a pressure difference through the gap between the upper and lower end surfaces. Therefore, setting this lubricating oil leakage amount to the minimum oil amount required for maintaining the sealing function of the cylinder working space is important in achieving an improvement in the performance of the compressor.
The lubricating oil in an amount more than the required amount causes a decrease in performance of the compressor due to heating loss, agitation loss, and the like. In addition, the amount of leakage of the lubricating oil is proportional to the third power of the end face clearance. Therefore, in order to reduce the amount of leakage of the lubricating oil, it is necessary to equalize the upper and lower end face clearances of the rolling piston.
However, in the rotary compressor disclosed in patent document 1, the pressure imbalance due to the discharge port is not considered. Therefore, there are the following problems: pressure equalization of the upper and lower end faces of the rolling piston is not achieved, and the leakage amount of lubricating oil is increased and the performance of the compressor is reduced due to the influence of deviation generated by the gap between the upper and lower end faces.
The invention aims to equalize the pressures of the upper and lower end surfaces of a roller, equalize the clearances of the end surfaces, reduce the supply amount of lubricating oil to a working space in a cylinder, and improve the performance and reliability in a hermetic rotary compressor.
Means for solving the problems
In order to achieve the above object, a hermetic rotary compressor according to the present invention includes a plurality of rotary compression elements, each of the rotary compression elements including a cylinder having a cylinder chamber and a roller accommodated in the cylinder chamber, a rotary shaft having an eccentric portion, the roller being fitted in the eccentric portion, discharge valve devices being provided in the main bearing and the sub-bearing, respectively, and a pressure equalizing groove being provided in at least one of an end surface of the main bearing and an end surface of the sub-bearing which are in sliding contact with an end surface of the roller and both end surfaces of the partition plate which is in sliding contact with an end surface of the roller.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, in the hermetic rotary compressor, the pressures of the upper and lower end surfaces of the roller can be equalized, the gap between the end surfaces can be equalized, and the supply amount of the lubricating oil to the working space in the cylinder can be reduced. In addition, the annual energy consumption efficiency of the refrigerating and air-conditioning apparatus can be improved by using such a hermetic rotary compressor.
Drawings
Fig. 1 is a longitudinal sectional view showing a hermetic rotary compressor according to an embodiment of the present invention.
Fig. 2 is a cross-sectional view a-a of fig. 1.
Fig. 3 is a sectional view B-O-B of fig. 2.
Fig. 4 is an enlarged sectional view of a main portion of a sectional view C-O-B corresponding to fig. 2.
Fig. 5 is an exploded view showing a positional relationship of the pressure equalizing groove of fig. 4.
Fig. 6 is a bottom view showing the pressure equalizing groove of the main bearing.
Fig. 7 is a plan view showing the pressure equalizing groove of the sub-bearing.
Fig. 8 is a plan view showing the pressure equalizing grooves of the partition plate.
Fig. 9A is a cross-sectional view D-D of fig. 8.
Fig. 9B is a partial cross-sectional view showing a modification of fig. 9A.
Fig. 10 is a partial longitudinal sectional view showing a hermetic rotary compressor according to another embodiment of the present invention.
Fig. 11 is an enlarged sectional view showing a main portion of the hermetic rotary compressor of fig. 10.
Fig. 12 is an exploded view showing a positional relationship of the pressure equalizing groove of fig. 11.
Fig. 13 is a partially enlarged view of fig. 11.
Fig. 14 is a plan view showing the sub-bearing of fig. 13.
Fig. 15 is a cross-sectional view E-E of fig. 14.
Fig. 16 is a schematic configuration diagram showing a refrigeration cycle of a refrigerating and air-conditioning apparatus including a hermetic rotary compressor according to the present invention.
In the figure: 1-a closed container, 2-a rotary compression unit, 2A-a first rotary compression unit, 2B-a second rotary compression unit, 3-a motor portion, 3 a-a stator, 3B-a rotor, 4-a rotary shaft, 4a, 4B-an eccentric portion, 4c, 4 d-a thrust portion, 5-a partition plate, 5 a-a through hole, 6A-a first cylinder, 6B-a second cylinder, 7-a main bearing, 7a, 8 a-a discharge cap, 7B, 8B-a discharge valve device, 7c, 8 c-a discharge port, 7d, 8 d-an annular groove, 7 e-a main bearing inner face, 8-a sub bearing, 8 e-a sub bearing inner face, 9a, 9B-a roller, 10 a-a first cylinder chamber, 10B-a second cylinder chamber, 11a, 11B-a vane, 12A, 12B-a vane spring, 14-a suction pipe, 15-a suction box, 16A, 16B-a suction pipe, 17a, 17B-a suction passage, 18-discharge pipe, 19-lubricating oil, 20, 21, 22, 23-pressure equalizing tank, 21 a-thrust surface oil supply tank, 24-fixing bolt, 24 a-bolt hole, 25-discharge passage, 30-hermetic rotary compressor, 31-refrigeration cycle, 32-condenser, 33-expansion valve, 34-evaporator, 35-refrigerant piping, 57, 58-notch portion, 67, 68-valve housing.
Detailed Description
The hermetic rotary compressor of the present invention is applied to, for example, an air conditioner, a refrigerator, and the like. In the present specification, a refrigerating and air-conditioning apparatus is a generic term for an air conditioner, a refrigerator, and the like that constitute a refrigeration cycle using a hermetic rotary compressor.
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The same symbols in the drawings of the respective embodiments denote the same or similar substances.
A hermetic rotary compressor according to a first embodiment of the present invention will be described with reference to fig. 1 to 9B.
Fig. 1 is a longitudinal sectional view showing a hermetic rotary compressor according to an embodiment of the present invention. Fig. 2 is a cross-sectional view a-a of fig. 1. Fig. 3 is a sectional view B-O-B of fig. 2. Fig. 4 is an enlarged sectional view of a main portion of a sectional view C-O-B corresponding to fig. 2. Fig. 5 is an exploded view of fig. 4 illustrating a positional relationship of the pressure equalizing grooves according to the embodiment of the present invention. Fig. 6 is a plan view of a main bearing showing a structure of a pressure equalizing groove which is a feature of the present invention. Fig. 7 is a plan view of a sub-bearing showing a structure of a pressure equalizing groove, which is a feature of the present invention. Fig. 8 is a plan view of a spacer plate showing a structure of a pressure equalizing groove, which is a feature of the present invention. Fig. 9A is a cross-sectional view D-D of fig. 8. Fig. 9B shows a modification of fig. 9A.
In fig. 1 to 3, reference numeral 1 denotes a closed container, a plurality of rotary compression units 2 are housed in a lower portion of the closed container 1, a motor unit 3 for driving the rotary compression units is housed in an upper portion, and the motor unit 3 and the rotary compression units 2 are coupled to each other by a rotary shaft 4. The motor unit 3 includes a stator 3a fixed to the inner surface of the closed casing 1 and a rotor 3b fixed to the rotating shaft 4. The rotor 3b is arranged to maintain a predetermined gap from the inside of the stator 3 a. The motor unit 3 is electrically connected to an inverter (not shown) for controlling the operating frequency.
The rotary compression element 2 includes a first rotary compression element 2A and a second rotary compression element 2B arranged vertically with a partition plate 5 interposed therebetween. The first rotary compression unit 2A on the upper side includes a first cylinder 6A. On the other hand, the second rotary compression element 2B on the lower side includes a second cylinder 6B.
The first cylinder 6A overlaps the lower surface of the main bearing 7 fixed to the inner surface of the closed casing 1. A sub bearing 8 is attached to the lower surface of the second cylinder 6B. The rotary shaft 4 is rotatably supported by a main bearing 7 and a sub-bearing 8. At the rotary shaft 4, two eccentric portions 4a, 4B are arranged at positions inside the first and second cylinders 6A, 6B with a phase difference of about 180 °. Rollers 9a and 9b (rolling pistons) are rotatably fitted to the outer peripheries of the eccentric portions 4a and 4 b.
The first cylinder 6A and the second cylinder 6B are partitioned into upper and lower surfaces by the partition plate 5, the main bearing 7, and the sub-bearing 8. A first cylinder chamber 10a is formed in the first cylinder 6A, and a second cylinder chamber 10B is formed in the second cylinder 6B.
A discharge cover 7a forming a discharge space for the compressed working fluid is attached to the main bearing 7. The discharge cover 7a covers a discharge valve device 7b attached to an end plate of the main bearing 7. A discharge cover 8a is also attached to the sub-bearing 8. The discharge cover 8a covers a discharge valve device 8b fitted to an end plate of the sub-bearing 8.
The discharge valve device 7b of the main bearing 7 communicates with the first cylinder chamber 10a, opens when the pressure in the cylinder chamber 10a rises to a predetermined pressure by a compression action, and discharges the compressed working fluid into the discharge cover 7 a. The discharge valve device 8b of the sub-bearing 8 communicates with the second cylinder chamber 10b, and is opened by a compression action when the pressure in the cylinder chamber 10b rises to a predetermined pressure, and discharges the compressed working fluid into the discharge cover 8 a.
As shown in fig. 3, a vane 11a disposed to reciprocate is housed in a cylinder chamber 10a of the first cylinder 6A. Similarly, the vane 11B is housed in the cylinder chamber 10B of the second cylinder 6B. Blade springs 12a and 12b are housed in rear end portions of the blades 11a and 11b, respectively. The blades 11a and 11b press the tip portions against the outer peripheral portions of the rollers 9a and 9b by the elastic forces of the blade springs 12a and 12b, respectively, to bias the rollers 9a and 9 b.
The lower end of the rotating shaft 4 protrudes below the sub-bearing 8 and is immersed in the lubricating oil 19 retained at the bottom of the closed casing 1. An oil feed pump is attached to the lower end surface of the rotary shaft 4, and lubricating oil is supplied from this oil feed pump through an oil feed passage to the sliding portions of the members constituting the second rotary compression unit 2B and the first rotary compression unit 2A.
In fig. 1, reference numeral 14 denotes an intake pipe through which the working fluid flows from an external refrigeration circuit into an intake box 15 having a gas-liquid separation function. A suction pipe 16a as a first suction pipe and a suction pipe 16b as a second suction pipe are connected to the bottom of the suction box 15. The suction pipes 16a, 16b are connected to a compressor. The intake pipe 16A communicates with the inside of the first cylinder chamber 10a via an intake passage 17a formed in the first cylinder 6A. The suction pipe 16B communicates with the inside of the second cylinder chamber 10B via a suction passage 17B formed in the second cylinder 6B.
A structure of the present invention for equalizing the pressures at the upper and lower end surfaces of the roller will be described with reference to fig. 4 to 9B.
Fig. 4 is an enlarged sectional view of a main portion of a sectional view C-O-B corresponding to fig. 2. Fig. 5 is an exploded view of fig. 4 with the rotary shaft 4, the first cylinder 6A, the second cylinder 6B, the rollers 9a, 9B, and the discharge valve devices 7B, 8B removed for explaining the positional relationship of the pressure equalizing grooves shown in the embodiment of the present invention.
In the present embodiment, an annular groove 7d is formed in the end surface of the main bearing 7 on the cylinder 6A side in order to prevent local contact between the rotary shaft 4 and the bearing. Similarly, an annular groove 8d is formed in the end surface of the sub-bearing 8 on the cylinder 6B side. A thrust portion 4c is formed on the bearing-side end surface of the eccentric portion 4a of the rotary shaft 4. A thrust portion 4d is formed on the bearing-side end surface of the eccentric portion 4b of the rotary shaft 4. Thereby, the shaft thrust load can be supported.
Further, the discharge valve device 7b of fig. 4 is provided at the bottom of the valve housing 67 of fig. 5. In addition, the discharge valve device 8b of fig. 4 is provided at the bottom of the valve housing 68 of fig. 5.
The partition plate 5 has a through hole 5 a. The rotary shaft 4 is inserted into the main bearing 7, the through hole 5a, and the sub-bearing 8.
The pressure equalizing grooves 20 and 21 ensure a bearing surface for the thrust load acting due to the weight of the rotary shaft 4, and eliminate pressure imbalance between the upper and lower end surfaces of the roller due to the through-holes 5a formed in the partition plate 5. Further, by providing the pressure equalizing grooves 20 and 21, pressure imbalance between the upper and lower end surfaces of the roller can be eliminated, the amount of leakage of lubricating oil into the cylinder chamber and the like can be reduced, the thickness of the wall separating the valve sleeves 67 and 68 and the annular grooves 7d and 8d can be ensured, and the strength of the main bearing 7 and the sub-bearing 8 can be maintained.
Further, although the effect of eliminating the pressure imbalance can be obtained even in either of the pressure equalizing grooves 20 and 21, it is preferable to have both of the pressure equalizing grooves 20 and 21.
The pressure equalizing groove 22 formed in the upper end surface of the partition plate 5 has the same shape (diameter d) as the discharge port 7c (discharge outlet portion) of the discharge valve device 7b disposed in the main bearing 7p1) And shallow grooves having a depth of 0.1mm or less recessed in the same projected position facing each other across the cylinder 6A. In other words, when the pressure equalizing groove 22 and the discharge port 7c are projected to a plane orthogonal to the rotation axis direction, the outer edge portions of the pressure equalizing groove 22 and the discharge port 7c are configured to overlap.In this case, the overlap deviation between the outer edge portions is preferably within 0.8% of the diameter of the discharge port 7 c.
The pressure equalizing groove 23 formed in the lower end surface of the partition plate 5 has the same shape (diameter d) as the discharge port 8c (discharge port portion) of the discharge valve device 8b provided in the sub-bearing 8p2) And shallow grooves having a depth of 0.1mm or less recessed at the same projected position facing each other across the cylinder 6B. In other words, when the pressure equalizing groove 23 and the discharge port 8c are projected to a plane orthogonal to the rotation axis direction, the pressure equalizing groove 23 is configured to overlap the outer edge portion of the discharge port 8 c. In this case, the overlap deviation between the outer edge portions is preferably within 0.8% of the diameter of the discharge port 8 c.
In general, the pressure equalizing grooves 22, 23 are formed on both end faces of the partition plate 5.
These pressure equalization grooves 22 and 23 can eliminate pressure imbalance between the upper and lower end surfaces of the roller due to the discharge ports 7c and 8 c. Even if only one of the pressure equalizing grooves 22 and 23 can obtain the effect of eliminating the pressure imbalance, it is preferable to have both the pressure equalizing grooves 22 and 23.
As described above, since the pressures on the upper and lower end surfaces of the roller can be equalized, the gap between the upper and lower end surfaces of the roller can be equalized, and the supply of the lubricating oil to the working space in the cylinder can be kept to a minimum.
Here, how the pressure equalization grooves 20, 21, 22, and 23 can eliminate the pressure imbalance will be further described.
If the pressure equalizing grooves 20, 21, 22, and 23 are not provided, the inner diameter sides of the rollers 9a and 9b are at the same pressure as the inside of the closed vessel, but the range of the pressure acting on the upper and lower end surfaces of the rollers is different due to the through hole 5a of the partition plate 5 and the discharge ports 7d and 8d provided in the main bearing 7 and the sub-bearing 8, so that the loads acting on the upper and lower surfaces of the rollers are different, and the rollers are pressed to the low load side. In contrast, in the case of the pressure equalizing grooves 20, 21, 22, and 23, the pressures acting on the upper and lower end surfaces of the roller can be made completely equal, and therefore, the loads acting on the upper and lower surfaces of the roller are made equal.
The pressure equalizing grooves 20, 21, 22, and 23 are effective, and if all of them are provided, the effect is most effective.
Further, the cylinder 6A is provided with a notch 57. This can reduce the flow path resistance of the fluid passing through the discharge port 7c from the inside of the cylinder chamber 10 a. Further, the cylinder 6B is provided with a notch portion 58. This can reduce the flow path resistance of the fluid passing through the discharge port 8c from the cylinder chamber 10 b.
Next, the operation of the hermetic rotary compressor configured as above will be described.
In fig. 1, when a current is applied to a stator 3a of the motor unit 3, a rotor 3b is driven, and a rotary shaft 4 supported by a main bearing 7 and a sub-bearing 8 is driven to rotate. Then, the rollers 9a and 9B rotatably fitted to the outer peripheries of the eccentric portions 4a and 4B of the rotary shaft 4 eccentrically rotate in the cylinders 6A and 6B, respectively, and the compression operation of the working fluid is performed.
The low-pressure working fluid passes through the suction tank 15 from the suction pipe 14, is introduced into the cylinder chambers 10a and 10B of the cylinders 6A and 6B through the suction pipes 16A and 16B, and is compressed. The compressed high-pressure working fluid flows out into the discharge covers 7a and 8a through the discharge valve portions 7b and 8b attached to the end plates of the main bearing 7 or the sub-bearing 8, and is discharged from the closed casing 1 to the external refrigeration circuit through the discharge pipe 18. The lubrication of each sliding portion of the hermetic rotary compressor is configured such that, as the rotary shaft 4 is driven, a centrifugal pump action of an oil feed pump attached to the lower end surface of the rotary shaft 4 is generated, the lubricating oil 19 accumulated in the bottom portion of the hermetic container 1 is extracted, and the lubricating oil is supplied to the sliding portions of the rotary compression units 2A and 2B through an oil feed passage (not shown) formed in the rotary shaft 4.
Next, the structure of each of the pressure equalizing grooves, which is a feature of the present invention, will be described with reference to fig. 6 to 9B.
Fig. 6 is a bottom view of the main bearing.
In this figure, a main bearing inner surface 7e is provided from the center of the rotation shaft, and an annular groove 7d is formed on the outer side thereof. A pressure equalizing groove 20 is formed outward from the outer peripheral portion of the annular groove 7 d. The inner diameter of the pressure equalizing groove 20 is equal to the outer diameter of the annular groove 7 d. In other words, the annular groove 7d and the pressure equalizing groove 20 constitute a continuous groove having a step. The inner peripheral portion of the pressure equalizing groove 20 may be formed in a shape opening to the annular groove 7 d. The annular groove 7d and the pressure equalizing groove 20 are recessed grooves.
In fig. 6, reference numeral 24a denotes a bolt hole of the fixing bolt 24 shown in fig. 2.
Fig. 7 is a plan view of the sub-bearing.
In this figure, a sub-bearing inner surface 8e is provided from the center of the rotation shaft, and an annular groove 8d is formed on the outer side thereof. A pressure equalizing groove 21 is formed outside the annular groove 8 d. The inner diameter of the pressure equalizing groove 21 is larger than the outer diameter of the annular groove 8 d. Therefore, the pressure equalizing groove 21 and the annular groove 8d do not have an overlapping portion. In other words, the pressure equalizing groove 21 is a recessed groove formed on the outer peripheral side of the annular groove 8d with the axial thrust load receiving surface interposed therebetween.
Fig. 8 is a top view of the spacer.
In this figure, a through hole 5a is formed in the center of the partition plate 5.
In the assembled state, the pressure equalizing groove 22 is formed at a position facing the discharge port 7c of the main bearing 7 shown in fig. 4. In this regard, the following can be seen: when the partition plate 5 shown in the present figure is inverted and overlapped with the main bearing 7 shown in fig. 6, the pressure equalizing groove 22 is overlapped with the discharge port 7c of the main bearing 7.
Fig. 9A and 9B are cross-sectional views D-D of fig. 8, showing the cross-sectional shape of the pressure equalizing grooves 22 formed in the partition plate 5.
In fig. 9A, the pressure equalizing groove 22 is formed in the same shape (diameter d) as the discharge port 7c formed in the main bearing 7p1) And a shallow groove having a depth delta of 0.1mm or less (fixed value). That is, in the case of this figure, the pressure equalizing groove 22 is a groove recessed by a simple cylindrical spot facing.
By forming the pressure equalizing grooves 22 in such a shape, it is possible to minimize an increase in dead volume due to the formation of the pressure equalizing grooves 22, and to eliminate pressure imbalance between the upper and lower end surfaces of the roller due to the discharge ports.
The specification of the depth δ of the pressure equalizing groove 22 to 0.1mm or less may be changed depending on the discharge capacity of the compressor and the operating conditions. The required specification of the present embodiment can be satisfied by defining the depth δ so that the volume of the pressure equalizing groove 22 becomes 5% or less of the volume of the discharge port portion. If the amount exceeds 5%, the refrigerant gas tends to accumulate, and the adverse effect on the performance of re-expansion of the accumulated gas increases, so that the desired performance improvement effect may not be obtained. Here, the volume of the discharge port portion refers to the volume of the discharge port 7c (cylindrical hole) shown in fig. 4.
In fig. 9B, the increase in dead volume is further reduced by forming the shape of the pressure equalizing groove 22 into a substantially conical shape. The depth of the deepest part is δ, and δ is 0.1mm or less. Note that the equalizing grooves 23 formed at end face positions (overlapping positions of the back surfaces of the partition plates 5) opposed to the equalizing grooves 22 are the same as the equalizing grooves 22, and therefore, the description thereof is omitted.
A hermetic rotary compressor according to a second embodiment of the present invention will be described with reference to fig. 10 to 15.
Fig. 10 is a longitudinal sectional view of the hermetic rotary compressor shown in the present embodiment. Fig. 11 is an enlarged sectional view of a main portion of fig. 10. Fig. 12 is an exploded view of fig. 11 illustrating a positional relationship of the pressure equalizing grooves in the present embodiment. Fig. 13 is a partially enlarged view of fig. 11. Fig. 14 is a plan view of the sub-bearing of fig. 13 showing the shape of the pressure equalizing grooves. Fig. 15 is a cross-sectional view E-E of fig. 14. In the drawings, the same members denoted by the same reference numerals as those in fig. 1 are the same members and exhibit the same functions.
In the present embodiment, the annular groove 7d of the first embodiment is not formed in the end surface of the main bearing 7 on the cylinder 6A side. Similarly, the annular groove 8d of the first embodiment is not formed in the end surface of the sub-bearing 8 on the cylinder 6B side.
In this case, the outer diameter of the pressure equalizing groove 20 formed in the end surface of the main bearing 7 on the cylinder 6A side is also equal to the outer diameter d of the through hole 5a formed in the partition plate 5mSubstantially the same size, inner diameter Di1Inner diameter d of main bearing 7s1Is large. Further, the receiving surface of the thrust portion 4c of the rotary shaft 4 is secured on the rotary shaft 4 side of the pressure equalizing groove 20.
The outer diameter of the pressure equalizing groove 21 formed in the cylinder 6B-side end surface of the sub-bearing 8 is equal to the outer diameter d of the through hole 5a formed in the partition plate 5mSubstantially the same size, inner diameter Di2Inner diameter d of secondary bearing 8s2Is large. And, at specific pressure and uniform pressureThe groove 21 secures a receiving surface of the thrust portion 4d of the rotary shaft 4 on the rotary shaft 4 side.
The pressure equalizing groove 22 formed in the upper end surface of the partition plate 5 has the same shape (diameter d) as the discharge port 7c of the discharge valve device 7b disposed in the main bearing 7 in the same manner as in the first embodimentp1) And shallow grooves having a depth of 0.1mm or less recessed in the same projected position facing each other with the cylinder 6A interposed therebetween. The pressure equalizing groove 23 formed in the lower end surface of the partition plate 5 has the same shape (diameter d) as the discharge port 8c of the discharge valve device 8b disposed in the sub-bearing 8p2) And shallow grooves having a depth of 0.1mm or less recessed in the same projected position facing each other across the cylinder 6B.
As shown in fig. 13 to 15, in the present embodiment, a thrust surface oil supply groove 21a that communicates the sub-bearing inner surface 8e with the pressure equalizing groove 21 is provided in the thrust receiving surface 8f formed on the inner peripheral side of the pressure equalizing groove 21 of the sub-bearing 8, and oil is supplied through this oil supply groove, whereby lubrication between the thrust receiving surface 8f and the thrust portion 4d of the rotary shaft 4 is maintained well.
The pressure equalization of the upper and lower end surfaces of the roller can be achieved by the pressure equalization grooves 20, 21, 22, 23 described above. Therefore, the gaps between the upper and lower end surfaces of the roller can be equalized, and the supply of the lubricating oil from the inner periphery of each roller to the working space in the cylinder can be kept to a minimum. In addition, the performance and reliability of the hermetic rotary compressor can be improved.
In addition, although the hermetic rotary compressor having two rotary compression elements has been described in the above description, the hermetic rotary compressor of the present invention is not limited to this, and can be applied to a hermetic rotary compressor having a structure in which three or more rotary compression elements are overlapped.
Next, a specific example of a refrigerating and air-conditioning apparatus equipped with the hermetic rotary compressor of the present invention will be described with reference to a configuration diagram of a refrigerating cycle shown in fig. 16.
Fig. 16 is a schematic diagram of a refrigeration cycle (refrigerating and air-conditioning apparatus) including a hermetic rotary compressor according to an embodiment of the present invention. Here, a refrigeration cycle using R32 as a working fluid (refrigerant) will be described as an example. R32 is a refrigerant having a Global Warming Potential (GWP) lower than that of the refrigerant R410A conventionally used in a refrigeration and air-conditioning system, and has been drawing attention in recent years from the viewpoint of global warming prevention.
In fig. 16, the members denoted by the same reference numerals as those in fig. 1 are the same members and exhibit the same functions. The refrigeration cycle 31 includes a hermetic rotary compressor 30. A condenser 32, an expansion valve 33, and an evaporator 34 are connected in this order by a refrigerant pipe 35, thereby constituting the refrigeration cycle 31.
Next, the flow of the refrigerant will be described.
The high-temperature and high-pressure refrigerant discharged from hermetic rotary compressor 30 enters condenser 32 to dissipate heat, and the temperature thereof decreases. The refrigerant discharged from the condenser 32 enters an expansion valve 33, becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant, and is discharged. The two-phase gas-liquid refrigerant that has exited the expansion valve 33 enters the evaporator 34, absorbs heat, is gasified, returns to the hermetic rotary compressor 30, is compressed again, and is repeatedly circulated in the same manner. Thus, in the case of the refrigeration apparatus, the evaporator 34 cools the object to be cooled. In the case of an air conditioner, a cooling operation for cooling the indoor air by the evaporator 34 or a heating operation for heating the indoor air by the condenser 32 is performed.
In the description of fig. 16, the case where the working fluid is R32 is described, but the present invention is not limited to this, and can be applied to a case where another working fluid is used.
As described above, according to the present invention, it is possible to provide a hermetic rotary compressor having uniform gaps between the end surfaces of the respective rollers and excellent performance and reliability, and to improve the performance and reliability of a refrigerating and air-conditioning system.
Claims (11)
1. A hermetic rotary compressor is characterized by comprising:
a plurality of rotary compression units;
a rotating shaft;
a main bearing;
a secondary bearing; and
the space plate is arranged on the upper surface of the base plate,
the rotary compression unit includes a cylinder having a cylinder chamber and a roller accommodated in the cylinder chamber,
the rotating shaft is provided with an eccentric part,
the roller is embedded in the eccentric part,
the main bearing and the auxiliary bearing are respectively provided with a discharge valve device,
an annular groove is formed in the end surface of the main bearing and the sub-bearing on the cylinder side,
a pressure equalizing groove is provided in at least one of an end surface of the main bearing and an end surface of the sub bearing which are in sliding contact with an end surface of the roller,
the pressure unevenness of the upper and lower end surfaces of the roller due to the through-holes formed in the partition plate is eliminated by the pressure equalizing grooves.
2. The hermetic rotary compressor according to claim 1,
the outer diameter of the pressure equalizing groove is substantially equal to the inner diameter of the through hole formed in the partition plate.
3. The hermetic rotary compressor according to claim 2,
the difference between the outer diameter of the pressure equalizing groove and the diameter of the through hole is within + -0.3% with the diameter of the through hole as a denominator.
4. The hermetic rotary compressor according to any one of claims 1 to 3,
the inner diameter of the pressure equalizing groove is larger than the outer diameter of the rotating shaft.
5. The hermetic rotary compressor according to claim 4,
and connected to a refrigeration cycle using R32 as a refrigerant as a working fluid.
6. A hermetic rotary compressor is characterized by comprising:
a plurality of rotary compression units;
a rotating shaft;
a main bearing;
a secondary bearing; and
the space plate is arranged on the upper surface of the base plate,
the rotary compression unit includes a cylinder having a cylinder chamber and a roller accommodated in the cylinder chamber,
the rotating shaft is provided with an eccentric part,
the roller is embedded in the eccentric part,
the main bearing and the auxiliary bearing are respectively provided with a discharge valve device,
an annular groove is formed in the end surface of the main bearing and the sub-bearing on the cylinder side,
a pressure equalizing groove is provided on at least one of both end surfaces of the partition plate which is in sliding contact with the end surface of the roller,
the pressure unevenness of the upper and lower end surfaces of the roller due to the through-holes formed in the partition plate is eliminated by the pressure equalizing grooves.
7. The hermetic rotary compressor according to claim 6,
when the pressure equalizing groove and the discharge port of the discharge valve device are projected to a plane orthogonal to the rotation axis direction, the pressure equalizing groove and the outer edge of the discharge port overlap.
8. The hermetic rotary compressor according to claim 7,
the volume of the pressure equalizing groove is 5% or less of the volume of the discharge port portion.
9. A hermetic rotary compressor is characterized by comprising:
a plurality of rotary compression units;
a rotating shaft;
a main bearing;
a secondary bearing; and
the space plate is arranged on the upper surface of the base plate,
the rotary compression unit includes a cylinder having a cylinder chamber and a roller accommodated in the cylinder chamber,
the rotating shaft is provided with an eccentric part,
the roller is embedded in the eccentric part,
the main bearing and the auxiliary bearing are respectively provided with a discharge valve device,
an annular groove is formed in the end surface of the main bearing and the sub-bearing on the cylinder side,
pressure equalizing grooves are provided in both end surfaces of the main bearing and the sub bearing which are in sliding contact with the end surfaces of the rollers and in both end surfaces of the partition plate which is in sliding contact with the end surfaces of the rollers,
the pressure unevenness of the upper and lower end surfaces of the roller due to the through-holes formed in the partition plate is eliminated by the pressure equalizing grooves.
10. The hermetic rotary compressor according to any one of claims 1 to 3 and 6 to 9,
and connected to a refrigeration cycle using R32 as a refrigerant as a working fluid.
11. A refrigerating and air-conditioning apparatus is characterized in that,
the disclosed device is provided with: the hermetic rotary compressor according to any one of claims 1 to 10, a condenser, an expansion valve, and an evaporator, which are connected by refrigerant pipes.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-252858 | 2016-12-27 | ||
| JP2016252858A JP6568841B2 (en) | 2016-12-27 | 2016-12-27 | Hermetic rotary compressor and refrigeration air conditioner |
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| Publication Number | Publication Date |
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| CN108240332A CN108240332A (en) | 2018-07-03 |
| CN108240332B true CN108240332B (en) | 2020-02-14 |
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| CN201711192662.3A Active CN108240332B (en) | 2016-12-27 | 2017-11-24 | Closed rotary compressor and refrigerating air conditioner |
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| JP (1) | JP6568841B2 (en) |
| CN (1) | CN108240332B (en) |
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| EP3896285A4 (en) * | 2018-12-12 | 2022-08-03 | Toshiba Carrier Corporation | Rotary compressor and refrigeration cycle device |
| JP7170547B2 (en) * | 2019-01-21 | 2022-11-14 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle equipment |
| WO2021079477A1 (en) * | 2019-10-24 | 2021-04-29 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
| JP7470567B2 (en) | 2019-10-24 | 2024-04-18 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
Citations (4)
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|---|---|---|---|---|
| JP2011117309A (en) * | 2009-11-30 | 2011-06-16 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
| CN103511253A (en) * | 2012-11-14 | 2014-01-15 | 广东美芝制冷设备有限公司 | Rotary compressor and multiple-cylinder rotary compressor |
| CN104838145A (en) * | 2013-03-26 | 2015-08-12 | 东芝开利株式会社 | Multiple-cylinder rotary compressor and refrigeration cycle device |
| CN205036575U (en) * | 2015-09-17 | 2016-02-17 | 广东美芝制冷设备有限公司 | Multi -cylinder rotary compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04143483A (en) * | 1990-10-05 | 1992-05-18 | Daikin Ind Ltd | Compressor with rolling piston |
| KR20050011523A (en) * | 2003-07-23 | 2005-01-29 | 삼성전자주식회사 | Variable capacity rotary compressor |
| JP2015049006A (en) * | 2013-09-03 | 2015-03-16 | ダイキン工業株式会社 | Refrigeration device |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011117309A (en) * | 2009-11-30 | 2011-06-16 | Toshiba Carrier Corp | Rotary compressor and refrigerating cycle device |
| CN103511253A (en) * | 2012-11-14 | 2014-01-15 | 广东美芝制冷设备有限公司 | Rotary compressor and multiple-cylinder rotary compressor |
| CN104838145A (en) * | 2013-03-26 | 2015-08-12 | 东芝开利株式会社 | Multiple-cylinder rotary compressor and refrigeration cycle device |
| CN205036575U (en) * | 2015-09-17 | 2016-02-17 | 广东美芝制冷设备有限公司 | Multi -cylinder rotary compressor |
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| CN108240332A (en) | 2018-07-03 |
| JP6568841B2 (en) | 2019-08-28 |
| JP2018105243A (en) | 2018-07-05 |
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