EP1975413A1 - Multi stage rotary compressor - Google Patents
Multi stage rotary compressor Download PDFInfo
- Publication number
- EP1975413A1 EP1975413A1 EP08251003A EP08251003A EP1975413A1 EP 1975413 A1 EP1975413 A1 EP 1975413A1 EP 08251003 A EP08251003 A EP 08251003A EP 08251003 A EP08251003 A EP 08251003A EP 1975413 A1 EP1975413 A1 EP 1975413A1
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- EP
- European Patent Office
- Prior art keywords
- compressing section
- stage
- low
- stage compressing
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
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- 230000006835 compression Effects 0.000 claims abstract description 28
- 238000007906 compression Methods 0.000 claims abstract description 28
- 230000004323 axial length Effects 0.000 claims abstract description 13
- 239000003507 refrigerant Substances 0.000 claims description 33
- 238000005192 partition Methods 0.000 claims description 4
- 230000003247 decreasing effect Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 4
- 230000010349 pulsation Effects 0.000 description 4
- 241000237983 Trochidae Species 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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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
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- 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
-
- 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
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
-
- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/601—Shaft flexion
Definitions
- the present invention relates to a rotary compressor having two-stage compressing sections including a low-stage compressing section and a high-stage compressing section. More particularly, it relates to a technique for preventing a deflection occurring on a shaft connecting a motor and the compressing section to each other to enhance the reliability.
- a compressing section is arranged in the lower part of a closed vessel in which lubricating oil accumulates.
- a two-stage compression rotary compressor in order to make better the balance of compressive load torques produced in two compressing sections and the balance of centrifugal forces acting on the off-center parts corresponding to the two compressing sections, that is, turning pistons and the off-center parts of a shaft engaging with the pistons, the compression phases of a low-stage compressing section and a high-stage compressing section are shifted through 180 degrees.
- the volume of the high-stage compressing section must be smaller than the volume of the low-stage compressing section.
- the thickness of compression chamber that is, the thickness of a cylinder is decreased
- the turning radius of the piston is decreased.
- the low-stage compressing section is arranged above the high-stage compressing section, there arises a problem described below.
- the oil level of lubricating oil lowers from the compressing section arranged on the upper side in the closed vessel, and the compressing section on the upper side is exposed to refrigerant gas. Therefore, the refrigerant leaks into a suction chamber and the compression chamber passing through a gap between a vane and a vane groove, whereby a leakage loss is created.
- the low-stage compressing section is arranged on the upper side, since the interior of closed vessel has the discharge pressure of the high-stage compressing section, the difference in pressure between the suction chamber and the compression chamber is large as compared with the case where the high-stage compressing section is arranged on the upper side, so that the quantity of refrigerant leaking into the suction chamber and the compression chamber through the gap increases, which presents a problem of further decreased efficiency of compressor.
- an object of the present invention is to provide a rotary compressor in which the mass of a balancer can be decreased, and thereby the deflection of a shaft is reduced, so that the seizure in bearing parts and the contact of a rotor with a stator can be prevented.
- a rotary compressor having a two-stage compressing section including a low-stage compressing section and a high-stage compressing section provided in a closed shell, and a motor for driving the two-stage compressing section, the high-stage compressing section being arranged on the motor side is characterized in that when the axial length of the off-center part of shaft corresponding to the low-stage compressing section, that is, a low-stage side crankshaft, is taken as L1, and the axial length of the off-center part of shaft corresponding to the high-stage compressing section, that is, a high-stage side crankshaft, is taken as L2, L2 is longer than L1.
- the mass of a balancer attached to a rotor can be made small by making the axial length of the high-stage side crankshaft longer than that of the low-stage side crankshaft. Thereby, the deflection of the whole of the shaft is reduced, so that seizure caused by a local excessive load of a bearing part and the contact of the rotor with a stator can be prevented.
- the rotary compressor is characterized in that the rotational speed of the compressing section is variable.
- the rotational speed is variable, when the rotational speed is high, the centrifugal forces acting on an upper balancer and a lower balancer increase, by which the deflection of the shaft is increased, and therefore the effect of the present invention is further increased.
- a rotary compressor 1 includes a cylindrical closed vessel 2 arranged in the vertical direction, a motor 4 provided in an upper part in the closed vessel 2, and a compressing section 3 in a lower part therein.
- the closed vessel 2 consists of a cylindrical main shell 21, a dome-shaped top shell 22 that closes the upper end part of the main shell 21, and a dome-shaped bottom shell 23 that closes the lower end part of the main shell 21.
- the top shell 22 and the bottom shell 23 are fixed to the main shell 21 by welding.
- the top shell 22 is provided with a refrigerant discharge pipe 24 for discharging the refrigerant having been discharged into the closed vessel 2 from the compressing section 3 to the outside of the closed vessel 2.
- a stator 41 of the motor 4 is shrinkage fitted to the main shell 21.
- a rotor 42 of the motor 4 is shrinkage fitted onto a shaft 7 mechanically connecting the motor 4 to the compressing section 3.
- an upper balancer 43 and a lower balancer 44 are attached, respectively, to balance the centrifugal forces of the whole of rotating parts.
- the compressing section 3 is provided with a high-stage compressing section 32 in the upper part thereof and a low-stage compressing section 31 in the lower part thereof.
- the discharge side of the low-stage compressing section 31 and the suction side of the high-stage compressing section 32 are connected to each other by an intermediate connection pipe 26 on the outside of the closed vessel 2, by which a two-stage compressing section is formed.
- FIG. 2 shows the transverse cross section of the low-stage compressing section 31 shown in FIG. 1 .
- the configuration of the high-stage compressing section 32 is the same as that of the low-stage compressing section 31 except that the pistons are 180° out-of-phase.
- Each of the compressing sections 31 and 32 has a cylinder 200, 400 and a cylindrical piston 220, 420 accommodated in a cylindrical cylinder bore 200a, 400a formed on the inside of the cylinder 200, 400. Between the internal wall of the cylinder bore 200a, 400a and the outer peripheral surface of the piston 220, 420, a working space for refrigerant is formed.
- the cylinder 200, 400 is provided with a cylinder groove 200b, 400b directed from the cylinder bore 200a, 400a toward the outer periphery direction, and has a flat plate shaped vane 230, 430 in the cylinder groove 200b, 400b.
- a spring 240, 440 is provided between the vane 230, 430 and the internal wall of the closed vessel 2.
- the tip end of the vane 230, 430 is brought into sliding contact with the outer wall of the piston 220, 420, by which the working space is divided into a suction chamber V1, V2 and a compression chamber C1, C2.
- each of the cylinder 200, the piston 220, and the vane 230 on the high-stage side has a smaller thickness in the axial direction than each of the cylinder 400, the piston 420, and the vane 430 on the low-stage side.
- the compressor 1 has a main frame 100 above the high-stage side cylinder 200, an intermediate partition plate 300 between the high-stage side cylinder 200 and the low-stage side cylinder 400, and a sub-frame 500 below the low-stage side cylinder 400, and the upside and the downside of each of the two working spaces are closed by the main frame 100, the intermediate partition plate 300, and the sub-frame 500, whereby each of the two working spaces is formed into a closed space.
- a high-stage side discharge muffler cover 130 is provided above the main frame 100, and a high-stage side discharge muffler chamber M2 for reducing the pressure pulsation of discharged refrigerant is formed.
- a low-stage side discharge muffler cover 510 is provided below the sub-frame 500, and a low-stage side discharge muffler chamber M1 for reducing the pressure pulsation of discharged refrigerant is formed.
- the high-stage side discharge muffler cover 130, the main frame 100, the high-stage side cylinder 200, the intermediate partition plate 300, the low-stage side cylinder 400, the sub-frame 500, and the low-stage side discharge muffler cover 510 are fixed integrally with bolts (not shown), and further the outer peripheral part of the main frame 100 is fixed to the main shell 21 by spot welding.
- the main frame 100 and the sub-frame 500 have bearing parts 110 and 502, respectively, so that the shaft 7 is fitted in the bearing parts 110 and 502 so as to be rotatably supported.
- the shaft 7 has two crankshafts 72 and 73 that are off-centered in the 180 different direction.
- One crankshaft 72 engages with the piston 220 of the high-stage compressing section 32, and the other crankshaft 73 engages with the piston 420 of the low-stage compressing section 31.
- the pistons 220 and 420 turn while slidingly contacting with the inside walls of the respective cylinder bores 200a and 400a, and following this turning motion of the pistons 220 and 420, the vanes 230 and 430 reciprocate, by which the volumes of the suction chambers V1 and V2 and the compression chambers C1 and C2 are changed continuously.
- the compressing section 3 repeats the suction and compression of refrigerant.
- the suction chamber V1 of the low-stage compressing section 31 is connected to a refrigerant suction pipe 64 via a low-stage side suction hole 410 provided in the cylinder 400.
- the compression chamber C1 of the low-stage compressing section 31 is connected to the intermediate connection pipe 26 via a low-stage side discharge hole 520 provided in the sub-frame 500 and the low-stage side discharge muffler chamber M1.
- the low-stage side discharge hole 520 is provided with a check valve 540.
- the refrigerant suction pipe 64 is connected to the low-stage side suction hole 410 via a low-stage side suction connection pipe 411, and the intermediate connection pipe 26 is connected to the low-stage side discharge muffler chamber M1 via an intermediate discharge connection pipe 521.
- the suction chamber V2 of the high-stage compressing section 32 is connected to the intermediate connection pipe 26 via a high-stage side suction hole 210 provided in the cylinder 200.
- the compression chamber C2 of the high-stage compressing section 32 is open to the interior of the closed vessel 2 via a high-stage side discharge hole 120 provided in the main frame 100 and the high-stage side discharge muffler chamber M2.
- the high-stage side discharge hole 120 is provided with a check valve 140.
- the intermediate connection pipe 26 is connected to the high-stage side suction hole 210 via an intermediate suction connection pipe 211.
- an accumulator 6 consisting of an independent closed vessel 61 is provided.
- a refrigerant return pipe 62 is provided, the refrigerant return pipe 62 being connected to a heat pump system, not shown.
- the refrigerant suction pipe 64 one end having an L shape of which is extended to the upper part in the accumulator 6 and the other end of which is connected to the suction chamber V1 of the low-stage compressing section 31 from the side surface of the compressor 1.
- the low-stage side suction chamber V1 comes to a position isolated from the low-stage side suction hole 410, and is turned to the low-stage side compression chamber C1 as it is, by which the refrigerant is compressed.
- the check valve 540 When the pressure of the compressed refrigerant reaches the pressure in the low-stage side discharge muffler chamber M1 on the outside of the check valve 540 provided in the low-stage side discharge hole 520, that is, an intermediate pressure, the check valve 540 is opened, by which the compressed refrigerant is discharged into the low-stage side discharge muffler chamber M1.
- the refrigerant After the pressure pulsation of refrigerant, which may cause noise, has been reduced in the low-stage side discharge muffler chamber M1, the refrigerant is guided into the suction chamber V2 of the high-stage compressing section 32 through the intermediate connection pipe 26.
- the refrigerant guided into the suction chamber V2 of the high-stage compressing section 32 is sucked, compressed, and discharged in the high-stage compressing section 32 on the same principle as that of the low-stage compressing section 31. After the pressure pulsation of refrigerant has been reduced in the high-stage side discharge muffler chamber M2, the refrigerant is discharged into the closed vessel 2.
- the refrigerant is further guided to a portion above the motor 4 after passing through a core notch (not shown) in the stator 41 of the motor 4 and a gap between a core and a coil, and is discharged to the system side through the discharge pipe 24.
- FIG. 3 is a schematic view extractingly showing the rotating parts in the compressor.
- Equation (2) To balance moments that tend to tilt the whole of shaft, Equation (2) is obtained from the moment around the application point of F3.
- F ⁇ 1 ⁇ Lx - Ly F ⁇ 2 ⁇ Ly + F ⁇ 4 ⁇ Lz F3 and F4, that is, the mass of the upper balancer 43 of the rotor 42 and the mass of the lower balancer 44 thereof are determined so as to satisfy Equation (2).
- the upper balancer 43 of the rotor 42 can be made smaller as the mass of the low-stage side crankshaft 73 is decreased or the mass of the high-stage side crankshaft 72 is increased.
- FIG. 4 is a schematic view extractingly showing the shaft 7 and the bearing part 110 supporting the shaft 7.
- the shaft 7 deforms exceeding the gap between the shaft 7 and the bearing part 110, and comes locally into contact with the bearing part 110 at the upper or lower part of the bearing part 110, which may cause seizure.
- the axial length of the high-stage side crankshaft 72 is made longer than the axial length of the low-stage side crankshaft 73.
- the upper balancer 43 of the rotor 42 can be made small, so that the deflection of the whole of the shaft 7 is reduced, whereby seizure caused by a local excessive load of the bearing part 110 and the contact of the rotor 42 with the stator 41 can be prevented.
- the compression ratio ⁇ 2 of the high-stage compressing section 32 is high necessarily.
- the load torque of the high-stage compressing section 32 is higher than that of the low-stage compressing section 31.
- the length of crankshaft not shorter than a predetermined length is necessary.
- the increase in length of crankshaft achieved than necessary is unfavorable because it may cause an increase in slide loss in a crank part.
- the axial length L2 of the high-stage side crankshaft is made longer than the axial length L1 of the low-stage side crankshaft (L2 > L1).
- the rotary compressor 1 configured so that in the compressor provided with the two-stage compression type compressing section having the low-stage compressing section 31 and the high-stage compressing section 32, the working space volume of the high-stage compressing section 32 is made smaller than that of the low-stage compressing section 31 by making the axial length of the high-stage compressing section 32 shorter than that of the low-stage compressing section 31 has been shown typically as a preferred mode.
- the configuration of the rotary compressor 1 may be such that the working space volume of the high-stage compressing section 32 is made smaller by making the axial lengths of the low-stage compressing section 31 and the high-stage compressing section 32 equal to each other and by making the turning radius of the high-stage side piston 220 smaller than that of the low-stage side piston 420.
- the rotary compressor 1 may be a two-stage compression rotary compressor configured so that a gas injection cycle is used as the refrigerating cycle, and an injection refrigerant is allowed to flow into an intermediate compressing section between the low-stage compressing section 31 and the high-stage compressing section 32.
- the compressing mechanism of the compressing section 3 is not limited to the compressing mechanism shown in this embodiment if the compressor is configured so that the change in volumes of the suction chamber V1, V2 and the compression chamber C1, C2 caused by the turning motion of the piston 220, 420 imparted by the crankshaft 72, 73 is utilized.
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Abstract
Description
- The present invention relates to a rotary compressor having two-stage compressing sections including a low-stage compressing section and a high-stage compressing section. More particularly, it relates to a technique for preventing a deflection occurring on a shaft connecting a motor and the compressing section to each other to enhance the reliability.
- Generally, in a rotary compressor, in order to reduce a loss of refrigerant caused by the leakage by sealing the gap of a compression chamber and to lubricate sliding portions such as bearings, a compressing section is arranged in the lower part of a closed vessel in which lubricating oil accumulates.
- Also, in a two-stage compression rotary compressor, in order to make better the balance of compressive load torques produced in two compressing sections and the balance of centrifugal forces acting on the off-center parts corresponding to the two compressing sections, that is, turning pistons and the off-center parts of a shaft engaging with the pistons, the compression phases of a low-stage compressing section and a high-stage compressing section are shifted through 180 degrees.
- By the centrifugal forces acting on the two off-center parts of the shaft and the two turning pistons, a moment that tends to tilt the whole of the shaft is produced. Therefore, a balancer is attached to above and below a rotor of a motor to cancel the moment that tends to tilt the whole of the shaft.
- In the two-stage compression rotary compressor, in terms of the compression characteristics thereof, the volume of the high-stage compressing section must be smaller than the volume of the low-stage compressing section. As means for decreasing the volume of compression chamber, there are available a method in which the thickness of compression chamber, that is, the thickness of a cylinder is decreased and a method in which the turning radius of the piston is decreased. In both of these methods, the centrifugal forces acting on the off-center parts of the shaft and the pistons are smaller in the high-stage compressing section having a smaller volume than in the low-stage compressing section having a larger volume.
- Therefore, as described in Japanese Patent Application Publication No.
H11-230073 - However, in the case where the low-stage compressing section is arranged above the high-stage compressing section, there arises a problem described below. Depending on the operation pressure condition and the rotational speed condition of the compressor, the oil level of lubricating oil lowers from the compressing section arranged on the upper side in the closed vessel, and the compressing section on the upper side is exposed to refrigerant gas. Therefore, the refrigerant leaks into a suction chamber and the compression chamber passing through a gap between a vane and a vane groove, whereby a leakage loss is created.
- If the low-stage compressing section is arranged on the upper side, since the interior of closed vessel has the discharge pressure of the high-stage compressing section, the difference in pressure between the suction chamber and the compression chamber is large as compared with the case where the high-stage compressing section is arranged on the upper side, so that the quantity of refrigerant leaking into the suction chamber and the compression chamber through the gap increases, which presents a problem of further decreased efficiency of compressor.
- Accordingly, an object of the present invention is to provide a rotary compressor in which the mass of a balancer can be decreased, and thereby the deflection of a shaft is reduced, so that the seizure in bearing parts and the contact of a rotor with a stator can be prevented.
- To achieve the above object, the present invention has some features described below. A rotary compressor having a two-stage compressing section including a low-stage compressing section and a high-stage compressing section provided in a closed shell, and a motor for driving the two-stage compressing section, the high-stage compressing section being arranged on the motor side, is characterized in that when the axial length of the off-center part of shaft corresponding to the low-stage compressing section, that is, a low-stage side crankshaft, is taken as L1, and the axial length of the off-center part of shaft corresponding to the high-stage compressing section, that is, a high-stage side crankshaft, is taken as L2, L2 is longer than L1.
- According to this configuration, the mass of a balancer attached to a rotor can be made small by making the axial length of the high-stage side crankshaft longer than that of the low-stage side crankshaft. Thereby, the deflection of the whole of the shaft is reduced, so that seizure caused by a local excessive load of a bearing part and the contact of the rotor with a stator can be prevented.
- As a preferable mode, the rotary compressor is characterized in that the rotational speed of the compressing section is variable. According to this configuration, in the rotary compressor in which the rotational speed is variable, when the rotational speed is high, the centrifugal forces acting on an upper balancer and a lower balancer increase, by which the deflection of the shaft is increased, and therefore the effect of the present invention is further increased.
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FIG. 1 is a longitudinal sectional view of a rotary compressor in accordance with one embodiment of the present invention; -
FIG. 2 is a transverse sectional view of a compressing section of the rotary compressor shown inFIG. 1 ; -
FIG. 3 is a schematic view showing rotating parts of the rotary compressor shown inFIG. 1 and centrifugal forces acting thereon; and -
FIG. 4 is a schematic view showing a deflected state of a shaft formed by centrifugal forces of the rotary compressor shown inFIG. 1 . - An embodiment of the present invention is explained with reference to
FIG. 1 . The present invention is not limited to this embodiment. A rotary compressor 1 includes a cylindrical closedvessel 2 arranged in the vertical direction, amotor 4 provided in an upper part in the closedvessel 2, and acompressing section 3 in a lower part therein. - The closed
vessel 2 consists of a cylindricalmain shell 21, a dome-shapedtop shell 22 that closes the upper end part of themain shell 21, and a dome-shaped bottom shell 23 that closes the lower end part of themain shell 21. Thetop shell 22 and thebottom shell 23 are fixed to themain shell 21 by welding. - The
top shell 22 is provided with arefrigerant discharge pipe 24 for discharging the refrigerant having been discharged into the closedvessel 2 from the compressingsection 3 to the outside of the closedvessel 2. - A
stator 41 of themotor 4 is shrinkage fitted to themain shell 21. Arotor 42 of themotor 4 is shrinkage fitted onto ashaft 7 mechanically connecting themotor 4 to the compressingsection 3. Above and below therotor 42, anupper balancer 43 and alower balancer 44 are attached, respectively, to balance the centrifugal forces of the whole of rotating parts. - The compressing
section 3 is provided with a high-stage compressingsection 32 in the upper part thereof and a low-stage compressingsection 31 in the lower part thereof. The discharge side of the low-stage compressingsection 31 and the suction side of the high-stage compressingsection 32 are connected to each other by anintermediate connection pipe 26 on the outside of the closedvessel 2, by which a two-stage compressing section is formed. - Next, the configuration of each section of the compressing
section 3 is explained with reference toFIG. 2. FIG. 2 shows the transverse cross section of the low-stage compressingsection 31 shown inFIG. 1 . The configuration of the high-stage compressing section 32 is the same as that of the low-stage compressingsection 31 except that the pistons are 180° out-of-phase. - Each of the
compressing sections cylinder cylindrical piston cylindrical cylinder bore cylinder piston - The
cylinder cylinder groove cylinder bore vane cylinder groove - Between the
vane vessel 2, aspring spring vane piston - In order to make the working space volume of the high-stage compressing
section 32 smaller than that of low-stage compressingsection 31, each of thecylinder 200, thepiston 220, and thevane 230 on the high-stage side has a smaller thickness in the axial direction than each of thecylinder 400, thepiston 420, and thevane 430 on the low-stage side. - Next, referring again to
FIG. 1 , the whole of the compressor 1 is explained. The compressor 1 has amain frame 100 above the high-stage side cylinder 200, anintermediate partition plate 300 between the high-stage side cylinder 200 and the low-stage side cylinder 400, and asub-frame 500 below the low-stage side cylinder 400, and the upside and the downside of each of the two working spaces are closed by themain frame 100, theintermediate partition plate 300, and thesub-frame 500, whereby each of the two working spaces is formed into a closed space. - Above the
main frame 100, a high-stage sidedischarge muffler cover 130 is provided, and a high-stage side discharge muffler chamber M2 for reducing the pressure pulsation of discharged refrigerant is formed. Below thesub-frame 500, a low-stage sidedischarge muffler cover 510 is provided, and a low-stage side discharge muffler chamber M1 for reducing the pressure pulsation of discharged refrigerant is formed. - The high-stage side
discharge muffler cover 130, themain frame 100, the high-stage side cylinder 200, theintermediate partition plate 300, the low-stage side cylinder 400, thesub-frame 500, and the low-stage sidedischarge muffler cover 510 are fixed integrally with bolts (not shown), and further the outer peripheral part of themain frame 100 is fixed to themain shell 21 by spot welding. - The
main frame 100 and thesub-frame 500 have bearingparts shaft 7 is fitted in the bearingparts - The
shaft 7 has twocrankshafts crankshaft 72 engages with thepiston 220 of the high-stage compressingsection 32, and theother crankshaft 73 engages with thepiston 420 of the low-stage compressing section 31. - Along with the rotation of the
shaft 7, thepistons pistons vanes section 3 repeats the suction and compression of refrigerant. - The suction chamber V1 of the low-stage compressing
section 31 is connected to arefrigerant suction pipe 64 via a low-stageside suction hole 410 provided in thecylinder 400. The compression chamber C1 of the low-stage compressingsection 31 is connected to theintermediate connection pipe 26 via a low-stageside discharge hole 520 provided in thesub-frame 500 and the low-stage side discharge muffler chamber M1. - More specifically, the low-stage
side discharge hole 520 is provided with acheck valve 540. Also, therefrigerant suction pipe 64 is connected to the low-stageside suction hole 410 via a low-stage sidesuction connection pipe 411, and theintermediate connection pipe 26 is connected to the low-stage side discharge muffler chamber M1 via an intermediatedischarge connection pipe 521. - The suction chamber V2 of the high-
stage compressing section 32 is connected to theintermediate connection pipe 26 via a high-stageside suction hole 210 provided in thecylinder 200. The compression chamber C2 of the high-stage compressing section 32 is open to the interior of theclosed vessel 2 via a high-stageside discharge hole 120 provided in themain frame 100 and the high-stage side discharge muffler chamber M2. - More specifically, the high-stage
side discharge hole 120 is provided with acheck valve 140. Also, theintermediate connection pipe 26 is connected to the high-stageside suction hole 210 via an intermediatesuction connection pipe 211. - At the side of the body of the compressor 1, an
accumulator 6 consisting of an independentclosed vessel 61 is provided. Above theaccumulator 6, arefrigerant return pipe 62 is provided, therefrigerant return pipe 62 being connected to a heat pump system, not shown. Below theaccumulator 6, there is provided therefrigerant suction pipe 64 one end having an L shape of which is extended to the upper part in theaccumulator 6 and the other end of which is connected to the suction chamber V1 of the low-stage compressing section 31 from the side surface of the compressor 1. - Next, the flow of refrigerant in the above-described configuration is explained with reference to
FIGS. 1 and2 . The refrigerant flowing from the heat pump system side into theaccumulator 6 passing through therefrigerant return pipe 62 is separated so that a liquid refrigerant lies in the lower part of theaccumulator 6 and a gas refrigerant lies in the upper part thereof. - When the low-
stage side piston 420 is turned to increase the volume of the low-stage side suction chamber V1, the gas refrigerant in theaccumulator 6 is sucked into the low-stage side suction chamber V1 of the compressor body 1 through therefrigerant suction pipe 64. - After one turn of the
piston 420, the low-stage side suction chamber V1 comes to a position isolated from the low-stageside suction hole 410, and is turned to the low-stage side compression chamber C1 as it is, by which the refrigerant is compressed. - When the pressure of the compressed refrigerant reaches the pressure in the low-stage side discharge muffler chamber M1 on the outside of the
check valve 540 provided in the low-stageside discharge hole 520, that is, an intermediate pressure, thecheck valve 540 is opened, by which the compressed refrigerant is discharged into the low-stage side discharge muffler chamber M1. - After the pressure pulsation of refrigerant, which may cause noise, has been reduced in the low-stage side discharge muffler chamber M1, the refrigerant is guided into the suction chamber V2 of the high-
stage compressing section 32 through theintermediate connection pipe 26. - The refrigerant guided into the suction chamber V2 of the high-
stage compressing section 32 is sucked, compressed, and discharged in the high-stage compressing section 32 on the same principle as that of the low-stage compressing section 31. After the pressure pulsation of refrigerant has been reduced in the high-stage side discharge muffler chamber M2, the refrigerant is discharged into theclosed vessel 2. - The refrigerant is further guided to a portion above the
motor 4 after passing through a core notch (not shown) in thestator 41 of themotor 4 and a gap between a core and a coil, and is discharged to the system side through thedischarge pipe 24. - Next, the centrifugal forces acting on the rotating parts in the compressor configured as described above are explained with reference to
FIG. 3. FIG. 3 is a schematic view extractingly showing the rotating parts in the compressor. - As the centrifugal forces acting on the rotating parts, there are generated a centrifugal force (F1) acting on the low-
stage side crankshaft 73 and the low-stage side piston 420 engaging therewith, a centrifugal force (F2) acting on the high-stage side crankshaft 72 and the high-stage side piston 220 engaging therewith, a centrifugal force (F4) acting on theupper balancer 43 attached to above therotor 42, and a centrifugal force (F3) acting on thelower balancer 44 attached to below therotor 42. To balance these centrifugal forces in the horizontal direction, the following equation holds. -
-
- From Equation (3), it can be seen that F4 can be decreased as F1 is decreased or F2 is increased.
- That is to say, the
upper balancer 43 of therotor 42 can be made smaller as the mass of the low-stage side crankshaft 73 is decreased or the mass of the high-stage side crankshaft 72 is increased. - Hereunder, the state in which the
shaft 7 is deflected by the centrifugal forces acting on theshaft 7 is explained with reference toFIG. 4. FIG. 4 is a schematic view extractingly showing theshaft 7 and thebearing part 110 supporting theshaft 7. - If the deflection of the whole of the
shaft 7 increases, especially in thebearing part 110 of themain frame 100, theshaft 7 deforms exceeding the gap between theshaft 7 and thebearing part 110, and comes locally into contact with thebearing part 110 at the upper or lower part of thebearing part 110, which may cause seizure. - To solve this problem, the axial length of the high-
stage side crankshaft 72 is made longer than the axial length of the low-stage side crankshaft 73. Thereby, theupper balancer 43 of therotor 42 can be made small, so that the deflection of the whole of theshaft 7 is reduced, whereby seizure caused by a local excessive load of thebearing part 110 and the contact of therotor 42 with thestator 41 can be prevented. - On the other hand, the effect described below can be achieved. In the compressor used for a heat pump for an air conditioner, a water heater, and the like, the suction pressure Ps and the discharge pressure Pd of the compressor change mainly depending on the outside air temperature condition. This fact means that the compression ratio φ (= Pd/Ps) as the whole of compressor is not constant, so that it is necessary to respond to a wide range.
- Taking the suction volume of the low-
stage compressing section 31 as V1, the suction volume of the high-stage compressing section 32 as V2, and the specific heat of compressed gas as κ, in the case where losses in the compressingsections stage compressing section 31 is expressed as φ 1 = (V1/V2)κ. That is to say, the compression ratio φ 1 of the low-stage compressing section 31 is determined by the suction volumes of the two cylinders without depending on the outside air temperature condition. - Therefore, under the condition in which the total compression ratio φ is high, for example, in a cooling operation under a condition in which the outside air temperature is especially high or in a heating operation under a condition in which the outside air temperature is especially low, the
compression ratio φ 2 of the high-stage compressing section 32 is high necessarily. - That is to say, under such a condition, the load torque of the high-
stage compressing section 32 is higher than that of the low-stage compressing section 31. To support this load, the length of crankshaft not shorter than a predetermined length is necessary. However, the increase in length of crankshaft achieved than necessary is unfavorable because it may cause an increase in slide loss in a crank part. - Therefore, as described above, the axial length L2 of the high-stage side crankshaft is made longer than the axial length L1 of the low-stage side crankshaft (L2 > L1). Thereby, both of the improvement in reliability in the crankshaft bearing parts and the improvement in efficiency due to the reduction in slide loss can be achieved.
- In this embodiment, the rotary compressor 1 configured so that in the compressor provided with the two-stage compression type compressing section having the low-
stage compressing section 31 and the high-stage compressing section 32, the working space volume of the high-stage compressing section 32 is made smaller than that of the low-stage compressing section 31 by making the axial length of the high-stage compressing section 32 shorter than that of the low-stage compressing section 31 has been shown typically as a preferred mode. However the configuration of the rotary compressor 1 may be such that the working space volume of the high-stage compressing section 32 is made smaller by making the axial lengths of the low-stage compressing section 31 and the high-stage compressing section 32 equal to each other and by making the turning radius of the high-stage side piston 220 smaller than that of the low-stage side piston 420. - Also, the rotary compressor 1 may be a two-stage compression rotary compressor configured so that a gas injection cycle is used as the refrigerating cycle, and an injection refrigerant is allowed to flow into an intermediate compressing section between the low-
stage compressing section 31 and the high-stage compressing section 32. - Also, the compressing mechanism of the
compressing section 3 is not limited to the compressing mechanism shown in this embodiment if the compressor is configured so that the change in volumes of the suction chamber V1, V2 and the compression chamber C1, C2 caused by the turning motion of thepiston crankshaft
Claims (2)
- A rotary compressor comprising:a closed vessel;a low-stage compressing section and a high-stage compressing section provided in the closed vessel;a shaft provided with a low-stage side off-center part and a high-stage side off-center part corresponding to the low-stage compressing section and the high-stage compressing section, respectively;a motor connected mechanically to the shaft to drive the low-stage compressing section and the high-stage compressing section,each of the low-stage compressing section and the high-stage compressing section having a cylinder; a piston turning in the cylinder while engaging with the off-center part of the shaft; and a vane the tip end of which comes into sliding contact with the piston while the vane reciprocates in a vane groove in the cylinder to form a suction chamber and a compression chamber for refrigerant together with the cylinder and the piston, andfurther comprising:an intermediate partition plate held between the low-stage compressing section and the high-stage compressing section to close one end surface of the suction chamber and the compression chamber; anda main frame and a sub-frame each of which is provided with a bearing part for rotatably supporting the shaft and closes one end surface of the suction chamber and the compression chamber, in whichmeans for allowing the discharge side of the low-stage compressing section and the suction side of the high-stage compressing section to communicate with each other is provided, whereby a two-stage compressing section is formed, whereinwhen the axial length of the off-center part of shaft corresponding to the low-stage compressing section is taken as L1, and the axial length of the off-center part of shaft corresponding to the high-stage compressing section is taken as L2, L2 is longer than L 1.
- The rotary compressor according to claim 1, wherein the rotational speed of the compressing section is variable.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007083399A JP2008240667A (en) | 2007-03-28 | 2007-03-28 | Rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1975413A1 true EP1975413A1 (en) | 2008-10-01 |
Family
ID=39537963
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08251003A Withdrawn EP1975413A1 (en) | 2007-03-28 | 2008-03-20 | Multi stage rotary compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20080240954A1 (en) |
EP (1) | EP1975413A1 (en) |
JP (1) | JP2008240667A (en) |
CN (1) | CN101275562A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2339179A3 (en) * | 2009-12-22 | 2011-11-23 | LG Electronics, Inc. | Rotary compressor |
CN102691661A (en) * | 2011-03-23 | 2012-09-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5201045B2 (en) * | 2009-03-24 | 2013-06-05 | 株式会社富士通ゼネラル | 2-stage compression rotary compressor |
KR101528645B1 (en) | 2009-04-09 | 2015-06-15 | 엘지전자 주식회사 | 2-stage rotary compressor |
CN102472280B (en) * | 2009-08-06 | 2014-08-20 | 大金工业株式会社 | Compressor |
KR101981096B1 (en) | 2012-10-12 | 2019-05-22 | 엘지전자 주식회사 | Hemetic compressor |
JP2016114049A (en) * | 2014-12-15 | 2016-06-23 | 三星電子株式会社Samsung Electronics Co.,Ltd. | Rotary compressor |
JP2018009534A (en) * | 2016-07-14 | 2018-01-18 | 株式会社富士通ゼネラル | Rotary Compressor |
JP2018123691A (en) | 2017-01-30 | 2018-08-09 | ダイキン工業株式会社 | Compressor |
CN109026693B (en) * | 2018-08-31 | 2023-10-03 | 珠海格力电器股份有限公司 | Pump body assembly, compressor and air conditioner |
DE102018217018A1 (en) * | 2018-10-04 | 2020-04-09 | Premium Aerotec Gmbh | SEMI-FINISHED PRODUCT AND METHOD FOR PRODUCING A STRUCTURAL COMPONENT |
CN110685911A (en) * | 2019-09-29 | 2020-01-14 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
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JP3389539B2 (en) * | 1999-08-31 | 2003-03-24 | 三洋電機株式会社 | Internal intermediate pressure type two-stage compression type rotary compressor |
TW568996B (en) * | 2001-11-19 | 2004-01-01 | Sanyo Electric Co | Defroster of refrigerant circuit and rotary compressor for refrigerant circuit |
-
2007
- 2007-03-28 JP JP2007083399A patent/JP2008240667A/en active Pending
-
2008
- 2008-03-06 US US12/073,484 patent/US20080240954A1/en not_active Abandoned
- 2008-03-20 EP EP08251003A patent/EP1975413A1/en not_active Withdrawn
- 2008-03-27 CN CNA2008100903440A patent/CN101275562A/en active Pending
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JPS61205390A (en) * | 1985-03-07 | 1986-09-11 | Mitsubishi Electric Corp | Two-cylinder type rotary compressor |
US5242280A (en) * | 1990-11-21 | 1993-09-07 | Matsushita Electric Industrial Co., Ltd. | Rotary type multi-stage compressor with vanes biased by oil pressure |
JPH11230073A (en) | 1998-02-10 | 1999-08-24 | Sanyo Electric Co Ltd | Compressor |
JP2005077039A (en) * | 2003-09-02 | 2005-03-24 | Toshiba Kyaria Kk | Air conditioner |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2339179A3 (en) * | 2009-12-22 | 2011-11-23 | LG Electronics, Inc. | Rotary compressor |
US8967984B2 (en) | 2009-12-22 | 2015-03-03 | Lg Electronics Inc. | Rotary compressor |
CN102691661A (en) * | 2011-03-23 | 2012-09-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
CN102691661B (en) * | 2011-03-23 | 2014-07-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
Also Published As
Publication number | Publication date |
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US20080240954A1 (en) | 2008-10-02 |
CN101275562A (en) | 2008-10-01 |
JP2008240667A (en) | 2008-10-09 |
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