US20070231171A1 - Displacement type compressor - Google Patents
Displacement type compressor Download PDFInfo
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- US20070231171A1 US20070231171A1 US11/627,389 US62738907A US2007231171A1 US 20070231171 A1 US20070231171 A1 US 20070231171A1 US 62738907 A US62738907 A US 62738907A US 2007231171 A1 US2007231171 A1 US 2007231171A1
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- United States
- Prior art keywords
- mechanism section
- compressing mechanism
- motor
- crankshaft
- claw
- Prior art date
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- Abandoned
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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
- 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
- F04C29/0085—Prime movers
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
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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
- 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
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Compressor (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
A displacement type compressor includes a compressing mechanism section for performing a compression, a motor for driving the compressing mechanism section, and a crankshaft adapted to be driven in rotation by the motor to rotate the compressing mechanism section. The motor includes stator cores and having claw-type magnetic poles formed of a magnetic powder and circumferentially arranged in alternately meshed states, and annular coils and wound in a toric shape around the claw-type magnetic poles. Thus, the displacement type compressor is capable of being at a high speed and has a reduced size.
Description
- 1. Field of the Invention
- The present invention relates to a displacement type compressor for treating air, carbon dioxide and another compressible gas, which may be used as an HFC refrigerant or a natural refrigerant, and particularly, to a displacement type compressor which is suitably designed to provide a high output, while being small-sized.
- 2. Description of the Related Art
- A displacement type compressor representative of a scroll compressor, a reciprocal compressor and a rotary compressor is widely utilized in a variety of fields not only as a compressor for a refrigerant air conditioner used for domestic, business, in-vehicle applications or the like, but also as an air supply compressor used for a source of air in a factory, for a fuel cell or the like. A high-energy efficiency is required from the viewpoint of prevention of global warming, and it is desired to reduce the size of the compressor for promoting the reduction in cost.
- It is conventionally known that in order to reduce the size of the compressor, the axial length of a motor for driving a compressing mechanism section is reduced, or a claw-type pole motor (a claw-type magnetic pole motor) having no coil end portion is used to reduce the entire length of the compressor. This is described, for example, in JP-A-2001-280247.
- In the above-described conventional technique, the reduction in size is provided merely by eliminating a coil end portion, and hence, it is not sufficiently considered that the compressor is operated at a high output and at a high speed in a range of larger capacity. For this reason, claw-type magnetic poles must be axially stacked as multiple layers for the purpose of an increase in output, and the increase in output results in the impairment of reduction in size for the original purpose.
- Accordingly, it is an object of the present invention to provide a displacement type compressor which is capable of being rotated at a high output and at a high speed and has a high-energy efficiency and which is small-sized. It is another object of the present invention to ensure that the axial length of, particularly, a displacement type compressor is reduced, and the reliability is enhanced.
- To achieve the above object, according to the present invention, there is provided a displacement type compressor, comprising a compressing mechanism section adapted to perform a compression, and a motor for driving the compressing mechanism section, wherein the motor comprises a stator core in which claw-type magnetic poles formed of a magnetic powder are circumferentially arranged in alternately meshed states, and annular coils wound in a toric shape around the claw-type magnetic poles.
- With the arrangement of the above feature, the motor is constructed using the claw-type magnetic poles formed of the magnetic powder. Therefore, it is possible to provide a displacement type compressor which is capable of being rotated at a higher speed and which has a high-energy efficiency.
- The above and other objects, features and advantages of the invention will become apparent from the following description of the preferred embodiment taken in conjunction with the accompanying drawings.
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FIG. 1 is a sectional view showing the entire compressor according to one embodiment of the present invention; -
FIG. 2 is a sectional view showing a stator core in the embodiment; -
FIG. 3 is a plan view showing a claw-type core portion in the embodiment; -
FIG. 4 is a sectional view showing the claw-type core portion in the embodiment; -
FIG. 5A is a plan view of a rotor in the embodiment; -
FIG. 5B is a plan view of other rotor in the embodiment; -
FIG. 5C is a plan view of other rotor in the embodiment; -
FIG. 6 is a sectional view showing the entire compressor according to another embodiment of the present invention; -
FIG. 7 is a sectional view showing the entire compressor according to a further embodiment of the present invention; -
FIG. 8 is a view showing the entire compressor according to a yet further embodiment of the present invention; and -
FIG. 9 is a sectional view showing the entire compressor according to a yet further embodiment of the present invention. - A displacement type compressor according to an embodiment of the present invention will now be described with reference to
FIGS. 1 to 5 . - The displacement type compressor includes a
compressing mechanism section 1 using a scroll compressing mechanism which is small-sized and capable of providing a high output, and a drive means contained in a closedcontainer 5 for driving anorbiting scroll 3 in orbiting movement. Thecompressing mechanism section 1 comprises afixed scroll 2, theorbiting scroll 3 and aframe 4 as basic elements. Thefixed scroll 2 or theframe 4 is fixed to the closedcontainer 5. - The
fixed scroll 2 includes aspiral wrap 2 a, amirror plate 2 b and adischarge bore 2 c, and is fixed to theframe 4 through a bolt. Thewrap 2 a is mounted on themirror plate 2 b to rise vertically. Theorbiting scroll 3 has aspiral wrap 3 a, amirror plate 3 b and ashaft support portion 3 c. Thewrap 3 a is mounted on themirror plate 3 b to rise vertically. Acompression chamber 7, in which thefixed scroll 2 and theorbiting scroll 3 are meshed with each other, performs a compressing motion, whereby the volume of thecompression chamber 7 is decreased by the orbiting movement of the orbitingscroll 3. - With the orbiting movement of the
orbiting scroll 3, a working fluid is drawn via anintake space 9 into thecompression chamber 7, and the drawn working fluid is discharged through thedischarge bore 2 c into adischarge space 10 via a compression stroke and further discharged from the closedcontainer 5 via adischarge port 11. This causes a space within the closedcontainer 5 to be maintained at a discharge pressure. An over-compression preventing means (not shown) is also mounted in order to prevent an over-compression caused during an operation with a pressure ratio lower than a design pressure ratio. The over-compression preventing means includes a passage permitting the communication between thecompression chamber 7 and thedischarge space 10, and a valve adapted to open the passage when an over-compression is reached. - The drive means for driving the orbiting
scroll 3 in orbiting movement includes amotor 23 comprising astator 21 usingstator cores rotor 22, acrankshaft 24, an Oldham'sring 25 which is a main component for an automatic preventing mechanism for the orbitingscroll 3, theframe 4 and asub frame 12. - The
motor 23 provides a rotating action to thecrankshaft 24. Thecrankshaft 24 includes amain shaft portion 24 a, asub shaft portion 24 b and aneccentric pin portion 24 c. Ashaft support portion 6 disposed on theframe 4 and ashaft support portion 26 disposed on thesub frame 12 provide shaft supports with which themain shaft portion 24 a and thesub shaft portion 24 b of thecrankshaft 24 are rotatably engaged, and theeccentric pin portion 24 c of thecrankshaft 24 is engaged for movement in a rotationally axial direction and for rotation with the orbitingshaft support portion 3 c disposed on the orbitingscroll 3. The shaft supportportions compressing mechanism section 1 opposite from the motor and on the side of the motor opposite from the compressing mechanism section, respectively. It should be noted that in addition to a sliding bearing, a rolling bearing adaptable for service conditions and another shaft support member may be used for each of theshaft support portions - The Oldham's
ring 25 is disposed in a space defined by theorbiting scroll 3 and theframe 4. One of two sets of perpendicular key portions formed on the Oldham'sring 25 slides in akey groove 27 a which is a receiver for the Oldham'sring 25 and formed in theframe 4, and the remaining one set slides in akey groove 27 b formed in a back of the orbitingscroll wrap 2 a. Thus, the orbitingscroll 3 is orbited, without being rotated about its own axis, in a plane perpendicular to an axial direction which is a direction of rising of the scroll wrap. - To fix the
stator 21 within the closedcontainer 5, thestator cores core frame 30, and thecore frame 30 is engaged with thefixed scroll 2. If a mating member with which thecore frame 30 is engaged is thefixed scroll 2, the engagement can be achieved at a high accuracy, but thecore frame 30 may be engaged with a portion of thecompressing mechanism section 1, or the closedcontainer 5. -
FIG. 2 shows one of thestator cores type core portion 31 and a second claw-type core portion 32.Annular coils - A claw-type
magnetic pole 33 is provided in an axially folded state on the claw-type core portion in the form of a magnetic pole surface opposed to therotor 22. Theannular coils magnetic poles 33. In the stator core, two claw-type core portions are arranged circumferentially in a state in which the claw-type magnetic poles provided on the claw-type core portions are alternately meshed together. - Further,
FIG. 3 is a view showing the arrangement of the second claw-type core portion 32, andFIG. 4 shows a section of the second claw-type core portion 32 taken along a line A-A inFIG. 3 . InFIGS. 2 to 4 , two claw-type magnetic poles are present per one claw-type core portion and hence, four claw-type magnetic poles are present on one stator core. Thus, themotor 23 acts as a four-magnetic pole motor. - As shown in
FIG. 1 , in the threestator cores stator cores rotor 22 and the claw-type magnetic pole is reduced, it is feared that the magnetic powder is dropped from each of the claw-type core portions, resulting in a detracted reliability. In order to prevent this, a resinous film is formed on each of the claw-type core portions. A material which may be used for the resinous film includes PPS (polyphenylene sulfide)-based resin which is a thermo plastic engineering plastic having a good heat resistance, and the like. - The
rotor 22 is preferred to be one having a magnet disposed on its surface, because of its low price, but may be any other rotor such as a cage-shaped rotor as shown inFIG. 5A , a rotor as shown inFIG. 5B and having a cage-shaped conductor and a magnet and a rotor as shown inFIG. 5C and having a flux barrier (slit), if a magnetic pole engaged with a claw-type magnetic pole can be formed on the rotor. InFIG. 5 , each of 40 and 41 designates the case-shaped conductor; 42 designates the magnet; and 43 designates the flux barrier. - The
sub frame 12 having theshaft support portion 26 disposed thereon is engaged with thecore frame 30. It should be noted that a mating member with which thesub frame 12 is engaged may be theclosed container 5. Thesub frame 12 is provided with athrust bearing 13 adapted to receive a load when thecrankshaft 24 is moved downwards. When thecrankshaft 24 is moved upwards, the load is received by athrust receiver 18. - To lubricate the
shaft support portions oil supply pump 14 is mounted at a lower portion of thesub frame 12 and rotated by the rotation of thecrankshaft 24 to realize the pumping action. More specifically, a lubricating oil accumulated in a lower space in theclosed container 5 is sucked by theoil supply pump 14 and supplied to the various portions through anoil supply passage 24 d provided in the crankshaft or the like. Theoil supply pump 14 may be a centrifugal pump (not shown) formed on the crankshaft to realize an eccentric rotational motion. The lubricating oil supplied to theshaft support portions compression chamber 7 through acircular seal member 18 disposed on theframe 4 and a small oil supply bore 20. - In order to eliminate an eccentric unbalance caused by the rotation of the
orbiting scroll 3, theeccentric pin portion 24 c of the crankshaft or the like,balance weights compressing mechanism section 1 opposite from the motor and between thecompressing mechanism section 1 and themotor 23, respectively. Thebalance weight 16 between thecompressing mechanism section 1 and themotor 23 is of a shape smaller than inside diameters of thestator 21 and thestator cores stator 21 through thecrankshaft 24. - According to the above-described arrangement, the
motor 23 using the stator cores with the claw-type core portions formed of the magnetic powder being meshed with one another can be reduced in axial length because of having no end coil, as is a conventional claw-type magnetic pole motor; and this motor is capable of being rotated at a high speed and has a high-energy efficiency characteristic and a high-output characteristic. Therefore, the axial length of thecrankshaft 24 can be also reduced by the reduction in size of themotor 23, and hence, the deformation of thecrankshaft 24 can be reduced to suppress the one-sided striking on the shaft support portion, leading to an increase in reliability of the shaft support portion. - In addition, it is possible to provide a reduction in size and an increase in speed of the displacement type compressor, and because the resinous film is applied to each of the claw-
type core portions type core portions - Further, because the claw-
type core portions core frame 30, it is possible to prevent the fracture of the claw-type core portions due to the fitting of the stator core into the closed container, and to eliminate the deformation of the closed container due to the fitting. This means that the components to be engaged with the closed contained can be assembled with a good accuracy. - Furthermore, it is possible to position the
shaft support portion 6 provided on theframe 4 and thestator core 21 at a coaxiality of a high accuracy. - Yet further, the
core frame 30 can be fixed in an engaged manner to thesub frame 12 provided with theshaft support portion 26 and hence, it is possible to position theshaft support portion 6 provided on theframe 4, thestator 21 and the shaft support potion of thesub frame 12 at a coaxiality of a high accuracy. - Moreover, because the axial length of the displacement type compressor can be reduced, the axial length of the
crankshaft 24 can be further reduced; thecompressing mechanism section 1 and themotor 23 can be disposed between the twoshaft support portions crankshaft 24 is rotatably engaged, and the balance weights for eliminating the eccentric unbalance can be disposed on the side of thecompressing mechanism section 1 opposite from the motor and between thecompressing mechanism section 1 and themotor 23, respectively, thereby further reducing the deformation of thecrankshaft 24 during operation at a high speed. Thus, it is possible to provide an increase in reliability during operation at the high speed and to reduce a loss of sliding of the bearing due to the deformation of the crankshaft. - Further, the outside diameter of the balance weight disposed between the
compressing mechanism section 1 and themotor 23 is smaller than the inside diameters of thestator 21 and thestator cores compressing mechanism section 1. The arrangement is such that thecrankshaft 24 is mounted to extend through theorbiting scroll 3 and the fixedscroll 2, and the compressing mechanism section is sandwiched between theshaft support portions - A displacement type compressor according to a second embodiment of the present invention will now be described in detail with reference to
FIG. 6 .FIG. 6 shows the entire structure of a scroll compressor in the second embodiment. The arrangement ofshaft support portions thrust bearing 13, a thrustbearing support portion 51 and an oil supply way are different from those in the first embodiment. - For the shaft support portions for the
crankshaft 24, ashaft support portion 50 is formed on afixed scroll 2. Asub shaft portion 24 e of the crankshaft is rotatably engaged with theshaft support portion 50, and the deformation of thecrankshaft 24 due to the whirling of therotor 22 is influenced at most to a small extent. - The
thrust bearing 13 and athrust bearing 18 for supporting an axial force of thecrankshaft 24 are provided on the thrustbearing support portion 51 and theframe 4, but if thrust bearings are provided at opposite ends of theeccentric pin portion 24 c of the crankshaft, the structure is more simplified. InFIG. 6 , the thrustbearing support portion 51 is engaged with thecore frame 30 by a bolt. - The oil supply way is a centrifugal oil supply way which is effected by the rotation of the eccentric
oil supply passage 24 f within thecrankshaft 24. Therefore, it is possible to reduce the number of parts, despite the disposition of theshaft support portion 50. - By virtue of the disposition of the
shaft support portion 50 for supporting thesub shaft portion 24 c of thecrankshaft 24 on the fixedscroll 2, as described above, it is possible to reduce the number of parts in the entire compressor and to construct the compressor having a simple arrangement, a small size and a high efficiency. - A displacement type compressor according to a third embodiment of the present invention will now be described with reference to
FIG. 7 .FIG. 7 shows the entire structure of a rotary compressor. - A drive source is a
motor 23 which is comprised of astator 21 comprisingstator cores 21am annular coils rotor 22. Thestator cores 21 a 21 b and 21 c are contained in acore frame 30. - A
compressing mechanism section 101 of the rotary compressor is comprised of acylinder 102, afirst end plate 103 and asecond end plate 104 for closing opposite ends of thecylinder 102, aroller 105 disposed in a space surrounded by thecylinder 102, thefirst end plate 103 and thesecond end plate 104, and a vane (not shown) having a function of changing the volume of a space defined by thecylinder 102, thefirst end plate 103, thesecond end plate 104 and theroller 105 in accordance with the movement of theroller 105. A compressingchamber 106 is a space volume which is defined by thecylinder 102, thefirst end plate 103, thesecond end plate 104, theroller 105 and the vane, and which is varied in accordance with the movement of theroller 105. A working fluid is drawn via anintake port 107 into the compressingchamber 106. The working fluid is compressed with the movement of theroller 105 and discharged into adischarge space 110 within aclosed container 112 via adischarge bore 108 provided in thesecond end plate 104 and adischarge valve 109 and further discharged from theclosed container 112 via adischarge port 111. - A means for driving the
roller 105 includes amotor 23, acrankshaft 120, afirst end plate 103 and asub frame 121. Thecrankshaft 120 includes amain shaft portion 120 a, asun shaft portion 120 b and aneccentric pin portion 120 c. Ashaft support portion 122 disposed on thefirst end plate 103 and ashaft support portion 123 disposed on thesub frame 121 provide shaft support portions with which themain shaft portion 120 a and thesub shaft portion 120 b of thecrankshaft 120 are rotatably engaged, and theroller 105 is rotatably engaged with theeccentric pin portion 120 c of thecrankshaft 120. Theshaft support portions compressing mechanism section 101 opposite from the motor and on the side of themotor 23 opposite from the compressing mechanism section, respectively. In addition to a sliding bearing which may be used for each of theshaft support portions - A
thrust bearing 130 is disposed on thesub frame 121 and adapted to receive a load when thecrankshaft 120 is moved downwards. When thecrankshaft 120 is moved upwards, athrust bearing 131 supports the load. - To lubricate slide contact surfaces of the
shaft support portions roller 105 and theeccentric pin portion 120 c of the crankshaft, a pumping action is realized by employing both of a centrifugal oil supply action caused by the rotation of an eccentricoil supply passage 120 d within thecrankshaft 120 and a differential oil supply action caused by a difference in pressure between the compressingchamber 106 and adischarge space 110 within aclosed container 112. More specifically, a lubricatingoil 132 accumulated in a lower space in theclosed container 112 is sucked by the oil supply pumping action and supplied to various portions through theoil supply passage 120 d provided in the crankshaft. An oil supply pump which may be used includes a trochoid pump or the like as an external oil supply pump which is not shown. - In order to eliminate an eccentric unbalance caused by the rotation of the
roller 105, theeccentric pi portion 120 c of the crankshaft or the like,balance weights compressing mechanism section 101 opposite from the motor and between thecompressing mechanism section 1 and themotor 23, respectively. Thebalance weight 134 between thecompressing mechanism section 101 and themotor 23 is of a shape smaller than an inside diameter of thestator 21 and hence, is capable of being passed through an inside diameter portion of thestator 21 through thecrankshaft 120. - With the above-described arrangement, the axial length of the motor is short, and the axial length of the displacement type compressor can be further reduced using a core frame structure. Therefore, the axial length of the
crankshaft 120 can be further reduced; thecompressing mechanism section 101 and themotor 23 can be disposed between the twoshaft support portions crankshaft 24 is rotatably engaged, and the balance weights for eliminating the eccentric unbalance can be disposed on the side of thecompressing mechanism section 101 opposite from the motor and between thecompressing mechanism section 101 and themotor 23, respectively, thereby further reducing the deformation of thecrankshaft 120 during operation at a high speed. Thus, it is possible to provide an increase in reliability during operation at the high speed and to reduce a loss of sliding of the bearing due to the deformation of the crankshaft, leading to an increase in energy efficiency. - In addition, the outside diameter of the
balance weight 134 disposed between thecompressing mechanism section 101 and themotor 23 can be set to be smaller than the inside diameter of thestator 21, leading to an enhanced assemblability. Therefore, it is possible to rationalize the load on the shaft support portions and to further reduce the deformation of the crankshaft caused by the remarkable eccentric unbalance during operation at the high speed, thereby realizing the rotary compressor capable of being operated at the high speed and having a high-energy efficiency. - A displacement type compressor according to a fourth embodiment of the present invention will now be described in detail with reference to
FIG. 8 .FIG. 8 shows the entire structure of a rotary compressor. - For a shaft support portion for a
crankshaft 120, ashaft support portion 140 is provided on asecond end plate 104. Athrust bearing 141 and athrust bearing 131 for supporting an axial force of thecrankshaft 120 are formed on the side of theeccentric pin portion 120 c of thecrankshaft 120 closer to the motor and at thefirst end plate 103, respectively, but both of the thrust bearings may be formed at opposite ends of theeccentric pin portion 120 c of the crankshaft, and in the latter case, it is possible to provide a further simplification. - A displacement type compressor according to a fifth embodiment of the present invention will now be described in detail with reference to
FIG. 9 .FIG. 9 shows the entire structure of a rotary compressor. - This displacement type compressor has a feature in that a
compressing mechanism section 154 is disposed in a lower portion of aclosed container 112 andbalance weights rotor 22. Thebalance weights rotor 22, and may be disposed on a crankshaft. Athrust bearing 153 and athrust bearing 152 for supporting an axial force of thecrankshaft 120 are formed at opposite ends of aneccentric pin portion 120 c of thecrankshaft 120 for the purpose of the simplification. In place of the provision of thethrust bearing 153, a thrust load can be received on a first end plate itself, and in this case, it is possible to provide a further simplified structure. - As described above, a resinous film can be applied to each of claw-type core portions formed of a magnetic powder formed with an insulating film, thereby preventing the dropping of the powder from the claw-type core portions formed of the magnetic powder and constituting a stator core of a motor, thus ensuring the reliability of the displacement type compressor.
- In addition, it is not required that the stator core comprised of the claw-type core portions formed of the magnetic powder is fit directly to a compressor casing and hence, it is possible to eliminate a fitting force applied to the claw-type core portions formed of the magnetic powder and to prevent the fracture of the claw-type core portions formed of the magnetic powder. Further, it is possible to reduce the deformation of the compressor casing due to the fitting and hence, it is possible to assemble parts to be engaged with the compressor casing at a good accuracy.
- Further, the motor can be disposed in further proximity to the compressing mechanism section and hence, it is possible to provide a reduction in axial length of the displacement type compressor; to ensure the coaxiality at a high accuracy between the crank shaft support portion provided on the side of the compressing mechanism section opposite from the motor and the stator core; and to reduce the flexure of the crankshaft to reduce the deformation of the crankshaft due to an eccentric unbalance during rotation at a high speed, leading to an increase in reliability.
- Furthermore, it is possible to maintain the coaxiality at a high accuracy between the crankshaft support portion provided on the compressing mechanism section, the stator core and the crankshaft support portion provided on the motor. Therefore, the balance weights can be passed through the inside of the stator, leading to an enhancement in assemblability of the compressor.
- Yet further, the disposition of the crankshaft support portions on the opposite sides of the compressing mechanism section ensures that an increase in a bearing load due to the reduction in length of the crankshaft is not brought out, and besides, the eccentric unbalance during operation at the high speed can be reduced.
- It should be further understood by those skilled in the art that although the foregoing description has been made on embodiments of the invention, the invention is not limited thereto and various changes and modifications may be made without departing from the spirit of the invention and the scope of the appended claims.
Claims (9)
1. A displacement type compressor, comprising a compressing mechanism section adapted to perform a compression, a motor for driving said compressing mechanism section, and a crankshaft adapted to be driven in rotation by said motor to rotate said compressing mechanism section, wherein said motor comprises a stator core in which claw-type magnetic poles formed of a magnetic powder are circumferentially arranged in alternately meshed states, and annular coils wound in a toric shape around said claw-type magnetic poles.
2. A displacement type compressor according to claim 1 , wherein each of said claw-type magnetic poles has a resinous film formed thereon.
3. A displacement type compressor according to claim 1 , wherein said compressing mechanism section comprises a fixed scroll and an orbiting scroll meshed with each other to perform the compression by the orbiting movement of said orbiting scroll.
4. A displacement type compressor according to claim 1 , wherein said stator core is fixed to a toric core frame which is disposed within said displacement type compressor.
5. A displacement type compressor according to claim 1 , wherein said compressing mechanism section and said motor are disposed between two shaft support portions on which said crankshaft is rotatably supported.
6. A displacement type compressor according to claim 1 , further including a balance weight disposed between said compressing mechanism section and said motor and having an outside diameter smaller than an inside diameter of said stator core.
7. A displacement type compressor according to claim 1 , further including a balance weight disposed on the side of said compressing mechanism section opposite from said motor.
8. A displacement type compressor according to claim 1 , wherein said compressing mechanism section comprises a fixed scroll and an orbiting scroll meshed with each other to perform the compression by the orbiting movement of said orbiting scroll, and said crankshaft is passed through said orbiting scroll and said fixed scroll and rotatably supported on portions of said orbiting scroll and said fixed scroll through which said crankshaft is passed.
9. A displacement type compressor, comprising a compressing mechanism section adapted to perform a compression, a motor for driving said compressing mechanism section, a crankshaft adapted to be driven in rotation by said motor to rotate said compressing mechanism section, and two shaft support portions on which said crankshaft is rotatably supported, wherein
said motor comprises a stator core in which claw-type magnetic poles formed of a magnetic powder are circumferentially arranged in alternately meshed states, and annular coils wound in a toric shape around said claw-type magnetic poles,
said compressing mechanism section comprises a fixed scroll and an orbiting scroll meshed with each other to perform the compression by the orbiting movement of said orbiting scroll,
said compressing mechanism section and said motor are disposed between said shaft support portions, and
a balance weight is disposed between said compressing mechanism section and said motor and has an outside diameter smaller than an inside diameter of said stator core.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006096358A JP2007270696A (en) | 2006-03-31 | 2006-03-31 | Displacement type compressor |
JP2006-096358 | 2006-03-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070231171A1 true US20070231171A1 (en) | 2007-10-04 |
Family
ID=38559206
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/627,389 Abandoned US20070231171A1 (en) | 2006-03-31 | 2007-01-26 | Displacement type compressor |
Country Status (3)
Country | Link |
---|---|
US (1) | US20070231171A1 (en) |
JP (1) | JP2007270696A (en) |
CN (1) | CN101046200A (en) |
Cited By (3)
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CN103814219A (en) * | 2011-09-30 | 2014-05-21 | 大金工业株式会社 | Scroll compressor |
US20160146208A1 (en) * | 2014-11-24 | 2016-05-26 | Lg Electronics Inc. | Scroll compressor |
EP4108933A4 (en) * | 2020-02-17 | 2024-01-24 | Daikin Ind Ltd | Compressor |
Families Citing this family (7)
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CN101881275A (en) * | 2009-05-08 | 2010-11-10 | 乐金电子(天津)电器有限公司 | Rotary compressor |
US8222788B2 (en) * | 2009-09-01 | 2012-07-17 | Emerson Electric Co. | Electric machine |
KR20200085559A (en) | 2019-01-07 | 2020-07-15 | 엘지전자 주식회사 | Motor operated compressor |
KR102191122B1 (en) * | 2019-01-18 | 2020-12-16 | 엘지전자 주식회사 | Motor operated compressor |
JP7426280B2 (en) * | 2020-04-01 | 2024-02-01 | 三菱重工サーマルシステムズ株式会社 | compressor |
JP2022060787A (en) * | 2020-10-05 | 2022-04-15 | 三菱重工サーマルシステムズ株式会社 | Electric compressor |
KR20240017262A (en) * | 2022-07-29 | 2024-02-07 | 엘지전자 주식회사 | Scroll Compressor |
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JPH02294239A (en) * | 1989-05-08 | 1990-12-05 | Seiko Epson Corp | Manufacture of motor stator |
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JPH05308768A (en) * | 1992-04-28 | 1993-11-19 | Minebea Co Ltd | Stator yoke for stepping motor |
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JPH08200250A (en) * | 1995-01-20 | 1996-08-06 | Hitachi Ltd | Shaft through scroll compressor |
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JPH11299146A (en) * | 1998-04-10 | 1999-10-29 | Cimeo Precision Co Ltd | Permanent-magnet multipolar rotor and its manufacture |
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- 2006-03-31 JP JP2006096358A patent/JP2007270696A/en active Pending
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2007
- 2007-01-26 US US11/627,389 patent/US20070231171A1/en not_active Abandoned
- 2007-01-26 CN CNA2007100082656A patent/CN101046200A/en active Pending
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US20030147763A1 (en) * | 2002-02-05 | 2003-08-07 | Matsushita Electric Industrial Co., Ltd. | Air supply apparatus |
US20040007936A1 (en) * | 2002-07-10 | 2004-01-15 | Jerome Cros | Polyphase claw pole structures for an electrical machine |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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CN103814219A (en) * | 2011-09-30 | 2014-05-21 | 大金工业株式会社 | Scroll compressor |
EP2762727A4 (en) * | 2011-09-30 | 2015-05-06 | Daikin Ind Ltd | Scroll compressor |
US10001122B2 (en) | 2011-09-30 | 2018-06-19 | Daikin Industries, Ltd. | Scroll compressor |
US20160146208A1 (en) * | 2014-11-24 | 2016-05-26 | Lg Electronics Inc. | Scroll compressor |
US10087937B2 (en) * | 2014-11-24 | 2018-10-02 | Lg Electronics Inc. | Scroll compressor |
EP4108933A4 (en) * | 2020-02-17 | 2024-01-24 | Daikin Ind Ltd | Compressor |
Also Published As
Publication number | Publication date |
---|---|
CN101046200A (en) | 2007-10-03 |
JP2007270696A (en) | 2007-10-18 |
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