JP2006283602A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of improving capacity in the compressor having an axial gap type motor arranged in a low pressure side in a hermetic vessel. <P>SOLUTION: This compressor is provided with the hermetic vessel 1, a compression mechanism part 2 arranged in the hermetic vessel 1, and the axial gap type motor 3 arranged in the low pressure side in which low pressure refrigerant gas sucked by the compression mechanism part 2 exists in the hermetic vessel 1. An inlet 21a of a suction passage 21 of the compression mechanism part 2 is provided near a rotor 30 outer circumference part of the axial gap type motor 3. A plurality of blades sending refrigerant gas in an inner circumference side to an outer circumference side is provided on an end surface of the rotor 30 of the axial gap type motor 3. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a compressor used in, for example, an air conditioner or a refrigerator.

  Conventionally, there is a compressor in which a compression mechanism and an axial gap type motor are mounted in a hermetically sealed container (see, for example, JP-A-61-185041 (Patent Document 1)). This compressor does not generate radial force, has no problem of vibration and noise due to misalignment, etc., and can be downsized by reducing the axial dimension.

By the way, in the said compressor, although it can reduce in size, without changing capability, the further capability improvement is desired.
JP-A-61-185041

  SUMMARY OF THE INVENTION An object of the present invention is to provide a compressor capable of further improving performance in a compressor in which an axial gap type motor is arranged on the low pressure side in a sealed container.

In order to achieve the above object, the compressor of the present invention provides:
A sealed container;
A compression mechanism disposed in the sealed container;
An axial gap motor that is disposed in the closed container and on a low pressure side where the low pressure gas sucked by the compression mechanism portion exists, and drives the compression mechanism portion,
The inlet of the suction passage of the compression mechanism is provided near the outer periphery of the rotor of the axial gap motor.

  According to the compressor having the above configuration, in the axial gap type motor disposed on the low pressure side where the low pressure gas sucked by the compression mechanism portion exists, the gas flows along the end surface of the rotor due to the centrifugal force accompanying the rotation of the rotor. It flows from the peripheral side to the outer peripheral side, and the pressure at the outer peripheral portion of the rotor is higher than that at the inner peripheral side. By providing the inlet of the suction passage of the compression mechanism near the outer periphery of the rotor, the refrigerant gas having a high density is sucked into the compression mechanism, so that the volumetric efficiency of the compression mechanism can be improved. Therefore, in the compressor in which the axial gap type motor is arranged on the low pressure side in the hermetic container, the capability can be further improved.

  Moreover, the compressor of one embodiment is characterized in that the suction passage of the compression mechanism section is extended so that the inlet is near the outer periphery of the axial gap.

  According to the compressor of the above embodiment, since the inlet of the suction passage of the compression mechanism portion is extended to the outer periphery of the axial gap, it is possible to suck from where the pressure has increased to the maximum, and the volume efficiency of the compressor can be increased. Further increase is possible.

  The compressor according to an embodiment is characterized in that vanes for sending gas on the inner peripheral side to the outer peripheral side are provided on the end face of the rotor of the axial gap motor.

  According to the compressor of the above embodiment, since the gas on the inner peripheral side is sent to the outer peripheral side by the blades provided on the end face of the rotor of the axial gap type motor, the pressure on the outer peripheral portion of the rotor is further increased, and the compression mechanism The volumetric efficiency of the part can be further improved.

  In one embodiment of the compressor, the rotor of the axial gap motor has a plurality of magnets arranged at predetermined intervals in the circumferential direction, and has an inner circumference in a region between the magnets adjacent to each other. A gas passage for guiding the gas on the side to the outer peripheral side is formed.

  According to the compressor of the above embodiment, the gas on the inner peripheral side is guided to the outer peripheral side by the gas passage formed in the region between the adjacent magnets of the rotor of the axial gap type motor. Thus, the volumetric efficiency of the compression mechanism can be further improved.

  In the compressor according to an embodiment, a gas passage for guiding the gas on the inner peripheral side to the outer peripheral side is formed in a region between the plurality of magnetic poles of the stator of the axial gap motor adjacent to each other. Features.

  According to the compressor of the above embodiment, the gas on the inner peripheral side is guided to the outer peripheral side by the gas passage formed in the region between the magnetic poles adjacent to each other of the stator of the axial gap type motor. The pressure increase in the outer peripheral portion due to the centrifugal force of the rotor is further increased, and the volumetric efficiency of the compression mechanism portion can be further improved.

  Moreover, the compressor of one Embodiment was provided with the rotation speed control part which controls the rotation speed of the said axial gap type motor.

  According to the compressor of the above embodiment, the rotational speed of the axial gap motor is controlled by the rotational speed control unit, and the boosting effect is increased in the high speed region where the rotor rotates at high speed, while the rotor rotates at low speed. The boosting effect is small in the low speed region. Therefore, compared to a compressor with the same capacity range, the capacity is increased in the high speed area, so the rotational speed can be lowered in the high speed area to reduce the mechanical loss and improve the efficiency, while the capacity is decreased in the low speed area. Therefore, it is possible to improve efficiency by increasing the number of revolutions and preventing an increase in motor loss and leakage loss.

  As is clear from the above, according to the compressor of the present invention, further improvement in performance can be achieved in the compressor in which the axial gap type motor is arranged on the low pressure side in the hermetic container.

  Further, according to the compressor of one embodiment, the suction pressure is further increased by further extending the inlet of the suction passage of the compression mechanism portion to the outer periphery of the axial gap, and the volume efficiency of the compression mechanism portion can be further improved. .

  Further, according to the compressor of one embodiment, the pressure on the outer peripheral portion of the rotor is further increased by sending the gas on the inner peripheral side to the outer peripheral side by the blades provided on the end face of the rotor of the axial gap type motor, The volumetric efficiency of the compression mechanism can be further improved.

  Further, according to the compressor of one embodiment, the outer periphery of the rotor is guided by guiding the gas on the inner peripheral side to the outer peripheral side by the gas passage formed in the region between the adjacent magnets of the rotor of the axial gap type motor. The pressure of the part is further increased, and the volume efficiency of the compression mechanism part can be further improved.

  Further, according to the compressor of the embodiment, the gas on the inner peripheral side is guided to the outer peripheral side by the gas passage formed in the region between the magnetic poles adjacent to each other of the stator of the axial gap type motor, thereby facing the stator. The pressure increase of the gas at the outer peripheral portion due to the centrifugal force of the rotor is further increased, and the volumetric efficiency of the compression mechanism portion can be further improved.

  Also, according to the compressor of one embodiment, in a compressor having a rotation speed control unit that controls the rotation speed of an axial gap motor, the capability increases in the high speed region, so the rotation speed is decreased in the high speed region. While the efficiency can be improved by reducing the mechanical loss, the capacity is reduced in the low speed region, so that the efficiency can be improved by increasing the number of revolutions to prevent an increase in motor loss and leakage loss. Therefore, the control range of the rotational speed of the axial gap motor can be narrowed, and motor control is facilitated.

  Hereinafter, the compressor of the present invention will be described in detail with reference to the illustrated embodiments.

(First embodiment)
FIG. 1 shows a sectional view of a compressor according to a first embodiment of the present invention.

  As shown in FIG. 1, the compressor according to the first embodiment includes a sealed container 1, a compression mechanism unit 2 disposed in the sealed container 1, and the lower side of the compression mechanism unit 2 in the sealed container 1. And an axial gap motor 3 that drives the compression mechanism 2 via the rotary shaft 4 and is provided outside the sealed container 1 (may be provided inside the sealed container 1). And an inverter 10 for outputting a drive current. The inverter 10 includes a rotation speed control unit 10 a that controls the rotation speed of the axial gap type motor 3. The axial gap motor 3 is disposed in a low-pressure space on the suction side of the compression mechanism 2 in the sealed container 1. This compressor is a so-called low-pressure dome type.

  The axial gap type motor 3 includes a stator 40 and a rotor 30 disposed on the upper side of the stator 40. The rotor 30 is externally fitted and fixed to the rotary shaft 4, and the rotational force of the rotor 30 is transmitted to the compression mechanism unit 2 via the rotary shaft 4.

  The compression mechanism unit 2 includes a main body 20 attached in the sealed container 1, a fixed scroll 24 fixed to the main body 20, and a turning scroll 23 that meshes with the fixed scroll 24. The fixed scroll 24 and the orbiting scroll 23 each have a whirling wrap erected on the end plate, and the fixed scroll 24 and the orbiting scroll 23 mesh with each other to form a plurality of compression chambers 25. The orbiting scroll 23 is connected to the upper end of the rotating shaft 4 of the axial gap type motor 3 and revolves by the rotation of the rotating shaft 4 (actually, the rotation is changed to the revolution motion, but the present invention is not the revolution motion). Compression mechanism).

  The main body 20 rotatably supports the upper end side of the inserted rotating shaft 4. A holding portion 5 that rotatably supports the lower end side of the rotating shaft 4 is provided in the sealed container 1 and below the axial gap type motor 3.

  The main body 20 has a suction passage 21 that communicates the lower low-pressure space and the compression chamber 25, and the fixed scroll 24 has a discharge hole 26 that communicates the upper high-pressure space and the compression chamber 25. .

  A suction pipe 11 is connected to the lower side surface of the sealed container 1, while a discharge pipe 12 is connected to the upper part of the sealed container 1. The refrigerant gas supplied through the suction pipe 11 flows into the lower space of the axial gap motor 3.

  FIG. 2 is an exploded perspective view of the axial gap type motor 3. As shown in FIG. 2, the rotor 30 has a predetermined interval in the circumferential direction between a disk-shaped back yoke 31 made of a magnetic material having a central hole 31 a and a surface of the back yoke 31 that faces the stator 40. The four fan-shaped permanent magnets 32 and the disk-shaped magnetic plate 33 having the central hole 33a are overlapped. A plurality of curved blades 34 are provided radially above the back yoke 31 (on the side opposite to the rotor 30) (the blades 34 are omitted in FIG. 1). The magnetic plate 33 is not essential, but is useful for reducing the eddy current of the rotor permanent magnet and improving the demagnetization resistance.

  Further, four slits 33b are provided radially on the magnetic plate 33, and four permanent magnets 32 are arranged at predetermined intervals in the circumferential direction in an area partitioned by the four slits 33b. In addition, the back yoke 31 is provided with a circular hole 31b in a region facing the slit 33b of the magnetic plate 33 and in the vicinity of the central hole 31a. The slit 33b of the magnetic plate 33, the space between the permanent magnets 32, and the circular hole 31b of the back yoke 31 form a gas passage through which the refrigerant gas flows in the axial direction.

  The rotor 30 has four permanent magnets 32 arranged such that magnetic poles are alternately arranged in the circumferential direction. In the rotor 30, the four permanent magnets 32 are magnetically insulated from each other by the slits 33 b of the magnetic plates 33.

  The stator 40 includes a disk-shaped magnetic plate 41 having a central hole 41a, a substrate 43 made of a magnetic material, and six magnetic cores erected on the substrate 43 at predetermined intervals in the circumferential direction. 44 and a coil 42 wound around the six magnetic cores 44. The magnetic plate 41 of the stator 40 is radially provided with six slits 41b for magnetically insulating a plurality of magnetic cores 44 from each other. The magnetic plate 41 is not essential, but is useful for interlinking more magnetic flux of the permanent magnet with the windings.

  The six magnetic cores 44 are magnetically connected to each other by the substrate 43, and the side facing the rotor 30 is connected by the magnetic plate 41. The coil 42 is, for example, a three-phase star connection and supplies current from the inverter 10 (shown in FIG. 1).

  In the compressor configured as described above, when the compression mechanism unit 2 is driven by the axial gap motor 3 via the rotating shaft 4, the refrigerant gas supplied from the suction pipe 11 cools the axial gap motor 3 while being in the axial gap type. The refrigerant gas that passes through the air gap of the motor 3 or a gas passage (not shown) provided in the axial direction and is supplied through the suction passage 21 is compressed by the compression mechanism 2. The refrigerant gas thus compressed is discharged into the upper space from the discharge hole 26 of the compression mechanism unit 2 and is discharged to the outside of the sealed container 1 through the discharge pipe 12.

  At this time, the refrigerant gas flowing out from the inner peripheral side along the upper end surface of the rotor 30 is sent to the outer peripheral side by the centrifugal force generated by the rotation of the rotor 30 of the axial gap motor 3. As a result, the pressure of the refrigerant gas at the outer peripheral portion of the rotor 30 rises, and the compression mechanism 2 sucks in a high-density refrigerant gas from the inlet 21a of the suction passage 21.

  According to the compressor having the above configuration, in the axial gap type motor 3 disposed on the low pressure side where the low pressure refrigerant gas sucked by the compression mechanism section 2 exists, the suction passage of the compression mechanism section 2 is disposed in the vicinity of the outer peripheral portion of the rotor 30. By providing the inlet, a refrigerant gas having a high density is sucked into the compression mechanism section 2, so that the volumetric efficiency of the compression mechanism section 2 can be improved.

  Further, since the refrigerant gas on the inner peripheral side is sent to the outer peripheral side by the plurality of blades 34 provided on the end face of the rotor 30 of the axial gap motor 3, the pressure on the outer peripheral portion of the rotor 30 is further increased, and the compression mechanism unit The volumetric efficiency of 2 can be further improved.

  Accordingly, since the refrigerant gas having a high density is sucked into the compression mechanism unit 2, the volume efficiency of the compression mechanism unit 2 can be improved, and the compression mechanism unit 2 can be downsized.

  Further, the rotational speed of the axial gap motor 3 is controlled by the rotational speed control unit 10a, and the boosting effect is increased in the high speed region where the rotor 30 rotates at high speed, while the boosting effect is increased in the low speed region where the rotor 30 rotates at low speed. The effect is reduced. Therefore, compared to a compressor with the same capacity range, the capacity is increased in the high speed area, so the rotational speed can be lowered in the high speed area to reduce the mechanical loss and improve the efficiency, while the capacity is decreased in the low speed area. Therefore, it is possible to improve efficiency by increasing the number of revolutions and preventing an increase in motor loss and leakage loss.

  In the first embodiment, the compressor including the axial gap type motor 3 in which the rotor 30 is disposed on the upper side of the stator 40 has been described. However, the axial gap type motor in which the rotor is disposed on the upper side and the lower side of the stator, respectively. But you can.

(Second Embodiment)
FIG. 3 shows a sectional view of the compressor of the second embodiment of the present invention. The compressor of this 2nd Embodiment is carrying out the structure same as the compressor of 1st Embodiment except an axial gap type motor, and the same component is attached | subjected the same reference number.

  As shown in FIG. 3, the compressor according to the second embodiment includes a sealed container 1, a compression mechanism unit 2 disposed in the sealed container 1, and the lower side of the compression mechanism unit 2 in the sealed container 1. An axial gap motor 103 that drives the compression mechanism section 2 via the rotary shaft 4, and an inverter 10 that is provided outside the sealed container 1 and outputs a drive signal to the axial gap motor 3. ing. The inverter 10 includes a rotation speed control unit 10 a that controls the rotation speed of the axial gap motor 103.

  The axial gap type motor 103 includes a stator 40 and a rotor 130 disposed above the stator 40. The rotor 130 is fitted on and fixed to the rotary shaft 4, and the rotational force of the rotor 30 is transmitted to the compression mechanism unit 2 through the rotary shaft 4.

  FIG. 4 shows an exploded perspective view of the axial gap type motor 103. The axial gap type motor 103 has the same configuration as the axial gap type motor 3 shown in FIG. 2 of the first embodiment except for the back yoke 35.

  As shown in FIG. 4, the rotor 130 has a predetermined interval in the circumferential direction between a disk-shaped back yoke 35 made of a magnetic material having a central hole 31 a and a surface of the back yoke 35 facing the stator 40. The four fan-shaped permanent magnets 32 and the disk-shaped magnetic plate 33 having the central hole 33a are overlapped. The back yoke 35 is not provided with a hole through which the refrigerant gas flows in the axial direction. A gas passage 36 that guides the refrigerant gas from the inner peripheral side to the outer peripheral side is formed between the adjacent permanent magnets 32 of the rotor 130.

  In the compressor configured as described above, when the compression mechanism unit 2 is driven by the axial gap type motor 103 via the rotary shaft 4, the refrigerant gas supplied from the suction pipe 11 cools the axial gap type motor 103 while the axial gap type motor 103. The refrigerant gas that passes through the air gap of the motor 103 and the gas passage 36 provided in the rotor 130 and is supplied through the suction passage 21 is compressed by the compression mechanism section 2. The refrigerant gas thus compressed is discharged into the upper space from the discharge hole 26 of the compression mechanism unit 2 and is discharged to the outside of the sealed container 1 through the discharge pipe 12.

  At this time, the refrigerant gas flowing out from the upper center of the stator 40 is sent to the outer peripheral side by the centrifugal force generated by the rotation of the rotor 130 of the axial gap motor 3. As a result, the pressure of the refrigerant gas at the outer peripheral portion of the rotor 130 increases, and the compression mechanism 2 sucks in a high-density refrigerant gas from the inlet 21a of the suction passage 21.

  Accordingly, since the refrigerant gas having a high density is sucked into the compression mechanism unit 2, the volume efficiency of the compression mechanism unit 2 can be improved, and the compression mechanism unit 2 can be downsized.

  According to the compressor having the above configuration, in the axial gap type motor 103 disposed on the low pressure side where the low pressure refrigerant gas sucked by the compression mechanism section 2 exists, the lower side of the rotor 130 is caused by the centrifugal force accompanying the rotation of the rotor 130. The refrigerant gas flows from the inner peripheral side to the outer peripheral side along the end surface, and the pressure at the outer peripheral portion of the rotor 130 becomes higher than that on the inner peripheral side. By providing the inlet 21a of the suction passage 21 of the compression mechanism unit 2 in the vicinity of the outer periphery of the rotor 130, a refrigerant gas having a high density is sucked into the compression mechanism unit 2, so that the volumetric efficiency of the compression mechanism unit 2 can be improved. .

  Further, since the gas on the inner peripheral side is guided to the outer peripheral side by the gas passage 36 formed in the region between the adjacent permanent magnets 32 of the rotor 130 of the axial gap type motor 103, the pressure at the outer peripheral portion of the rotor 13 is increased. Becomes higher, and the volumetric efficiency of the compression mechanism portion 2 can be further improved.

  In the compressor of the second embodiment, a guide passage that connects the inlet 21a of the suction passage 21 of the compression mechanism 2 and the vicinity of the outer periphery of the rotor 130 is provided, and the inlet of the guide passage is connected to the refrigerant gas. More preferably, it is arranged at a location where the density is high.

(Third embodiment)
FIG. 5 shows an exploded perspective view of a stator of an axial gap type motor used in the compressor of the third embodiment of the present invention. The compressor of this 3rd Embodiment is carrying out the structure same as the compressor of 2nd Embodiment except a stator, the description of the same structure part is abbreviate | omitted and FIG. 3 is used.

  As shown in FIG. 5, the stator 50 of the axial gap type motor used in the compressor of the third embodiment includes a magnetic plate group 51 in which six magnetic plates 55 are arranged in the circumferential direction, and a substrate made of a magnetic material. 53, six magnetic cores 54 erected at predetermined positions in the circumferential direction at positions substantially opposite to the magnetic plates 55 on the substrate 53, and coils 52 wound around the six magnetic cores 54. And have. The magnetic plate group 51 is provided with a gas passage 56 for guiding the refrigerant gas from the inner peripheral side to the outer peripheral side in a region between the magnetic plates 55 adjacent to each other.

  A central hole 51 a is formed inside the magnetic plate group 51. The magnetic plate 55 constituting the magnetic plate group 51 includes an inner peripheral edge 55a that forms a part of the center hole 51a, and a front end of the inner peripheral edge 55a (opposite to the rotational direction R2 of the rotor) gradually toward the outer periphery. And a front edge 55b that curves backward (rotation direction R2 of the rotor), a rear edge 55c that curves gradually rearward from the rear end of the inner peripheral edge 55a toward the outer periphery, and an outer peripheral edge 55d.

  The six magnetic cores 54 are magnetically connected to each other by a substrate 53. The coil 52 is, for example, three-phase star-connected, and supplies current from the inverter 10.

  6A shows a perspective view of the stator 50 after assembly, FIG. 6B shows a side view of the stator 50, and FIG. 6C shows a plan view of the stator 50. As shown in FIG. 6C, a plurality of gas passages 56 are arranged radially.

  According to the compressor having the above-described configuration, the same effect as that of the compressor of the second embodiment is obtained, and gas formed in a region between adjacent magnetic poles (magnetic plates 55) of the stator 50 of the axial gap motor. By guiding the gas on the inner peripheral side to the outer peripheral side through the passage 56, the pressure increase of the gas at the outer peripheral portion due to the centrifugal force of the rotor 130 facing the stator 50 is further increased, and the volumetric efficiency of the compression mechanism portion 2 is further improved. it can.

  Further, the skew effect is caused by the shape of the magnetic plate 55 having the front edge 55b that gradually curves backward toward the outer periphery and the rear edge 55c that gradually curves backward from the rear end of the inner peripheral edge 55a toward the outer periphery. As a result, the cogging torque can be reduced, and the vibration and noise of the axial gap motor can be suppressed.

(Fourth embodiment)
FIG. 7 shows an exploded perspective view of a rotor of an axial gap type motor used in the compressor of the fourth embodiment of the present invention, and FIG. 8 shows an exploded perspective view of this axial gap type motor. The compressor of this 4th Embodiment is carrying out the structure same as the compressor of 2nd Embodiment except the rotor of an axial gap type motor, The description of the same structure part is abbreviate | omitted and FIG. 3 is used.

  As shown in FIG. 7, the rotor 60 of the fourth embodiment includes a disk-shaped back yoke 61 made of a magnetic material having a central hole 61a, and a surface side of the back yoke 61 that faces the stator (not shown). And four permanent magnets 62 arranged at predetermined intervals in the circumferential direction. A curved gas passage 63 for guiding the refrigerant gas from the inner peripheral side to the outer peripheral side is provided in a region between the adjacent permanent magnets 62 of the rotor 60. The permanent magnet 62 includes an inner peripheral edge 62a, and a front edge 62b that curves gradually rearward (opposite to the rotor rotational direction R3) from the front end (rotor rotational direction R3) of the inner peripheral edge 62a toward the outer periphery. , A rear edge 62c that gradually curves rearward from the rear end of the inner peripheral edge 62a toward the outer periphery, and an outer peripheral edge 62d.

  Moreover, as shown in FIG. 8, the stator 40 that rotationally drives the rotor 60 has the same configuration as the stator 40 of the second embodiment.

  According to the compressor having the above-described configuration, the gas passage 63 formed in the region between the adjacent permanent magnets 62 of the rotor 60 of the axial gap motor has the same effect as the compressor of the second embodiment. Since the gas on the inner peripheral side is guided to the outer peripheral side, the pressure on the outer peripheral portion of the rotor 60 is further increased, and the volumetric efficiency of the compression mechanism portion 2 can be further improved. Further, the skew effect is caused by the shape of the permanent magnet 62 having the front edge 62b that gradually curves backward toward the outer periphery and the rear edge 62c that gradually curves backward from the rear end of the inner peripheral edge 62a toward the outer periphery. As a result, the cogging torque can be reduced, and the vibration and noise of the axial gap motor can be suppressed.

(Fifth embodiment)
FIG. 9 shows a sectional view of a compressor according to a fifth embodiment of the present invention. The compressor of the fifth embodiment has the same configuration as the compressor of the first embodiment except for the axial gap type motor and the suction pipe, and the same components are denoted by the same reference numerals and description thereof is omitted. To do.

  As shown in FIG. 9, the compressor according to the fifth embodiment includes a sealed container 1, a compression mechanism portion 2 disposed in the sealed container 1, and the lower side of the compression mechanism portion 2 in the sealed container 1. An axial gap motor 203 that drives the compression mechanism section 2 via the rotary shaft 4 and an inverter 10 that is provided outside the sealed container 1 and outputs a drive signal to the axial gap motor 203. ing. The inverter 10 includes a rotation speed control unit 10 a that controls the rotation speed of the axial gap type motor 203.

  The axial gap type motor 203 has a stator 240 and a rotor 230 disposed below the stator 240. The rotor 230 is externally fitted and fixed to the rotary shaft 4, and the rotational force of the rotor 230 is transmitted to the compression mechanism unit 2 through the rotary shaft 4.

  One end of the guide passage 14 is connected to the inlet end of the suction passage 21 of the compression mechanism portion 2, and the inlet 14a of the guide passage 14 is near the outer periphery of the rotor 230 (particularly, near the outer periphery of the motor air gap, that is, the axial gap). It arrange | positions in the location where the density of the refrigerant gas is high. The inlet passage 21 of the compression mechanism 2 may be extended as it is so that the inlet is near the outer periphery of the axial gap.

  In the compressor configured as described above, when the compression mechanism unit 2 is driven by the axial gap type motor 203 via the rotary shaft 4, the refrigerant gas supplied from the suction pipe 13 cools the axial gap type motor 203 while the axial gap type motor 203. The refrigerant gas that passes through the air gap of the motor 203 and the gas passage provided in the rotor 230 and is supplied through the suction passage 21 is compressed by the compression mechanism 2. The refrigerant gas thus compressed is discharged into the upper space from the discharge hole 26 of the compression mechanism unit 2 and is discharged to the outside of the sealed container 1 through the discharge pipe 12.

  At this time, the refrigerant gas flowing out from the lower center through the hole (not shown) provided in the axial direction of the stator 240 by the centrifugal force generated by the rotation of the rotor 230 of the axial gap motor 3 is moved to the outer peripheral side. send. As a result, the pressure of the refrigerant gas at the outer peripheral portion of the rotor 230 increases, and the compression mechanism 2 sucks in a high-density refrigerant gas from the inlet 14a of the guide passage 14.

  Accordingly, since the refrigerant gas having a high density is sucked into the compression mechanism unit 2, the volume efficiency of the compression mechanism unit 2 can be improved, and the compression mechanism unit 2 can be downsized.

  In the fifth embodiment, as in the second embodiment, a space between adjacent permanent magnets may be used as a gas passage through which the refrigerant gas flows in the axial direction, as in the third embodiment. Further, the refrigerant gas may be guided from the inner peripheral side to the outer peripheral side by a gas passage formed in a region between the magnetic plates adjacent to each other of the stator, and further, the rotors are adjacent to each other as in the fourth embodiment. The refrigerant gas may be guided from the inner peripheral side to the outer peripheral side by a curved gas passage provided in a region between the permanent magnets.

  Next, the shape of the rotor blades and gas passages of the axial gap motor of the compressor according to the present invention will be described with reference to the examples shown in FIGS.

  FIG. 10A shows a rotor 71 rotating in a clockwise direction, and a plurality of blades 72 whose intermediate portions are curved backward are provided at predetermined intervals in the circumferential direction (in FIG. 10A, the blades). 72 shows only a part). The plurality of blades 72 correspond to a sirocco fan.

  Further, in FIG. 10B, a plurality of linear blades 82 are provided radially on the rotor 81 whose rotation direction is clockwise (only a part of the blades 82 is shown in FIG. 10B). The plurality of blades 82 correspond to a radial fan.

  Further, in FIG. 10C, a rotor 91 whose rotation direction is clockwise is provided with a plurality of blades 92 whose intermediate portions are curved forward at predetermined intervals in the circumferential direction (FIG. 10C). Then, the blade 92 shows only a part). The plurality of blades 92 correspond to a turbo type fan.

  If the conditions such as the rotational speed are the same in the order of the rotor 71 in FIG. 10A, the rotor 81 in FIG. 10B, and the rotor 91 in FIG. 10C, the flow rate increases.

  10 (a) to 10 (c) may be provided with a gas passage having a similar shape, or a similar gas passage may be provided for a non-rotating stator. Moreover, the shape of a blade | wing or a gas channel | path is not restricted to the shape shown to Fig.10 (a)-(c).

  In the first to fifth embodiments, the compressor of the scroll mechanism has been described. However, the present invention is not limited to this, and the present invention is applied to a compressor having a compressor mechanism of another structure such as a rotary system. May be applied.

  In addition, the motor does not necessarily have a permanent magnet, and a switched reluctance motor, an induction motor, or the like can be applied. However, by having a permanent magnet, the magnetic flux density of the air gap portion can be increased. It is excellent in that torque and motor efficiency can be improved.

  Furthermore, the motor only needs to have an axial gap, and may have both an axial gap and a radial gap.

FIG. 1 is a sectional view of a compressor according to a first embodiment of the present invention. FIG. 2 is an exploded perspective view of the axial gap motor of the compressor. FIG. 3 is a sectional view of a compressor according to the second embodiment of the present invention. FIG. 4 is an exploded perspective view of the axial gap motor of the compressor. FIG. 5 is an exploded perspective view of a stator of an axial gap type motor used in the compressor according to the third embodiment of the present invention. FIG. 6A is a perspective view of the stator after assembly. FIG. 6B is a side view of the stator. FIG. 6C is a plan view of the stator. FIG. 7 is an exploded perspective view of a rotor of an axial gap motor used in the compressor according to the fourth embodiment of the present invention. FIG. 8 is an exploded perspective view of the axial gap motor. FIG. 9 is a sectional view of a compressor according to a fifth embodiment of the present invention. FIG. 10 is a diagram for explaining the shape of rotor blades or gas passages.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Sealed container 2 ... Compression mechanism part 3,103,203 ... Axial gap type motor 4 ... Rotary shaft 5 ... Holding part 10 ... Inverter 10a ... Speed control part 11 ... Intake pipe 12 ... Discharge pipe 20 ... Main-body part 21 ... Suction passage 23 ... Orbiting scroll 24 ... Fixed scroll 25 ... Compression chamber 26 ... Discharge hole 30, 130, 230 ... Rotor 31a ... Central hole 31 ... Back yoke 32 ... Permanent magnet 33 ... Magnetic plate 33a ... Central hole 33b ... Slit 34 ... Blade 35 ... Back yoke 40, 240 ... Stator 41 ... Magnetic plate 41a ... Central hole 41b ... Slit 42 ... Coil 43 ... Substrate 44 ... Magnetic core 50 ... Stator 51 ... Magnetic plate group 52 ... Coil 53 ... Substrate 54 ... Magnetic core 55 ... Magnetic Plate 56 ... Gas passage 60 ... Rotor 61 ... Back yoke 62 ... Permanent magnet 63 ... Gas passage

Claims (6)

A sealed container (1);
A compression mechanism (2) disposed in the sealed container (1);
An axial gap type motor (3, 103, 203) that is disposed in the hermetic container (1) and on the low-pressure side where the low-pressure gas sucked by the compression mechanism (2) exists and drives the compression mechanism (2). And
A compressor characterized in that an inlet of the suction passage of the compression mechanism (2) is provided in the vicinity of the outer peripheral portion of the rotor (30, 130, 230) of the axial gap type motor (3, 103, 203). The compressor according to claim 1,
The compressor characterized in that the suction passage of the compression mechanism (2) is extended so that the inlet is near the outer periphery of the axial gap. The compressor according to claim 1,
A compressor characterized in that a blade (34) for sending gas on the inner peripheral side to the outer peripheral side is provided on an end face of the rotor (30) of the axial gap motor (3). The compressor according to claim 1,
The rotor (130) of the axial gap type motor (103) has a plurality of magnets (32) arranged at predetermined intervals in the circumferential direction, and is arranged on the inner circumferential side in a region between the adjacent magnets. The compressor is characterized in that a gas passage (36) for guiding the gas to the outer peripheral side is formed. The compressor according to claim 1,
A compressor characterized in that a gas passage (56) for guiding an inner peripheral side gas to an outer peripheral side is formed in a region between adjacent magnetic poles of a stator (50) of the axial gap type motor. The compressor according to any one of claims 1 to 5,
A compressor comprising a rotation speed control section (10a) for controlling the rotation speed of the axial gap motor (3, 103, 203).

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