KR20110005203A - Compressor - Google Patents

Abstract

PURPOSE: A compressor equipped with an intake/exhaust unit is provided to reduce the rotation of an electric motor used in a compressor equipped with a rotating cylinder. CONSTITUTION: A compressor equipped comprises an intake/exhaust unit. A piston seal is formed within the rotating cylinder. The intake/exhaust unit can perform the intake and exhaust of air since a piston moves in a reciprocating motion. A first intake/exhaust unit and a second intake/exhaust unit are parallel in the rotation axis direction of the cylinder. The first intake/exhaust unit comprises a first cylinder(28). The second intake/exhaust unit comprises a second cylinder(30). The crank shaft is inserted into the first cylinder and the second cylinder.

Description

Compressor {COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor having a suction / discharge mechanism portion for suctioning and discharging by reciprocating a piston in a piston chamber formed in a rotating cylinder.

This kind of compressor is disclosed by patent document 1, for example. In the compressor of patent document 1, the shaft is connected to the piston accommodated in the groove | channel (piston chamber) formed in the cylinder, and when a shaft rotates, a piston rotates around the axis of rotation of a shaft. This rotation causes the cylinder to rotate and the piston to reciprocate in the grooves. By the rotation of the cylinder and the reciprocating motion of the piston, the fluid is sucked into the piston chamber through the suction port, and the fluid in the piston chamber is discharged through the discharge port.

Japanese Patent Application Laid-Open No. 11-125191

The shaft is rotated by obtaining a driving force from the electric motor, and the driving force for rotating the shaft is transmitted to the cylinder through the shaft. As a result, the cylinder rotates once for two revolutions of the shaft. In short, in order to rotate the cylinder once, it is necessary to rotate the electric motor twice, and the high rotational operation of the electric motor increases the noise.

An object of the present invention is to achieve low rotation of an electric motor used in a compressor having a rotating cylinder.

The present invention is directed to a compressor having a piston chamber formed in a rotating cylinder, and having a suction / discharge mechanism portion in which a piston performs suction and discharge by reciprocating in the piston chamber. The first suction / discharge mechanism portion and the second suction / discharge mechanism portion are formed in parallel in the rotational axis direction of the cylinder, the first suction / discharge mechanism portion includes a first cylinder, and the second suction / discharge mechanism portion is second A cylinder is provided, A crankshaft is inserted through the said 1st cylinder and a said 2nd cylinder, The center axis of the said crankshaft is eccentric with respect to the rotational axis of the said 1st cylinder and the said 2nd cylinder, The said rotation The rotation angle position of the first cylinder about an axis and the rotation angle of the second cylinder around the rotation axis Deviation value, and wherein the cylinder is formed in the ring of the annular rotor constituting the electric motor, is connected to be able to rotate integrally with the rotor and the cylinder is e.

According to such a structure, when an electric motor rotates once, a cylinder rotates once. The number of rotations of the electric motor can be reduced by half compared with the conventional compressor in which the cylinder rotates half a revolution of the electric motor, and the noise (motor rotation noise) due to the rotation of the electric motor is reduced. Moreover, in the compressor provided with two suction / discharge mechanism parts, discharge is performed twice by each suction / discharge mechanism part with respect to one rotation of an electric motor.

In a preferable example, the first suction / discharge mechanism portion includes a first suction chamber and a first discharge chamber, and the fluid in the first suction chamber is sucked into the first piston chamber of the first cylinder, and the first suction chamber is provided. The fluid in the piston chamber is discharged to the first discharge chamber, and the second suction / discharge mechanism portion includes a second suction chamber and a second discharge chamber, and the fluid in the second suction chamber is formed of the second cylinder. The second piston chamber is sucked into the fluid, the fluid in the second piston chamber is discharged to the second discharge chamber, and an in-axis passage is formed through the crankshaft, so that the first discharge chamber and the second discharge chamber are in the shaft passage. Communicating through.

In the configuration in which the first discharge chamber and the second discharge chamber communicate with each other via the in-axis passage, only one discharge port may discharge the fluid out of the compressor.

In a preferable example, the first suction / discharge mechanism portion includes a first suction chamber and a first discharge chamber, and the fluid in the first suction chamber is sucked into the first piston chamber of the first cylinder, and the first suction chamber is provided. The fluid in the piston chamber is discharged to the first discharge chamber, and the second suction / discharge mechanism portion includes a second suction chamber and a second discharge chamber, and the fluid in the second suction chamber is formed of the second cylinder. The second piston chamber is sucked into the fluid, the fluid in the second piston chamber is discharged to the second discharge chamber, and an in-axis passage is formed through the crankshaft, so that the first discharge chamber and the second suction chamber are in the shaft passage. And a discharge volume in the second piston chamber is smaller than a discharge volume in the first piston chamber.

The difference between the pressure in the first suction chamber of the first suction / discharge mechanism part and the pressure in the first discharge chamber of the first suction / discharge mechanism part, and the pressure and the second suction / discharge in the second suction chamber of the second suction / discharge mechanism part The difference in pressure in the second discharge chamber of the mechanism portion can be made small.

In a preferable example, the length in the rotational axis direction of the second cylinder and the second piston is shorter than the length in the rotational axis direction of the first cylinder and the first piston.

Such a configuration is simple in providing a difference between the discharge volume in the first piston chamber and the discharge volume in the second piston chamber.

In a preferable example, the rotor and the cylinder are formed separately, the cylinder is fitted in a ring of the rotor, the annular rotor has a torque transmission plane on its inner circumferential surface, and the cylinder And a torque receiving plane joined to the torque transmission plane.

In the case where the cylinder and the rotor are keyed, there is a risk that the keyway is deformed due to the torque, and the backlash is increased in such a way that a noise is generated. In addition, when the cylinder is press-fitted into the rotor, the cylinder chamber may be deformed, and if so, the piston is locked in the piston chamber.

In the structure which joins a torque transmission plane and a torque receiving plane, problems, such as generation | occurrence | production of a noise and locking of a piston, do not arise.

The present invention exhibits an excellent effect of achieving low rotation of an electric motor used for a compressor having a rotating cylinder.

1 is a side cross-sectional view showing a first embodiment.
FIG. 2A is a cross-sectional view taken along the line AA of FIG. 1, and FIG. 2B is a cross-sectional view taken along the line BB of FIG. 1.
FIG. 3A is a cross-sectional view taken along the line CC of FIG. 1, and FIG. 3B is a cross-sectional view taken along the line DD of FIG. 1.
(A1), (a2), (a3) and (a4) are sectional views for explaining the rotational position of the first cylinder 28 and the position of the first piston 35 in the first piston chamber 281. 4 (b1), (b2), (b3) and (b4) are sectional views for explaining the rotational position of the second cylinder 30 and the position of the second piston 36 in the second piston chamber 301. to be.
5 is a side sectional view showing a second embodiment.
FIG. 6A is a cross-sectional view taken along the line EE of FIG. 5, and FIG. 6B is a cross-sectional view taken along the line FF of FIG. 1.
FIG.7 (a), (b) is sectional drawing of 3rd Embodiment.
8 (a) and 8 (b) are cross-sectional views of the fourth embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, 1st Embodiment which actualized this invention is described based on FIGS.

As shown in FIG. 1, the front housing 12 is connected to one end of the cylindrical center housing 11, and the rear housing 13 is connected to the other end of the center housing 11. The center housing 11, the front housing 12, and the rear housing 13 constitute the entire housing of the electric compressor 10.

On the inner surface of the end wall 121 of the front housing 12, a pair of cylindrical partition walls 14 and 15 protrude and are formed. The partition wall 15 is surrounded by the partition wall 14. The first suction chamber 16 and the first discharge chamber 17 are partitioned and formed between the partition wall 14 and the partition wall 15, and the communication chamber 18 is partitioned in the partition wall 15. Formed.

On the inner surface of the end wall 131 of the rear housing 13, a pair of cylindrical partition walls 19 and 20 protrude and are formed. The partition wall 20 is surrounded by the partition wall 19. The second suction chamber 21 and the second discharge chamber 22 are partitioned and formed between the partition wall 19 and the partition wall 20, and the communication chamber 23 is partitioned in the partition wall 20. Formed.

The crankshaft 24 is supported by the partition wall 15 and the partition wall 20 so that rotation through the bearings 25 and 26 is possible. In the crankshaft 24, the in-axis passage 27 penetrates along the central axis 240 of the crankshaft 24. The intraaxial passage 27 communicates with the communication chamber 18 and the communication chamber 23.

The partition wall 14 is supported by a cylindrical first cylinder 28 so as to be able to rotate through the bearing 29, and the partition wall 19 is supported by a cylindrical second cylinder 30. It is supported to rotate through. The first cylinder 28 and the second cylinder 30 are separated in the direction of the center axis 240 of the crankshaft 24 via the annular partition plate 32. The pin 48 is inserted in the opposing end surface of the 1st cylinder 28 and the 2nd cylinder 30 so that the partition board 32 may penetrate. The first cylinder 28 and the second cylinder 30 are integrally connected by the pins 48.

An annular partition plate 33 is interposed between the first cylinder 28 and the tips of the partition walls 14, 15, and an annular partition between the second cylinder 30 and the tips of the partition walls 19, 20. The partition plate 34 is interposed. The suction plate 331 and the discharge port 332 are formed in the partition plate 33, and the suction port 341 and the discharge port 342 are formed in the partition plate 34.

The crankshaft 24 passes through the rings of the partition plates 33 and 34 and the partition plate 32. The partition plate 33 and the partition plate 32 partition the first piston chamber 281 in the first cylinder 28, and the partition plate 34 and the partition plate 32 are the second cylinder 30. The second piston chamber 301 is partitioned inside.

As shown to Fig.2 (a), the cylindrical 1st piston 35 is accommodated in the 1st piston chamber 281 of the 1st cylinder 28. As shown to FIG. The crankshaft 24 passes through the 1st piston 35, and the 1st piston 35 is fitted so that relative rotation to the 1st crank part 241 of the crankshaft 24 is possible. The first piston 35 can move relatively in the first piston chamber 281 in a direction perpendicular to the central axis 240. The first piston 35 divides the inside of the first piston chamber 281 into a first loss 282 and a second loss 283. The 1st cylinder 28 and the 1st piston 35 comprise the 1st suction / discharge mechanism part which performs suction and discharge.

As shown in FIG.2 (b), the cylindrical 2nd piston 36 is accommodated in the 2nd piston chamber 301 of the 2nd cylinder 30. As shown in FIG. The crankshaft 24 passes through the 2nd piston 36, and the 2nd piston 36 is fitted so that relative rotation to the 2nd crank part 242 of the crankshaft 24 is possible. The second piston 36 can move relatively in the second piston chamber 301 in a direction perpendicular to the central axis 240. The second piston 36 divides the inside of the second piston chamber 301 into a first loss 302 and a second loss 303. The 2nd cylinder 30 and the 2nd piston 36 comprise the 2nd suction and discharge mechanism part which performs suction and discharge.

As shown to FIG.2 (a), (b), the phase difference of 180 degrees centering on the center axis | shaft 240 is provided with the 1st crank part 241 and the 2nd crank part 242. As shown to FIG.

The 1st cylinder 28 and the 2nd cylinder 30 are the same size of the same shape, and the outer peripheral surface of the 1st cylinder 28 and the outer peripheral surface of the 2nd cylinder 30 are circumferential surface shape. The rotation axis of the first cylinder 28 and the rotation axis of the second cylinder 30 are on the same axis 47 (hereinafter referred to as the rotation axis 47). The center axis 240 of the crankshaft 24 is eccentric with respect to the rotation axis 47 by the distance r (shown in FIG. 3 (a), (b)).

The first suction / discharge mechanism portion and the second suction / discharge mechanism portion are formed in parallel in the direction of the rotation axis 47. A cylindrical rotor 37 is fitted to each outer circumferential surface of the first cylinder 28 constituting the first suction / discharge mechanism portion and the second cylinder 30 constituting the second suction / discharge mechanism portion.着) The rotor 37 consists of a rotor core 38 and a plurality of permanent magnets 39 embedded in the rotor core 38. Rotation angle position around the rotation axis 47 of the first cylinder 28 formed in the ring of the annular rotor 37 (rotor core 38), and the annular rotor 37 (rotor core ( 38) The rotation angle position centering on the rotation axis 47 of the 2nd cylinder 30 formed in the ring of ()) is shifted by 90 degrees.

As shown in FIG. 1, the rotor core 38 is comprised by laminating | stacking the core board 381 of several sheets of magnetic bodies (electromagnetic steel plate).

The stator 40 is fixed to the inner circumferential surface of the center housing 11.

As shown in Figs. 2 (a) and 2 (b), the stator 40 is formed in the slot 43 between the annular stator core 41 and the teeth 42 arranged in plural on the inner circumference of the stator core 41. Consisting of a winding 44 carried out. As shown in FIG. 1, the stator core 41 is comprised by laminating | stacking the core board 411 of several sheets of magnetic bodies (electromagnetic steel plate).

The stator 40 and the rotor 37 constitute an electric motor M in which the rotor 37 rotates by energization of the windings 44. In accordance with the operation of the electric motor M, the first cylinder 28 and the second cylinder 30 fitted to the rotor 37 rotate integrally in the direction indicated by the arrow R.

The communication port 141 is formed in the partition wall 14 of the front housing 12. The communication port 141 communicates with the motor chamber 45 accommodating the stator 40 and the first suction chamber 16. The communication port 151 is formed in the partition wall 15 of the front housing 12. The communication port 151 communicates with the first discharge chamber 17 and the communication chamber 18.

The communication port 191 is formed in the partition wall 19 of the rear housing 13. The communication port 191 communicates with the motor chamber 45 and the second suction chamber 21. The communication port 201 is formed in the partition wall 20 of the rear housing 13. The communication port 201 communicates with the second discharge chamber 22 and the communication chamber 23.

An introduction port 132 is formed in the end wall 131 of the rear housing 13. The introduction port 132 is connected to an external refrigerant circuit (not shown), and refrigerant (gas) is introduced into the motor chamber 45 through the introduction port 132 from the external refrigerant circuit.

A part of the refrigerant introduced into the motor chamber 45 includes a passage 46 (shown in FIGS. 2A and 2B) and a communication port between the inner circumferential surface of the center housing 11 and the outer circumferential surface of the stator 40. It is introduced into the first suction chamber 16 via 141. The refrigerant in the first suction chamber 16 is sucked into the first piston chamber 281 from the suction port 331 in accordance with the reciprocating motion of the first piston 35. The refrigerant in the first piston chamber 281 is discharged from the discharge port 332 to the first discharge chamber 17 in accordance with the reciprocating motion of the first piston 35. The refrigerant discharged into the first discharge chamber 17 flows into the communication chamber 23 via the communication port 151, the communication chamber 18, and the in-axis passage 27.

The remaining refrigerant introduced into the motor chamber 45 is introduced into the second suction chamber 21 via the communication port 191. The refrigerant in the second suction chamber 21 is sucked into the second piston chamber 301 from the suction port 341 in accordance with the reciprocating motion of the second piston 36. The refrigerant in the second piston chamber 301 is discharged from the discharge port 342 to the second discharge chamber 22 in accordance with the reciprocating motion of the second piston 36. The refrigerant discharged to the second discharge chamber 22 flows out into the communication chamber 23 via the communication port 201.

The coolant in the communication chamber 23 flows out to the external coolant circuit through the discharge port 133 formed on the end wall 131. The coolant flowing out to the external coolant circuit is refluxed into the motor chamber 45 through the introduction port 132.

2 (a) and 2 (b) show the rotation states of the first cylinder 28 and the second cylinder 30 when the rotation angle of the rotor 37 is 0 °.

When the first cylinder 28 and the second cylinder 30 rotate in accordance with the operation of the electric motor M, the first piston 35 moves in the first piston chamber 281 and the second piston 36 moves in the second piston chamber 301.

4A shows the rotational state of the first cylinder 28 and the position of the first piston 35 in the first piston chamber 281 when the rotation angle is 45 °, and FIG. 4A2 shows the rotation. The rotational state of the first cylinder 28 and the position of the first piston 35 in the first piston chamber 281 when the angle is 90 ° are shown. 4 (a3) shows the rotational state of the first cylinder 28 and the position of the first piston 35 in the first piston chamber 281 when the rotation angle is 135 °, and FIG. 4 (a4) shows the rotation. The rotational state of the first cylinder 28 and the position of the first piston 35 in the first piston chamber 281 when the angle is 180 ° are shown.

4 (b1) shows the rotation state of the second cylinder 30 and the position of the second piston 36 in the second piston chamber 301 when the rotation angle is 45 °, and FIG. 4 (b2) shows the rotation. The rotational state of the second cylinder 30 and the position of the second piston 36 in the second piston chamber 301 when the angle is 90 ° are shown. 4 (b3) shows the rotational state of the second cylinder 30 and the position of the second piston 36 in the second piston chamber 301 when the rotation angle is 135 °, and FIG. 4 (b4) shows the rotation. The rotational state of the second cylinder 30 and the position of the second piston 36 in the second piston chamber 301 when the angle is 180 ° are shown.

In the state of FIG. 2 (a) with a rotation angle of 0 °, the refrigerant in the first suction chamber 16 does not flow into the first loss 282 of the first piston chamber 281, and the first piston chamber ( The refrigerant in the second lost 283 of 281 is not discharged to the first discharge chamber 17. In the state of FIG. 2 (b) with a rotation angle of 0 °, the refrigerant in the second suction chamber 21 flows into the first loss 302 of the second piston chamber 301, and thus the second piston chamber 301 The refrigerant in the second loss 303 is discharged to the second discharge chamber 22.

In the state of FIG. 4 (a1) with a rotation angle of 45 °, the refrigerant in the first suction chamber 16 flows into the first loss 282 of the first piston chamber 281, and the first piston chamber 281 is provided. The refrigerant in the second lost 283 of the discharge is discharged to the first discharge chamber 17. In the state of FIG. 4 (b1) having a rotation angle of 45 °, the refrigerant in the second suction chamber 21 flows into the first loss 302 of the second piston chamber 301, and thus, of the second piston chamber 301. The refrigerant in the second loss 303 is discharged to the second discharge chamber 22.

In the state of FIG. 4 (a2) having a rotation angle of 90 °, the refrigerant in the first suction chamber 16 flows into the first loss 282 of the first piston chamber 281, and the first piston chamber 281 is provided. The refrigerant in the second lost 283 of the discharge is discharged to the first discharge chamber 17. In the state of FIG. 4 (b2) having a rotation angle of 90 °, the refrigerant in the second suction chamber 21 does not flow into the first loss 302 of the second piston chamber 301, and the second piston chamber ( The refrigerant in the second loss 303 of the 301 is not discharged to the second discharge chamber 22.

In the state of FIG. 4 (a3) having a rotation angle of 135 °, the refrigerant in the first suction chamber 16 flows into the first loss 282 of the first piston chamber 281 and the first piston chamber 281 is provided. The refrigerant in the second lost 283 of the discharge is discharged to the first discharge chamber 17. In the state of FIG. 4 (b3) having a rotation angle of 135 °, the refrigerant in the second suction chamber 21 flows into the second loss 303 of the second piston chamber 301, thereby The refrigerant in the first loss 302 is discharged to the second discharge chamber 22.

In the state of FIG. 4 (a4) with a rotation angle of 180 °, the refrigerant in the first suction chamber 16 does not flow into the first loss 282 of the first piston chamber 281, and the first piston chamber ( The refrigerant in the second lost 283 of 281 is not discharged to the first discharge chamber 17. In the state of FIG. 4 (b4) having a rotation angle of 180 °, the refrigerant in the second suction chamber 21 flows into the second loss 303 of the second piston chamber 301, and thus The refrigerant in the first loss 302 is discharged to the second discharge chamber 22.

While the first cylinder 28 and the second cylinder 30 are rotated once, the first piston 35 reciprocates once in the first piston chamber 281, and the second piston 36 is second The piston chamber 301 is reciprocated once. The one-way distance of the first piston 35 and the second piston 36 is twice the eccentric distance r.

While the first cylinder 28 and the second cylinder 30 are rotated 180 degrees, the crankshaft 24 rotates 360 degrees about the central axis 240. In short, the crankshaft 24 rotates twice with respect to one rotation of the electric motor M. As shown in FIG.

In the first embodiment, the following effects are obtained.

(1) In the configuration in which the first cylinder 28 and the second cylinder 30 are rotatably connected in the ring of the annular rotor 37, when the electric motor M rotates once, the first cylinder While the 28 and the second cylinder 30 rotate one time, the crankshaft 24 rotates two times. In the conventional electric compressor which directly rotates a crankshaft by an electric motor, a crankshaft rotates one rotation with respect to one rotation of an electric motor. As compared with such a conventional electric compressor, in the electric compressor 10 of this embodiment, the rotation speed of the electric motor M can be reduced by half, and the noise (motor rotation noise) by the rotation of the electric motor M is reduced. Is reduced.

(2) In the motor-driven compressor 10 having two suction / discharge mechanism parts, two discharges are performed by each suction / discharge mechanism part with respect to one rotation of the electric motor M. FIG. Rotation angle position centering on the rotation axis 47 in the first cylinder 28 that accommodates the first piston 35 and in the second cylinder 30 that accommodates the second piston 36. The rotation angle position centering on the rotation axis 47 is shifted by 90 degrees. In this case, the first piston 35 in the first cylinder 28 or the second piston 36 in the second cylinder 30 is reversed by the discharge pressure in the piston chambers 281 and 301. There is a concern.

The configuration in which the rotation angles of the first cylinder 28 and the second cylinder 30 are shifted by 90 degrees is the first piston 35 in the first cylinder 28 and the second piston 36 in the second cylinder 30. Inhibits the reverse operation of

(3) The first discharge chamber 17 and the second discharge chamber 22 communicate with each other via the communication ports 151 and 201, the communication chambers 18 and 23, and the in-axis passage 27. In the configuration in which the first discharge chamber 17 and the second discharge chamber 22 are communicated via the in-axis passage 27, the discharge port for discharging the refrigerant (fluid) in addition to the electric compressor 10 is a discharge port 133. ), The external piping configuration is simplified.

Next, the second embodiment of FIGS. 5 and 6 will be described. The same code | symbol is used for the same structural part as 1st Embodiment, and the detailed description is abbreviate | omitted.

In the motor-driven compressor 10A of the second embodiment, the length L2 of the second cylinder 30A and the second piston 36A in the rotational axis 47 direction is in the rotational axis 47 direction. It is shorter than the length L1 of the 1st cylinder 28 and the 1st piston 35A. As a result, the discharge volume of the second piston chamber 301 becomes smaller than the discharge volume of the first piston chamber 281.

The discharge port 133 formed in the rear housing 13 is formed at a position which is in direct contact with the second discharge chamber 22, and the communication port 202 is provided with the second suction chamber 21 in the partition wall 20. It is formed so that the communication chamber 23 may communicate.

In addition, in this embodiment, as shown to FIG.6 (a), (b), the substantially elliptical 1st piston 35A and the substantially elliptical 2nd piston 36A are used.

The refrigerant introduced into the motor chamber 45 through the introduction port 132 from the external refrigerant circuit is the first suction chamber 16, the first piston chamber 281, the first discharge chamber 17, and the communication chamber 18. And flows into the communication chamber 23 via the in-axis passage 27. The refrigerant in the communication chamber 23 is sucked into the second piston chamber 301 through the communication port 202 and the second suction chamber 21. The refrigerant in the second piston chamber 301 is discharged to the second discharge chamber 22 through the discharge port 342, and the refrigerant in the second discharge chamber 22 is discharged from the discharge port 133 to the external refrigerant circuit. Discharged.

In the second embodiment, the following effects are obtained.

(4) In the motor-driven compressor 10A, since the discharge volume of the second piston chamber 301 is smaller than the discharge volume of the first piston chamber 281, in the first discharge chamber 17, in the shaft passage 27. And the pressure in the second suction chamber 21 is an intermediate pressure between the pressure (discharge pressure) in the second discharge chamber 22 and the pressure (suction pressure) in the first suction chamber 16. In other words, the first discharge chamber 17, the in-axis passage 27, and the second suction chamber 21 are intermediate pressure regions serving as intermediate pressures between the suction pressure and the discharge pressure. For this reason, the fluid leakage from the discharge pressure area | region (2nd discharge chamber 22) by the side of the 2nd suction / discharge mechanism to the suction pressure area | region (1st suction chamber 16) by the side of a 1st suction / discharge mechanism is suppressed. do.

(5) A configuration in which the length L2 of the second cylinder 30A and the second piston 36A is shorter than the length L1 of the first cylinder 28 and the first piston 35A is the second piston chamber. It is easy in making the discharge volume of 301 smaller than the discharge volume of the 1st piston chamber 281.

Next, 3rd Embodiment of FIG.7 (a), (b) is demonstrated. The same code | symbol is used for the same structural part as 1st Embodiment, and the detailed description is abbreviate | omitted.

In the third embodiment, the diameter Q2 of the second piston 36B is smaller than the diameter Q1 of the first piston 35A, and the discharge volume in the second piston chamber 301 is the first piston chamber. It is smaller than the discharge volume in 281.

In 3rd Embodiment, the effect similar to (4) term in 2nd Embodiment is acquired.

Next, 4th Embodiment of FIG.8 (a), (b) is demonstrated. The same code | symbol is used for the same structural part as 1st Embodiment, and the detailed description is abbreviate | omitted.

In 4th Embodiment, the 1st cylinder 28B and the 2nd cylinder 30B of polygonal shape (a regular hexagon in this embodiment) are used. The regular hexagon is adopted in accordance with the number of permanent magnets 39.

The outer circumferential surfaces of the polygonal first cylinders 28B and the second cylinders 30B fitted in the rings of the annular rotor 37 are composed of a plurality of torque receiving planes 49 and 50, and an annular rotor core ( The inner peripheral surface of 38B) (rotor 37) is composed of a plurality of torque transmission planes 51. The torque receiving planes 49 and 50 and the torque transmission plane 51 are opposed to one-to-one. When the 1st cylinder 28B and the 2nd cylinder 30B rotate, the torque transmission plane 51 and the torque receiving planes 49 and 50 are joined, and the torque receiving planes 49 and 50 from the torque transmission plane 51. Torque transmission is achieved.

In the case where the cylinder and the rotor 37 are keyed, there is a risk that the keyway is deformed by the torque, and if so, the backlash becomes large and a noise occurs. When the cylinder is press-fitted into the rotor 37, the piston chambers 281 and 301 may be deformed, and the pistons 35 and 36 are locked in the piston chambers 281 and 301.

In the structure in which the torque transmission plane 51 and the torque receiving planes 49 and 50 are joined, problems such as the occurrence of the above-mentioned joints and locking of the pistons 35 and 36 do not occur.

In the present invention, the following embodiments are also possible.

The crankshaft 24 and the cylindrical first piston 35 and the cylindrical second piston 36 may be integrally formed.

In the fourth embodiment, the shape of the cylinder may be a polygonal shape other than a triangular shape or a hexagon.

The technical idea grasped | ascertained from said embodiment is described below.

(A) The compressor according to claim 1, wherein the rotation angle position of the first cylinder and the rotation angle position of the second cylinder are shifted by 90 degrees about the rotation axis.

Reverse action of the first piston 35 and the second piston 36 is prevented.

10... Motorized compressor. 16... First suction chamber. 17... First discharge chamber. 21... Second suction chamber. 22 ... Second discharge chamber. 24... Crankshaft. 240... Center axis. 27... In-axis passage. 28... The 1st cylinder 28 which comprises a 1st suction and discharge mechanism part. 281... 1st piston chamber. 30 ... The 2nd cylinder which comprises a 2nd suction and discharge mechanism part. 301... 2nd piston chamber. 35... A first piston constituting the first suction / discharge mechanism portion. 36.. A second piston constituting the second suction / discharge mechanism portion. 37... Rotor. 47... Rotation axis. 49, 50... Torque receiving plane. 51... Torque transmission plane. M… Electric motor. L1, L2... Length.

Claims (5)

In a compressor having a piston chamber formed in a rotating cylinder, the piston having a suction / discharge mechanism portion for suctioning and discharging by reciprocating the piston chamber,
The first suction / discharge mechanism portion and the second suction / discharge mechanism portion are formed in parallel in the rotational axis direction of the cylinder, the first suction / discharge mechanism portion includes a first cylinder, and the second suction / discharge mechanism portion is first 2 cylinders, a crankshaft is inserted through the first cylinder and the second cylinder, and a center axis of the crankshaft is eccentric with respect to rotation axes of the first cylinder and the second cylinder. The rotation angle position of the first cylinder about the rotation axis and the rotation angle position of the second cylinder around the rotation axis are shifted,
The cylinder is formed in a ring of an annular rotor constituting an electric motor, and the rotor and the cylinder are connected to be rotatable integrally. The method of claim 1,
The first suction / discharge mechanism portion includes a first suction chamber and a first discharge chamber, and the fluid in the first suction chamber is sucked into the first piston chamber of the first cylinder, and the fluid in the first piston chamber is discharged. Is discharged to the first discharge chamber, and the second suction / discharge mechanism portion includes a second suction chamber and a second discharge chamber, and the fluid in the second suction chamber is transferred to the second piston chamber of the second cylinder. Suction, the fluid in the second piston chamber is discharged to the second discharge chamber, and an in-axis passage is formed through the crankshaft so that the first discharge chamber and the second discharge chamber communicate with each other through the in-axis passage. Compressor. The method of claim 1,
The first suction / discharge mechanism portion includes a first suction chamber and a first discharge chamber, and the fluid in the first suction chamber is sucked into the first piston chamber of the first cylinder, and the fluid in the first piston chamber is discharged. Is discharged to the first discharge chamber, and the second suction / discharge mechanism portion includes a second suction chamber and a second discharge chamber, and the fluid in the second suction chamber is transferred to the second piston chamber of the second cylinder. Suction, the fluid in the second piston chamber is discharged to the second discharge chamber, an in-axis passage is formed through the crankshaft, and the first discharge chamber and the second suction chamber communicate with each other through the in-axis passage. And a discharge volume in the second piston chamber is smaller than a discharge volume in the first piston chamber. The method of claim 3, wherein
The compressor in the rotation axis direction of the second cylinder and the second piston is shorter than the length in the rotation axis direction of the first cylinder and the first piston. The method according to any one of claims 1 to 4,
The cylinder is fitted in a ring of the rotor, the annular rotor has a torque transmission plane on the inner circumferential surface, and the cylinder has a torque receiving plane joined to the torque transmission plane.

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