Rotary machine

Abstract

A rotary machine sucking in working fluid through a suction port into a housing and discharging it through the discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces; first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; and first and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other.

Description

TECHNICAL FIELD

The present invention relates to a rotary machine, more particularly a rotary machine compressing a working fluid and able to rotate by expansion of the fluid. Further, it relates to a rotary machine compressing and pumping a non-compressible fluid and able to rotate by the fluid wherein the volume changes due to an orbiting part as seen in scroll and rolling piston types etc.

BACKGROUND ART

Rotary fluid machines used in vapor compression type refrigeration air-conditioning systems and the like since the past, have been noteworthy for their relatively high efficiency, low vibration, and low noise in comparison to other types of compressors, for example, reciprocating compressors and screw compressors. This is because a scroll compressor, in principle, performs compression operations simultaneously in multiple chambers.

Further, in order to effectively achieve a feeling of heating and a feeling of cooling in air-conditioning systems etc., there has been desired to be able to operate the compressor while maintaining a high efficiency over a wide range from slow to high speeds.

For example, Japanese Unexamined Patent Publication No. 5-332262 discloses a compressor designed to engage two parts having scroll laps and driving both with different motors. International Patent Publication WO 2006/067844 discloses a compressor engaging a part having a scroll lap on both surfaces with two fixed scrolls and driving the former with a motor.

However, the compressor disclosed in Japanese Unexamined Patent Publication No. 5-332262 uses two motors, so its mass is large, a larger size becomes unavoidable, and production costs rise also. Further, driving the two motors used simultaneously is difficult.

On the other hand, in the compressor disclosed in International Patent Publication WO 2006/067844 (W02006/067844-A1), there were the problems that machining of a double surface scroll is difficult and, further, assembly of the component parts is also difficult. Further, this compressor has a structure in which a shaft penetrates through the center of the scroll lap, so the outside circumference and the mass increase and the size becomes large.

SUMMARY OF THE INVENTION

The present invention was proposed to solve the above problems and has as its object to provide a rotary machine aiming at smaller size and lighter weight.

As a means for solving the problem, in the aspect of the invention in claim 1, there is provided a rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces; first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; and first and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other; the first and second rotational units further provided with working chambers, the volumes of the working chambers formed by the first and second rotational units made variable by rotation together with the first and second motor rotors, which render the working fluid sucked in through the suction port a high pressure by reduction of the volumes; and high pressure working fluid being discharged from the working chambers through the discharge port.

According to this, a motor stator having inside surfaces including a step surface designed to enclose the housing interior cavity is provided at the housing inside circumferential surface so as to drive the first and second rotational parts together with the first and second motor rotors at the inside of this inside surface, so a smaller size, lighter weight, and further cost reduction can be realized.

In the aspect of the invention in claim 2, there is provided a rotary machine sucking in working fluid through a suction port into its housing and able to rotate by expansion of the fluid, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces; first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; and first and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other; the first and second rotational units further provided with working chambers, the volumes of the working chambers formed by the first and second rotational units made variable by rotation of the first and second rotational units, which expand the working fluid introduced into the housing; and expansion of the working fluid by the working chambers causing the first and second rotational units and the first and second motor rotors to rotate so as to extract electricity.

According to this, working fluid introduced into the housing is expanded by the working chambers so as to make the first and second motor rotors rotate together with the first and second rotational units and take out electricity, so a smaller size, lighter weight, and further lower costs can be realized.

In the aspect of the invention in claim 3, there is provided the aspect of the invention as set forth in claim 1, wherein the first and second rotational units are first and second rotational units in a scroll type rotary machine, the first and second rotational units provided with a first scroll rotor and a second scroll rotor eccentrically engaging with the first scroll rotor; and the first and second scroll rotors are rotatably supported at the housing by respective bearings adjoining and eccentric to each other, and the first and second scroll rotors are respectively supported through the first and second motor rotors by thrust bearings at the housing in the thrust direction.

According to this, first and second second scroll rotors (61, 71) are driven while engaging with each other inside a motor stator having an inner diameter able to receive the first and second scroll rotors, so a smaller size, lighter weight, and further lower costs can be realized.

In the aspect of the invention as set forth in claim 4, there is provided the aspect of the invention as set forth in claim 1, wherein the first and second rotational unit are first and second rotational units in a scroll type rotary machine, the first and second rotational units provided with a first scroll rotor having a substantially circular end plate part and spiral shaped scroll vane part and a second scroll part having a substantially circular end plate part and spiral shaped scroll vane part; the scroll vane parts of the first scroll rotor and second scroll rotor engage eccentrically with each other to thereby form a plurality of working chambers taking in working fluid and rendering it high pressure between the scroll vane parts; and a high pressure cavity is defined inside of the inside wall at the side opposite to the discharge port in the housing so that a first pressure is applied to either of the end plate parts of the first or second scroll rotor, a second pressure applied to the plurality of the working chambers as a whole being set so as to become smaller than the first pressure so as to eliminate the bearing for receiving the force in the thrust direction for the inside wall of the housing at the side defining the high pressure cavity.

According to this, the bearing in the thrust direction for the inside wall of the housing at the side where the high pressure cavity is defined can be omitted, so the structure can be simplified significantly, contributing to smaller size and lighter weight.

In an aspect of the invention in claim 5, there is provided a rotary piston type rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces; first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; and first and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other; the first and second rotational units provided with first and second rotors respectively arranged between a first side plate and middle plate or between the middle plate and a second side plate through a shaft, first and second cylinders arranged eccentric to the first and second rotors respectively, first and second working chambers respectively formed between the first rotor and first cylinder or between the second rotor and second cylinder, and first and second vanes protruding out from the first and second cylinders toward the first and second rotors in the first and second working chambers so as to abut against the first and second rotors by first and second spring members.

According to this, there can be provided a rolling piston type rotary machine enabling a simplified structure, smaller size, and lighter weight.

In the aspect of the invention as set forth in claim 6, there is provided a swing type rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces; first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; and first and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other; the first and second rotational units provided with first and second rotors respectively arranged between a first side plate and middle plate or between the middle plate and a second side plate through a shaft, first and second cylinders arranged eccentric to the first and second rotors respectively, first and second working chambers respectively formed between the first rotor and first cylinder or between the second rotor and second cylinder, and first and second driving pins provided protruding out from the first and second rotors and coupling the first and second rotors to the first and second cylinders swingingly.

According to this, there can be provided a rolling piston type rotary machine enabling a simplified structure, smaller size, and lighter weight.

In the aspect of the invention as set forth in claim 7, there is provided the invention as set forth in claim 1, wherein the first and second rotational unit are 180 degrees out of phase with each other and are arranged inside of the motor stator in the cavity inside the housing.

According to this, when the first and second rotational units rotate, a dynamic balance of the rotating elements can be achieved, and vibration can be suppressed.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional explanatory view of a scroll type rotary machine of an embodiment of the present invention.

FIG. 2 is a cross-sectional explanatory view showing another embodiment of a scroll rotor in the scroll type rotary machine shown in FIG. 1.

FIG. 3A is a cross-sectional explanatory view of the main parts of the rotary machine shown in FIG. 1 when cut along a line A-A. Along with FIGS. 3B to 3D, it explains the process of the scroll vanes of the first and second scroll rotors compressing a working fluid.

FIG. 3B is a cross-sectional explanatory view of the main parts of the rotary machine shown in FIG. 1 when cut along a line A-A.

FIG. 3C is a cross-sectional explanatory view of the main parts of the rotary machine shown in FIG. 1 when cut along a line A-A.

FIG. 3D is a cross-sectional explanatory view of the main parts of the rotary machine shown in FIG. 1 when cut along a line A-A.

FIG. 4 is a cross-sectional explanatory view of a scroll type rotary machine of another embodiment of the present invention.

FIG. 5 is a cross-sectional explanatory view of a rolling piston type rotary machine of an embodiment of the present invention.

FIG. 6 is a cross-sectional explanatory view of the rolling piston type rotary machine shown in FIG. 5 when cut along a line B-B.

FIG. 7A is a cross-sectional explanatory view of the main parts of the rolling piston type rotary machine shown in FIG. 5 explaining the process of it compressing the working fluid.

FIG. 7B is a cross-sectional explanatory view of the main parts of the rolling piston type rotary machine shown in FIG. 5 explaining the process of it compressing the working fluid.

FIG. 7C is a cross-sectional explanatory view of the main parts of the rolling piston type rotary machine shown in FIG. 5 explaining the process of it compressing the working fluid.

FIG. 8 is a cross-sectional explanatory view of a swing type rotary machine of an embodiment of the present invention.

FIG. 9 is a cross-sectional explanatory view of the swing type rotary machine shown in FIG. 8 when cut along a line C-C.

FIG. 10A is a cross-sectional explanatory view of the main parts of the swing type rotary machine shown in FIG. 8 explaining the process of it compressing the working fluid.

FIG. 10B is a cross-sectional explanatory view of the main parts of the swing type rotary machine shown in FIG. 8 explaining the process of it compressing the working fluid.

FIG. 10C is a cross-sectional explanatory view of the main parts of the swing type rotary machine shown in FIG. 8 explaining the process of it compressing the working fluid.

DESCRIPTION OF EMBODIMENTS

Below, embodiments of the rotary machine of the present invention will be explained.

First Embodiment

FIG. 1 is a cross-sectional view showing the overall configuration of a compressor when using a hermetic scroll type rotary machine as a compressor for an air-conditioning machine. This scroll type rotary machine 1 is a rotary machine that sucks in working fluid through a suction port 14 into its housing 2 to render it a high pressurize and discharges it through a discharge port 15.

This rotary machine 1 is provided with a motor stator 3 provided at an inside circumferential surface of the housing 2 and having inside surfaces, which include a step surface S, designed to enclose a housing interior cavity by its inside surfaces, first and second motor rotors 4, 5 arranged at the insides of the inside surfaces of the motor stator 3 separated at the step surface S, and first and second rotational units 6, 7, the first and second rotational units 6, 7 coupled to the first and second motor rotors 4, 5 respectively and the first and second rotational units 6, 7 supported by the bearings 8, 8′ at the housing 2 adjoiningly and eccentrically to each other.

Further, the first and second rotational units 6, 7 are provided with working chambers 12 having volumes changed by making the first and second rotational units 6, 7 rotate along with the first and second motor rotors 4, 5 and rendering working fluid that is sucked in through the suction port 14 to the housing 2 a high pressure by reducing the volumes.

At the inside surfaces of the motor stator 3, the inside surfaces facing the first and second rotational units 6, 7 are connected at the step surface S, whereby equal sized first and second cylindrical cavities 31, 32 are formed. The first and second rotational units 6, 7 have axial centers eccentric with each other and can rotate about their corresponding axial centers.

The first and second rotational units 6, 7 are provided with a first scroll rotor 61 and a second scroll rotor 71 eccentrically engaging with the first scroll rotor 61. The first scroll rotor 61 has a substantially circular end plate part 61a and a spiral shaped scroll vane part 61c. The second scroll rotor 71 has a substantially circular end plate part 71a and a substantially same shaped spiral shaped scroll vane part 71c engaging with the scroll vane part 61c of the first scroll rotor 61. By eccentrically engaging the scroll vane parts 61c, 71c to each other, a plurality of crescent shaped working chambers 12 taking in and compressing working fluid are formed between the spiral shaped scroll vane parts 61c, 71c.

The first and second scroll rotors 61, 71 are supported rotatably with respect to the housing 2 by bearings 8, 8′ respectively and are supported in the thrust direction (direction of force acting in the axial direction) by thrust bearings 10, 11, 10′, 11′ by interposing the first and second motor rotors 5, 7 respectively.

At one surface of the end plate part 61a of the first scroll rotor 61, there is formed a scroll vane part 61c. At the other surface of the end plate part 61a, there is provided a substantially cylindrical boss part 61b protruding toward a cover 21 of the housing 2. A holding part 21a is protrudes out at the cover 21 of the housing 2. The first scroll rotor 61 has the cylindrical boss part 61b inserted into the holding part 21a of the housing 2 whereby it is rotatably supported by the bearing 8.

At one surface of the end plate part 71a of the second scroll rotor 71, there is formed a scroll vane part 71c. At the other surface of the end plate part 71a, there is provided a protruding boss part 71b. The second scroll rotor 71 has the boss part 71b inserted into the holding part 22a protruding out from the bottom 22 side of the housing 2, whereby it is rotatably supported by the bearing 8′.

The first motor rotor 4 is fixed to the end plate part 61a where of the first scroll rotor 61 at the side where the boss part 61b is formed. A permanent magnet 41 is set at the first motor rotor 4. The first motor rotor 4 is supported in the thrust direction by the cover 21 of the housing 2 and the thrust bearings 10, 11 without hinderance to rotation.

Further, the second motor rotor 5 is fixed to the end plate part 71a of the second scroll rotor 71 at the side where boss part 71b is formed. A permanent magnet 51 is set at the second motor rotor 5. Further, the second motor rotor 5 is supported by the bottom 22 of the housing 2 and the thrust bearings 10′, 11′ without hinderance to rotation.

The first and second scroll rotors 61, 71 have scroll vane parts 61c, 71c eccentrically engaging with each other, whereby the spiral shaped vane parts 61c, 71c between them form a plurality of crescent shaped working chambers 12 (explained later) taking in and compressing working fluid. At the center region of the first and second scroll rotors 61, 71, there is formed a high pressure working chamber (not shown) where the pressure of the compressed working fluid is the highest. At the boss part 61b at the first scroll rotor 61, there is formed a discharge port 13 for discharging the compressed working fluid from the high pressure working chamber.

At the housing 2 of the scroll type rotary machine 1, a suction port 14 is formed at the bottom 22 side for taking in working fluid to the housing 2. At the center of the cover 21 of the housing 2, a discharge port 15 is formed. The suction port 14 is connected to the working chambers 12 formed between the spiral shaped scroll vane parts 61c, 71c of the first and second scroll rotors 61, 71.

The discharge port 15 at the center of the cover 21 of the housing 2 is connected with the discharge port 13 of the boss part 61b at the first scroll rotor 61.

At the passage from the discharge port 13 to the discharge port 15, reed valve 16 is interposed biased so as to normally block the passage with a spring member 16s.

If the pressure of working fluid at the high pressure working chamber existing at the center region of the first and second scroll rotors 61, 71 exceeds a predetermined pressure, it becomes larger than the biasing force from the spring member 16c at the the reed valve 16. Therefore, the passage from the discharge port 13 to the discharge port 15 is opened up, and high pressure working fluid flows out from the discharge port 15.

At the bottom 22 of the housing 2, there is interposed a hermetic terminal 17. Electricity is fed through the hermetic terminal 17 from an external controller (not shown) to a coil 3c of the motor stator 3.

The reed valve 16 can also be replaced with a poppet valve 18 such as shown in FIG. 2. The poppet valve 18 openably blocks the passage from the discharge port 13 to the discharge port 15 and is configured from a valve element 18a, spring member 18b, and spring holder 18c.

Next, the action of the scroll type rotary machine 1 of the present invention will be explained.

If electricity is fed to the motor stator 3 inside the housing 2 through the hermetic terminal 17 from the external controller, the motor stator 3 is magnetized, whereby the first and second motor rotors 4, 5 set with the permanent magnets 41, 51 are made to rotate. The first and second motor rotors 4, 5 are coupled with the first and second scroll rotors 61, 71, so these rotate as one unit. The first and second scroll rotors 61, 71 are supported respectively by the bearings 8, 8′ eccentric to the housing 2, so the scroll vane parts 61c, 71c rotate eccentrically while engaging with each other centered about these bearings 8, 8′.

When the scroll type rotary machine 1 is in operation, the first and second scroll rotors 61, 71 rotate while the scroll vane parts 61c, 71c engage. Due to this, working fluid that entered the housing interior cavity from the suction port 14 at the bottom 22 of the housing 2 spreads to the working chambers 12 between the spiral shaped vane parts 61c, 71c. Then, working fluid is gradually fed to the scroll center. The compressed working fluid from the high pressure working chamber at the center region of the first and second scroll rotors 61, 71 pushes through the reed valve 16, passes through the discharge port 13, and is discharged outside from the discharge port 15 at the center of the cover 21 of the housing 2.

In the above way, the scroll type rotary machine 1 is configured from the first and second motor rotors integral with the first and second scroll rotors 61, 71 and a motor stator 3 having first and second cylindrical cavities 31, 32 eccentric to each other, so smaller size, lighter weight, and further lower costs can be realized.

The process of compressing the working fluid will be explained with reference to FIG. 3A to FIG. 3D. FIG. 3A to FIG. 3D show an engaged state of the scroll vane parts 61c, 71c of the first and second scroll rotors 61, 71 of the rotary machine shown in FIG. 1 when cut along the line A-A.

When the scroll vane parts 61c, 71c engage and rotate, the rotational position of the scroll vane part 61c shown at FIG. 3A (hereinafter, referred to as “phase”) is defined as “0” degree. At this time, the scroll vane part 71c of the second scroll rotor 71 is 180 degrees out of phase from the scroll vane part 61c of the first scroll rotor 61.

Below, in FIG. 3B, the phase of the vane part 61c of the first scroll rotor 61 is shown to be 90 degrees, in FIG. 3C, the phase of the vane part 61c of the first scroll rotor 61 is shown to be 180 degrees, and in FIG. 3D, the phase of the vane part 61c of the first scroll rotor 61 is shown to be 270 degrees.

In the engaged state of the scroll vane parts 61c, 61c shown in FIG. 3A, the working fluid is sealed by the working chambers 12α1, 12β1. From this state, the first and second scroll rotors 61, 71 rotate integrally along with the rotation of the first and second motor rotors 4, 5. The working chamber 12α1 becomes narrower in the order of 12α1→12α2→12α3→12α4→12α5, whereby the working fluid is compressed and rendered a high pressure. When the working chamber 12 formed between the scroll vane parts 61c, 71c reaches the center working chamber 12γ, it reaches a position where it is able to connect with the discharge port 13 (the reed valve 16 is in a closed state). Further, the working chamber 12 becomes narrower in the order of the working chamber 12δ→working chamber 12ε. If becoming higher than a predetermined pressure, the fluid pushes through the reed valve 16 at the discharge port 13 and is discharged from the discharge port 15 at the center of the cover 21 of the housing 2 to the outside.

On the other hand, the working chamber 1231 also similarly becomes narrower in the order of 12β1→12β2→12β3→12β4→12β5, whereby the working fluid is compressed and rendered a high pressure. If the working chamber 12 formed between the scroll vane parts 61c, 71c becomes the central working chamber 12γ, it reaches a position where it is able to connect with the discharge port 13. Further, the working chamber 12 becomes narrower in the order of working chamber 12δ→working chamber 12ε, where if the working fluid has a pressure higher than a predetermined pressure, it pushes through the reed valve 16 at the discharge port 13 and is discharged from the discharge port 15 at the center of the cover 21 of the housing 2 to the outside.

Regarding the forces the working fluid of the working chambers 12 applies to the first and second scroll rotors 61, 71, the force in the radial direction is supported by the bearing 8, and the force in the thrust direction is supported by the thrust bearings 10, 11, so the first and second motor rotors 4, 5 and the first and second scroll rotors 61, 71 operate without hinderance to rotation and execute the above mentioned process of compressing the working fluid.

The scroll type rotary machine 1 performs a rotation operation in a state where the scroll vane parts 61c, 71c are mutually 180 degree out of phase, so a dynamic balance in the rotation operation can be achieved and vibration can be suppressed.

Second Embodiment

A second embodiment of the scroll type rotary machine 1 of the present invention will be explained below.

In the scroll type rotary machine 1 shown in FIG. 1, among the forces applied to the first and second scroll rotor 61, 71, the force in the radial direction is supported by the bearings 8, 8′ and the force in the thrust direction is supported by the thrust bearings 10, 11. On the other hand, in the second embodiment of the scroll type rotary machine 1 shown in FIG. 4, the thrust bearings 10′, 11′ between the second motor rotor 5 rotating integrally with the second scroll rotor 71 and the bottom 22 of the housing 2 are omitted.

In the scroll type rotary machine 1 shown in FIG. 4, a high pressure cavity 71d for forming a high pressure atmosphere is defined between the boss part 71b, which is rotatably supporting the second scroll rotor 71 at the bottom 22 of the housing 2, and the bottom 22. The high pressure cavity 71d is connected through the passage 71e to the center working chamber of the plurality of working chambers 12 formed between the scroll vane parts 61c, 71d by the highly pressurized working fluid. Due to this, highly pressurized working fluid flows into the high pressure cavity 71d, and a first pressure Fb (in the left direction at FIG. 4) acts on the end plate part 71a.

On the other hand, opposing the pressure Fb acting on the end plate part 71a, a second pressure F12 (in the right direction at FIG. 4), which is the total pressure from the working fluid, acts on all the working chambers 12 formed between the spiral shaped scroll vanes 61c, 71c of the first and second scroll rotor 61, 71. Therefore, if first pressure Fb>second pressure F12 is satisfied, even if the thrust bearings 10′, 11′ between the second motor rotor 5 and bottom 22 of the housing 2 are omitted, the first and second motor rotors 4, 5 and first and second scroll rotors 61, 71 rotate without hinderance to rotation.

By setting the first pressure Fb so as to exceed the second pressure F12, the thrust bearings 10′, 11′ between the second motor rotor 5 and bottom 22 of the housing 2 can be made omittable and the structure can be simplified significantly, allowing costs to be cut.

Third Embodiment

In the above, an explanation was made of an embodiment applied to a scroll type rotary machine as an air-conditioner compressor. The present invention can be worked as a rolling piston type rotary machine.

FIG. 5 is a cross-sectional explanatory view schematically showing a rolling piston type rotary machine 100 as a third embodiment. In this rolling piston type rotary machine 100, component substantially the same as the components in the above-mentioned scroll type rotary machine 1 are explained assigned the same reference numerals.

In this rotary machine 100 as well, the housing 2 has an opening sealed by a cover 21. At the inside wall of the housing 2, there is arranged a motor stator 3 having inside surfaces including a step surface designed to enclose the housing interior cavity by the inside surface.

A shaft 101 is inserted in the inside cavity of the motor stator 3 through the cover 21 of the housing 2 to the bottom 22 and is supported by the housing 2. At the shaft 101, first and second rotors 6 operating at mutually different phases are attached.

The first rotational unit 6 is provided with a first rotor 104a arranged between the middle plate 102 and first side plate 103a through the shaft 101 and with a first cylinder 105a arranged eccentric to the first rotor 104a. At the first cylinder 105a, there is attached a motor rotor 4 rotating with the first cylinder 105a. At the motor rotor 4, a permanent magnet 41 is set.

A first side plate 103a is rotatably supported by a bearing 106 at a holding part 21a protruding out from the cover 21 of the housing 2 eccentric to the axial center of the shaft 101. The first side plate 103a and first rotor 104a are rotatably coupled by a driving pin 107 embedded in the first side plate 103a through a depression portion (groove) 108 formed at the first rotor 104a side.

At a crescent shaped first working chamber 109a formed between the first rotor 104a and first cylinder 105a, a first vane 111a protrudes out by a first spring member 110a from a first cylinder 105a toward the first rotor 104a. The first vane 111a abuts against the first rotor 104a (refer to FIG. 6).

On the other hand, the second rotational unit 7 is provided with a second rotor 104b arranged between the middle plate 102 and second side plate 103b through the shaft 101 and with a second cylinder 105b arranged eccentric to the second rotor 104a. At the second cylinder 105b, there is attached a motor rotor 5 rotating with the second cylinder 105b. At the motor rotor 5, a permanent magnet 51 is set.

The second side plate 103b is rotatably supported by a bearing 106′ at a holding part 22a protruding out from the bottom 22 of the housing 2 eccentric to the axial center of the shaft 101. The second side plate 103b and second rotor 104b are coupled by a driving pin 107′ embedded in the second side plate 103b through a spot facing portion 108′ formed at the second rotor 104b side.

At the crescent shaped second working chamber 109b formed between the second rotor 104b and second cylinder 105b, a second vane 111b protrudes out by a second spring member 110b from the second cylinder 105b toward the second rotor 104b. The second vane 111b abuts against the second rotor 104b.

In the above rotary machine 100, the shaft 101 is inserted toward the bottom 22 through the housing 2 by which it is supported. To suck in, compress, and discharge the low pressure working fluid, the center of the cover 21 of the housing 2 has fit in it a suction pipe 112 having a suction port 14 for introducing low pressure working fluid into the housing 2. Further, the suction pipe 112 is connected with an introducing cavity 113 formed along the axial center of the shaft 101.

Next, the introducing cavity 113 of the shaft 101 is formed so as to reach, through the suction passages 114a, 114b running through the shaft 101 in the radial direction and through the suction passages 115a, 115b formed at the first and second rotors 104a, 104b, the crescent shaped first and second working chambers 109a, 109b formed between the first and second rotors 104a, 104b and first and second cylinders 105a, 105b. These form low pressure suction passages with respect to the first and second rotational units 6, 7.

The crescent shaped first and second working chambers 109a, 109b formed between the first and second rotors 104a, 104b and first and second cylinders 105a, 105b are formed so as to reach, through the high pressure passages 116a, 116b running through the first and second cylinder 105a, 105b and through the high pressure passages 117a, 117b running through the first and second side plates 103a, 103b, the discharge chamber 118 inside the housing 2. These form a high pressure discharge passage with respect to the first and second rotational units 6, 7. At the first and second side plates 103a, 103b, reed valves 119 are provided shutting and opening the passages leading to the discharge chamber 118. The reed valves 119 open and close under bias from the plate springs 119s. The discharge chamber 118 inside the housing 2 discharges high pressure fluid through the discharge port 15 provided at the bottom 22 of the housing 2.

Next, the operations of such a rotary machine 100 will be schematically explained based on FIG. 6 and FIG. 7A to FIG. 7C. The operations of only the first rotational unit 6 will be explained. Operations of the second rotational unit 7 are performed similarly at a different phase (180 degrees), so explanations thereof are omitted.

If the motor stator 3 is energized, the motor stator 3 is magnetized, and the first motor rotor 4 where the permanent magnet 41 is set and first side plate 103a and first cylinder 105a rotate. The first side plate 103a and first rotor 104a are coupled through the driving pin 107 and depression portion 108, so the first rotor 104a rotates about the central axis X1 of the shaft 101. The first motor rotor 4 and the first side plate 103a and first cylinder 105a rotate about the center axis X2, different from the central axis X1 of the shaft 101, so the first cylinder 105a rotates around the first rotor 104a.

If the first cylinder 105a rotates, at the first working chamber 109a between the first rotor 104a and first cylinder 105a, one of the volumes that are defined by the first vane 111a protruding out through the first spring member 110a is increased. Due to this, the working fluid is sucked in through the suction passage 114a of the shaft 101 and the suction passage 115a of the first rotor 104a into the first working chamber 109a.

On the other hand, the other volume defined by the first vane 111a is reduced, whereby the working fluid is made a high pressure. Therefore, the working fluid travels from the first working chamber 109a through the high pressure passage 116a of the first cylinder 105a and high pressure passage 117a of the first side plate 103a, pushes through the reed valve 119, and reaches the discharge chamber 118 inside the housing 2. The working fluid can be discharged as high pressure fluid through the discharge port 15 provided at the bottom 22 of the housing 2.

The second rotational unit 7 is arranged at the interior of the motor stator 3 in the cavity inside the housing 2 out of phase (by 180 degrees) with the first rotational unit 6, so when rotating, a dynamic balance of the rotational elements can be achieved and vibration can be suppressed.

Such a rotary machine 100 is configured from one motor stator 3 and first and second rotational units 6, 7 provided adjoining each other 180 degrees out of phase and eccentric to the shaft 101, so the structure can be made a smaller size and be given a lighter weight, and further lower cost can be realized.

Fourth Embodiment

The present invention can be worked as a swing type rotary machine 200 shown in FIG. 8.

In such a rotary machine 200, components substantially the same as the components in the above-mentioned scroll type rotary machine 1 and rolling piston type rotary machine 100 are explained assigned the same reference numerals.

That is, in the rotary machine 200 as well, the housing 2 has an opening that is sealed by a cover 21. At the inside wall of the housing 2, there is arranged a motor stator 3 having inside surfaces including a step surface designed to enclose the housing interior cavity by the inside surface. A shaft 101 is inserted in the inside cavity of the motor stator 3 through the cover 21 of the housing 2 to the bottom 22 and is supported by the housing 2. At the inside cavity of the motor stator 3, there are provided first and second rotational units 6, 7 arranged adjoiningly and eccentrically 180 degrees out of phase from each other. The space therebetween is divided by a middle plate 102.

The first rotational unit 6 is provided with a first rotor 104a arranged between the middle plate 102 and first side plate 103a through the shaft 101 and with a first cylinder 105a arranged eccentric to the first rotor 104a. At the first cylinder 105a, there is attached a motor rotor 4 rotating with the first cylinder 105a. At the motor rotor 4, a permanent magnet 41 is set.

A driving pin 201 (hereinafter, referred to as a “blade 201”) protruding out from the first rotor 104a is swingingly fit to the first cylinder 105a and swingingly couples the first rotor 104a to the first cylinder 105a.

The first side plate 103a is rotatably supported by a bearing 106 on a holding part 21a (eccentric to the shaft 101) protruding out from the cover 21 of the housing 2. Between the first rotor 104a and first cylinder 105a, there is formed a crescent shaped first working chamber 109a. The first working chamber 109a is defined by the blade 201 protruding out from the first rotor 104a (refer to FIG. 9).

On the other hand, the second rotational unit 7 is provided with a second rotor 104b arranged between the middle plate 102 and second side plate 103b through the shaft 101 and with a second cylinder 105b arranged eccentric to the second rotor 104b. At the second cylinder 105b, there is attached the motor rotor 5 rotating with the second cylinder 105b.

The blade 201 protruding out from the second rotor 104b is swingingly fit from the second rotor 104b into the second cylinder 105b and swingingly couples the second rotor 104b to the second cylinder 105b.

The second side plate 103b is rotatably supported by the bearing 106′ at the holding part 22a (eccentric to the shaft 101) protruding out from the bottom 22 of the housing 2.

In such a rotary machine 200, the shaft 101 is inserted toward the bottom 22 through the housing 2 by which it is supported. To suck in, compress, and discharge the low pressure working fluid, there is fit into the center of the cover 21 of the housing 2, a suction pipe 112 having a suction port 14 for introducing low pressure working fluid into the housing 2. Further, the suction pipe 112 is connected with an introducing cavity 113 formed along the axial center of the shaft 101.

Next, the introducing cavity 113 of the shaft 101 is formed so as to reach, through the suction passages 114a, 114b running through the shaft 101 in the radial direction and through the suction passages 115a, 115b formed at the first and second rotor 104a, 104b, the crescent shaped first and second working chambers 119a, 119b formed between the first and second rotors 104a, 104b and the first and second cylinders 105a, 105b. These form low pressure suction passages with respect to the first and second rotational units 6, 7.

The crescent shaped first and second working chambers 109a, 109b formed between the first and second rotors 104a, 104b and the first and second cylinders 105a, 105b are formed so as to reach, through the high pressure passages 116a, 116b running through the first and second cylinders 105a, 105b and through the high pressure passages 116a, 117b running through the first and second side plates 103a, 103b, the discharge chamber 118 inside the housing 2. These form high pressure discharge passages with respect to the first and second rotational units 6, 7. At the first and second side plates 103a, 103b, there are provided reed valves 119 shutting and opening the passages leading to the discharge chamber 118. The reed valves 119 open and close under bias from spring plates 119s. The discharge chamber 118 inside the housing 2 discharges high pressure fluid through the discharge port 15 provided at the bottom 22 of the housing 2.

Next, the operations for such a rotary machine 200 will be schematically explained based on FIG. 9 and FIG. 10A to FIG. 10C. The operations for only the first rotational unit 6 will be explained. Operations of the second rotational unit 7 are performed similarly at a different phase (180 degrees), so explanations thereof are omitted.

If the motor stator 3 is energized, the motor stator 3 is magnetized, and the first motor rotor 4 where the permanent magnet 41 is set and the first side plate 103a and first cylinder 105a rotate. The first rotor 104a is swingingly coupled to the first cylinder 105a through the blade 201. Therefore, the first rotor 104a rotates together about the center axis X1 of the shaft 101.

The first motor rotor 4 and the first side plate 103a and first cylinder 105a rotate about the center axis X2, different from the center axis X1 of the shaft 101. The first rotor 104a rotates together with the first cylinder 105a while swinging with respect the first cylinder 105a through the blade 201, so the first cylinder 105a rotates around the first rotor 104a.

Due to this, at the working chamber 109a between the first rotor 104a and first cylinder 105a, one of the volumes that are defined by the blade 201 is increased, whereby the working fluid is sucked in through the suction passage 114a of the shaft 101 and the suction passage 115a of the first rotor 104a into the working chamber 109a. The other volume defined by the blade 201 is reduced, causing a high pressure in the working fluid, which travels from the working chamber 109a through the high pressure passage 116a of the first cylinder 105a and the high pressure passage 117a of the first side plate 103a, pushes through the reed valve 119, and reaches the discharge chamber 118 inside the housing 2. The working fluid can be discharged as high pressure fluid through the discharge port 115 provided at the bottom 22 of the housing 2.

The second rotational unit 7 is arranged at the interior of the motor stator 3 in the cavity inside the housing out of phase (by 180 degrees) with the first rotational unit 6, so when in rotation, dynamic balance of the rotational elements can be achieved and vibration can be suppressed.

Such a rotary machine 200 is configured from one motor stator 3 and first and second rotational units 6, 7 installed adjoiningly each other 180 degrees out of phase and eccentric to the shaft 101, so the structure can be made a smaller size and be given a lighter weight, and further lower cost can be realized.

The rotary machine of the present invention was explained as a compressor in the embodiments, however, the rotary machine of the present invention can also be made to operate as a generator converting the energy of high pressure working fluid into electric energy for extraction.

For example, the scroll type rotary machine 1 of the first embodiment can also be operated, with the reed valves 16 and spring members 16s removed, with the discharge port 15 acting as an inflow port for high pressure working fluid, and with the suction port 14 acting as an outlet for low pressure working fluid.

In a scroll type rotary machine 1 in this case, the high pressure working fluid introduced from the discharge port 15 induces rotation of the first and second scroll rotors 61, 71. At the working chambers 12 formed between the scroll vane parts 61c, 71c, the working fluid is made a low pressure working fluid while expanding from the center working chamber 12 to the outer working chambers 12 and is discharged from the suction port 14.

At such a time, the first and second motor rotors 4, 5 rotate by the rotation of the first and second scroll rotors 61, 71, generating in the coil 3c at the motor stator 3 an induced current which can be extracted as electricity from the hermetic terminal 17 at the bottom 22 of the housing 2.

Claims

1. A rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces, which include a step surface, designed to enclose a housing interior cavity by the inside surfaces;first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; andfirst and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other;the first and second rotational units further provided with working chambers, the volumes of the working chambers formed by the first and second rotational units made variable by rotation together with the first and second motor rotors, which render the working fluid sucked in through the suction port a high pressure by reduction of the volumes; andhigh pressure working fluid being discharged from the working chambers through the discharge port.

2. A rotary machine sucking in working fluid through a suction port into its housing and able to rotate by expansion of the fluid, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces which include a step surface designed to enclose a housing interior cavity by the inside surfaces;first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; andfirst and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other;the first and second rotational units further provided with working chambers, the volumes of the working chambers formed by the first and second rotational units made variable by rotation of the first and second rotational units, which expand the working fluid introduced into the housing; andexpansion of the working fluid by the working chambers causing the first and second rotational units and the first and second motor rotors to rotate so as to extract electricity.

3. A rotary machine as set forth in claim 1, wherein the first and second rotational units are first and second rotational units in a scroll type rotary machine, the first and second rotational units provided with a first scroll rotor and a second scroll rotor eccentrically engaging with the first scroll rotor; and the first and second scroll rotors are rotatably supported at the housing by respective bearings adjoining and eccentric to each other, and the first and second scroll rotors are respectively supported through the first and second motor rotors by thrust bearings at the housing in the thrust direction.

4. A rotary machine as set forth in claim 1, wherein the first and second rotational unit are first and second rotational units in a scroll type rotary machine, the first and second rotational units provided with a first scroll rotor having a substantially circular end plate part and spiral shaped scroll vane part and a second scroll part having a substantially circular end plate part and spiral shaped scroll vane part; the scroll vane parts of the first scroll rotor and second scroll rotor engage eccentrically with each other to thereby form a plurality of working chambers taking in working fluid and rendering it high pressure between the scroll vane parts; anda high pressure cavity is defined inside of the inside wall at the side opposite to the discharge port in the housing so that a first pressure is applied to either of the end plate parts of the first or second scroll rotor, a second pressure applied to the plurality of the working chambers as a whole being set so as to become smaller than the first pressure so as to eliminate the bearing for receiving the force in the thrust direction for the inside wall of the housing at the side defining the high pressure cavity.

5. A rotary piston type rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces, which include a step surface, designed to enclose a housing interior cavity by the inside surfaces;first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; andfirst and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other;the first and second rotational units provided with first and second rotors respectively arranged between a first side plate and middle plate or between the middle plate and a second side plate through a shaft,first and second cylinders arranged eccentric to the first and second rotors respectively,first and second working chambers respectively formed between the first rotor and first cylinder or between the second rotor and second cylinder, andfirst and second vanes protruding out from the first and second cylinders toward the first and second rotors in the first and second working chambers so as to abut against the first and second rotors by first and second spring members.

6. A swing type rotary machine sucking in working fluid through a suction port into its housing to render it a high pressure and discharging it through a discharge port, provided with a motor stator provided at an inside circumferential surface of the housing and having inside surfaces, which include a step surface, designed to enclose a housing interior cavity by the inside surfaces;first and second motor rotors arranged at the insides of the inside surfaces separated by the step surface of the motor stator; andfirst and second rotational units, the first and second rotational units coupled to the first and second motor rotors respectively, and the first and second rotational units supported at the housing adjoiningly and eccentrically to each other;the first and second rotational units provided with first and second rotors respectively arranged between a first side plate and middle plate or between the middle plate and a second side plate through a shaft,first and second cylinders arranged eccentric to the first and second rotors respectively,first and second working chambers respectively formed between the first rotor and first cylinder or between the second rotor and second cylinder, andfirst and second driving pins provided protruding out from the first and second rotors and coupling the first and second rotors to the first and second cylinders swingingly.

7. A rotary machine as set forth in claim 1, wherein the first and second rotational unit are 180 degrees out of phase with each other and are arranged inside of the motor stator in the cavity inside the housing.