KR20170098265A - Rotating cylinder type compressor - Google Patents

Abstract

The cylinder rotary compressor includes a cylindrical cylinder 21 rotating around the center axis C1 and a cylindrical first rotor rotating around the eccentric axis C2 eccentric to the center axis C1 of the cylinder 21 22a, a second rotor 22b, a shaft 24, a first vane 23a, and a second vane 23b. The first vane 23a is slidably fitted in the first groove portion 222a formed in the first rotor 22a to divide the first compression chamber Va. The second vane 23b is slidably fitted in the second groove portion 222b formed in the second rotor 22b to divide the second compression chamber Vb. The first rotor 22a and the second rotor 22b are arranged in the direction of the center axis C1 of the cylinder 21.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a rotary compressor,

The present application is based on Japanese Patent Application No. 2015-66056, filed on March 27, 2015, the content of which is incorporated herein by reference.

The present disclosure relates to a cylinder rotary compressor for rotating a cylinder forming a compression chamber therein.

BACKGROUND ART [0002] Conventionally, there is known a cylinder rotation type compressor which compresses and discharges a fluid by changing the volume of a compression chamber by rotating a cylinder forming a compression chamber therein.

For example, Patent Document 1 discloses a sliding type portable electronic device that is slidable by a cylindrical cylinder integrally formed with a rotor of a motor base (electric motor portion), a cylindrical rotor disposed inside the cylinder, and a groove portion (slit portion) And a plate-shaped vane separating the compression chamber by being inserted into the compression chamber.

In this kind of the cylinder-rotation type compressor, the cylinder and the rotor are interlocked and rotated by different rotation shafts to displace the vanes, thereby changing the volume of the compression chambers. Further, in the cylinder rotary compressor of Patent Document 1, the compression mechanism is disposed on the inner circumferential side of the electric motor portion, thereby achieving downsizing of the compressor as a whole.

Patent Document 1: Japanese Patent Application Laid-Open No. 6-67735

As means for increasing the discharge capacity of the cylinder rotary compressor of Patent Document 1, a means for expanding the outer diameter (inner diameter of the cylinder) of the compression chamber to expand the capacity (discharge capacity) of the compression chamber is considered.

However, if the inner diameter of the cylinder is enlarged to increase the discharge capacity, the outer diameter of the electric motor portion disposed on the outer peripheral side of the cylinder is also increased, so that it is difficult to obtain the miniaturization effect of the compressor as a whole. Further, if the discharge capacity is enlarged, the fluctuation of the torque at the time of operation of the compressor also increases, which causes noise and vibration of the compressor as a whole.

It is an object of the present invention to provide a cylinder rotation type compressor capable of enlarging the capacity of a compression chamber without causing enlargement in the radial direction.

In one aspect of the present disclosure, a cylinder-rotating compressor includes: a cylindrical cylinder rotating about a central axis; A cylindrical first rotor and a second rotor disposed inside the cylinder and rotating about an eccentric shaft eccentric to the central axis of the cylinder; A shaft rotatably supporting the first rotor and the second rotor; A first vane which is slidably fitted in a first groove formed in the first rotor and which defines a first compression chamber formed between an outer circumferential surface of the first rotor and an inner circumferential surface of the cylinder; And a second vane that is slidably fitted in a second groove formed in the second rotor to define a second compression chamber formed between the outer circumferential surface of the second rotor and the inner circumferential surface of the cylinder. The first rotor and the second rotor are arranged in the center axis direction of the cylinder.

According to this, since the first rotor and the second rotor are provided, the first compression chamber and the second compression chamber can be formed. Therefore, the total capacity (total discharge capacity) of the first compression chamber and the second compression chamber can be easily expanded. Further, since the first rotor and the second rotor are arranged in line in the central axis direction of the cylinder, the total discharge capacity can be increased without enlarging the outer diameter of the cylinder.

As a result, it is possible to provide a cylinder rotation type compressor capable of expanding the capacity of the compression chamber without increasing the size in the radial direction.

The eccentric shaft of the first rotor and the eccentric shaft of the second rotor may be coaxially arranged. According to this structure, it is not necessary to form a portion having another eccentric shaft in the shaft, so that the shaft can be easily formed.

The rotation angle of the cylinder in which the fluid pressure in the first compression chamber reaches the maximum pressure and the rotation angle of the cylinder in which the fluid pressure in the second compression chamber reaches the maximum pressure may be shifted 180 degrees. This makes it possible to suppress an increase in torque fluctuation caused by enlarging the capacity of the compression chamber and effectively suppress the increase of noise and vibration as a whole of the compressor.

The term " 180 DEG out of phase " means not only that the phase is completely 180 DEG out of phase, but also includes a phase difference of 180 DEG due to manufacturing or assembly errors.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.
1 is an axial sectional view of a compressor according to a first embodiment of the present disclosure;
2 is a cross-sectional view taken along the line II-II in Fig.
3 is a cross-sectional view taken along the line III-III in Fig.
4 is an exploded perspective view of a compression mechanism of the compressor according to the first embodiment.
5 is an explanatory view for explaining the operating state of the compressor of the first embodiment.
6 is a graph showing the torque variation of the compressor of the first embodiment.
7 is an axial sectional view of the compressor of the second embodiment, and corresponds to Fig.
8 is an axial sectional view of the compressor of the third embodiment, and corresponds to Fig.

(First Embodiment)

Hereinafter, a first embodiment will be described with reference to the drawings. The cylinder-rotation type compressor 1 (hereinafter, simply referred to as "compressor 1") of the present embodiment is a compressor of a vapor compression refrigeration cycle apparatus for cooling air blown from a vehicle air conditioner to a passenger compartment In this refrigeration cycle apparatus, a function of compressing and discharging refrigerant as a fluid to be compressed is performed.

In this refrigeration cycle apparatus, an HFC-based refrigerant (specifically, R134a) is used as a refrigerant, and a sub-critical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant . Also, refrigerant, which is a lubricating oil for lubricating the sliding portion of the compressor 11, is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

1, the compressor 1 is provided with a compression mechanism 20 for compressing and discharging a refrigerant and an electric motor for driving the compression mechanism 20 in the housing 10 forming the outer periphery thereof, (Electric motor unit) 30 is accommodated. The upper and lower arrows in Fig. 1 show the respective directions of the upper and lower sides in a state where the compressor 1 is mounted on the vehicle air conditioner.

First, the housing 10 is formed by combining a plurality of metal members, and has a structure of a closed container which forms a substantially columnar space therein.

More specifically, as shown in Fig. 1, the housing 10 includes a cylindrical (cup-shaped) main housing 11 having a bottom and a bottom arranged to close an opening of the main housing 11 Shaped lid member 13 arranged to close the opening of the sub-housing 12 and the sub-housing 12 in one cylindrical shape.

A sealing member (not shown) made of an O-ring or the like is disposed at the abutting portion of the main housing 11, the sub housing 12, and the cover member 13 so that the refrigerant leaks from each abutting portion none.

A discharge port 11a for discharging the high pressure refrigerant boosted by the compression mechanism 20 to the outside of the housing 10 (specifically, the refrigerant inlet side of the condenser of the refrigeration cycle apparatus) is provided on the cylindrical side surface of the main housing 11. [ Respectively. A suction port 12a for sucking low-pressure refrigerant (specifically, low-pressure refrigerant discharged from the evaporator of the refrigeration cycle apparatus) from the outside of the housing 10 is formed on the cylindrical side surface of the sub-

Side suction port 12a for guiding the low-pressure refrigerant sucked from the suction port 12a to the first and second compression chambers Va and Vb of the compression mechanism unit 20 is provided between the sub-housing 12 and the lid member 13, And a passage 13a is formed. A driving circuit (inverter) 30a for supplying electric power to the electric motor unit 30 is attached to a surface of the lid member 13 opposite to the surface on the sub housing 12 side.

The motor base 30 has a stator 31 as a stator. The stator 31 is constituted by a stator core 31a formed of a metallic magnetic material and a stator coil 31b wound on the stator core 31a. The stator 31 is press-fitted into the inner peripheral surface of the cylindrical side surface of the main housing 11 And is fixed by means of shrinkage fitting, bolt tightening or the like.

When electric power is supplied from the drive circuit 30a to the stator coil 31b through a sealing terminal (hermetic seal terminal) (not shown), the cylinder 21 disposed on the inner peripheral side of the stator 31 is rotated A rotating magnetic field is generated. The cylinder 21 is made of a cylindrical metallic magnetic material and forms the first and second compression chambers Va and Vb of the compression mechanism 20 as described later.

Magnets (permanent magnets) 32 are fixed to the cylinder 21, as shown in the cross-sectional views of Figs. 2 and 3. Thus, the cylinder 21 also has a function as a rotor of the electric motor unit 30. [ The cylinder 21 rotates about the central axis C1 by a rotating system in which the stator 31 generates.

That is, in the compressor 1 of the present embodiment, the rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 are integrally formed. The rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 may be formed as separate members and integrated by means such as press fitting. The stator (the stator core 31a and the stator core 31a) of the electric motor unit 30 is disposed on the outer peripheral side of the cylinder 21.

Next, the compression mechanism 20 will be described. In the present embodiment, as the compression mechanism 20, there are provided two compression mechanism parts of the first compression mechanism 20a and the second compression mechanism 20b. The basic configurations of the first and second compression mechanism portions 20a and 20b are the same. In addition, the first and second compression mechanisms 20a and 20b are connected in parallel to the refrigerant flow in the housing 10.

As shown in Fig. 1, the first and second compression mechanism portions 20a and 20b are arranged in the direction of the center axis of the cylinder 21. Here, in the present embodiment, the first compression mechanism 20a is disposed on the bottom surface side of the main housing 11, and the second compression mechanism 20b is disposed on the sub housing 12 side, among the two compression mechanism sections .

In Figs. 1 and 4, the reference numerals of the constituent members of the second compression mechanism section 20b corresponding to the equivalent constituent members of the first compression mechanism section 20a are denoted by the letters "a" to "b" As shown in FIG. For example, the second rotor, which is a component corresponding to the first rotor 22a of the first compression mechanism 20a, is denoted by "22b" among the constituent members of the second compression mechanism 20a .

The first compression mechanism 20a is constituted by a cylinder 21, a first rotor 22a, a first vane 23a, a shaft 24, and the like. The second compression mechanism portion 20b is constituted by a cylinder 21, a second rotor 22b, a second vane 23b, a shaft 24, and the like. 1, a part of the bottom surface of the main housing 11 constitutes the first compression mechanism 20a in the cylinder 21 and the shaft 24, And the other part constitutes the second compression mechanism portion 20b.

The cylinder 21 rotates around the center axis C1 as the rotor of the electric motor unit 30 and the first compression chamber Va of the first compression mechanism unit 20a and the second compression chamber And is a cylindrical member forming the second compression chamber (Vb) of the mechanical section (20b). On one axial end side of the cylinder 21, a first side plate 25a, which is a closing member for closing the open end of the cylinder 21, is fixed by bolt tightening or the like. A second side plate 25b is likewise fixed to the other end side of the cylinder 21 in the axial direction.

The first and second side plates 25a and 25b have a disk-shaped upper portion extending in a direction substantially perpendicular to the rotation axis of the cylinder 21 and a boss portion disposed in the central portion of the disk-shaped upper portion and projecting in the axial direction. In the boss portion, through-holes penetrating through the first and second side plates 25a and 25b are formed.

A shaft supporting mechanism (not shown) is disposed in each of these through holes, and a shaft 24 is inserted into the shaft supporting mechanism. Thus, the cylinder 21 is rotatably supported with respect to the shaft 24 . Both ends of the shaft 24 are fixed to the housing 10 (specifically, the main housing 11 and the sub housing 12). Therefore, the shaft 24 is not rotated with respect to the housing 10. [

The cylinder 21 of this embodiment forms a first compression chamber Va and a second compression chamber Vb which are partitioned from each other. Therefore, between the first rotor 22a and the second rotor 22b inside the cylinder 21, a disk-like intermediate side plate (not shown) for partitioning the first compression chamber Va and the second compression chamber Vb, (Not shown). The intermediate side plate 25c has the same function as the first and second side plates 25a and 25b.

That is, in the cylinder 21 of the present embodiment, both end portions in the axial direction of the portion constituting the first compression mechanism portion 20a are closed by the first side plate 25a and the intermediate side plate 25c. In the cylinder 21, axial end portions of the portion constituting the second compression mechanism portion 20b are closed by the second side plate 25b and the intermediate side plate 25c.

In other words, the first side plate 25a and the second side plate 25b partition the first compression chamber Va together with the intermediate side plate 25c, the first rotor 22a, 25c, the second rotor 22b, and the like, as well as the second compression chamber Vb. The intermediate side plate 25c is disposed between the first rotor 22a and the second rotor 22b to partition the first compression chamber Va and the second compression chamber Vb.

Although the cylinder 21 and the intermediate side plate 25c are integrally formed in the present embodiment, the cylinder 21 and the intermediate side plate 25c may be formed as separate members, It may be integrated. In the present embodiment, the axial length of the first rotor 22a and the axial length of the second rotor 22b are equal, and the first compression chamber Va and the second compression chamber Vb are Are substantially equal in volume to each other.

The shaft 24 rotatably supports the cylinder 21 (specifically, each of the side plates 25a, 25b and 25c fixed to the cylinder 21), the first rotor 22a and the second rotor 22b In a substantially cylindrical shape.

An eccentric portion 24c having a smaller outer diameter than the end of the sub housing 12 side is provided at the axial center portion of the shaft 24. The center axis of the eccentric portion 24c is an eccentric axis C2 eccentric to the center axis C1 of the cylinder 21. [ The eccentric portion 24c is rotatably supported by the first and second rotors 22a and 22b via a shaft support mechanism (not shown).

As described above, the first and second compression mechanisms 20a and 20b of the present embodiment are arranged in the direction of the central axis of the cylinder 21. Therefore, the first rotor 22a and the second rotor 22b are also arranged in the direction of the central axis of the cylinder 21, as shown in Figs. 1 and 4. When the first and second rotors 22a and 22b rotate, they rotate around a common eccentric shaft C2 eccentric to the center axis C1 of the cylinder 21. [ That is, in this embodiment, the eccentric shaft of the first rotor 22a and the eccentric shaft of the second rotor 22b are disposed coaxially.

As shown in Fig. 1, a shaft 24 is provided in the shaft 24 and communicates with the housing-side suction passage 13a. A shaft for guiding the low-pressure refrigerant introduced from the outside to the first and second compression chambers Va and Vb A side suction passage 24d is formed. A plurality of (four in this embodiment) first and second shaft side outlet holes 240a and 240b for discharging the low-pressure refrigerant flowing through the shaft-side suction passage 24d are opened on the outer circumferential surface of the shaft 24 .

First and second shaft side concave portions 241a and 241b are formed on the outer circumferential surface of the shaft 24 so that the outer circumferential surface of the shaft 24 is recessed toward the inner circumferential side, as shown in Figs. The first and second shaft side outlet holes 240a and 240b are open to the portions where the first and second shaft side concave portions 241a and 241b are formed, respectively. Therefore, the first and second shaft side outlet holes 240a and 240b are formed in the annular first and second shaft side communication openings 241a and 241b formed in the first and second shaft side concave portions 241a and 241b, (242a, 242b).

The first rotor 22a is a cylindrical member disposed inside the cylinder 21 and extending in the direction of the central axis of the cylinder 21. [ The axial length of the first rotor 22a is substantially equal to the axial length of the portion constituting the first compression mechanism 20a of the shaft 24 and the cylinder 21 as shown in Fig. Respectively.

The outer diameter of the first rotor 22a is smaller than the inner diameter of the cylindrical space formed in the cylinder 21. More specifically, as shown in Figs. 2 and 3, the outer diameter of the first rotor 22a is larger than the outer diameter of the first rotor 22a when viewed in the axial direction of the eccentric shaft C2, 21 are brought into contact with each other at one contact point (C3).

A transmission mechanism is disposed between the first rotor 22a and the intermediate side plate 25c and between the first rotor 22a and the first side plate 25a. The transmission mechanism includes a cylinder 21 (more specifically, an intermediate side plate 25c and a first side plate 25a that rotate together with the cylinder 21) so that the first rotor 22a rotates synchronously with the cylinder 21, To the first rotor 22a.

This transmission mechanism will be described as an example in which it is disposed between the first rotor 22a and the intermediate side plate 25c. As shown in Fig. 2, the transmission mechanism includes a plurality of (four in this embodiment) circular first hole portions 221a formed on the surface of the first rotor 22a on the side of the intermediate side plate 25c, And a plurality of (four in this embodiment) driving pins 251c projecting from the intermediate side plate 25c toward the first rotor 22a in the central axis direction.

The plurality of drive pins 251c are smaller in diameter than the first hole portion 221a and protrude axially toward the rotor 22 and are fitted into the first hole portion 221a have. Therefore, the drive pin 251c and the first hole portion 221a constitute a mechanism equivalent to a so-called pin-hole type anti-rotation mechanism. The same applies to a transmission mechanism provided between the first rotor 22a and the first side plate 25a.

The relative position (relative distance) between each drive pin 251c and the eccentric portion 24c of the shaft 24 is smaller than the relative position of the drive pin 251c and the eccentric portion 24c of the shaft 24, Change. The sidewall surface of the first hole portion 221a of the first rotor 22a receives a load in the rotational direction from the drive pin 251c due to the change of the relative position (relative distance). As a result, the first rotor 22a rotates about the eccentric axis C2 in synchronization with the rotation of the cylinder 21. [

Here, in the transmission mechanism of the present embodiment, power is sequentially transmitted to the rotor 22 by the plurality of drive pins 251c and the first hole portion 221a. Therefore, it is preferable that the plurality of drive pins 251c and the first hole portions 221a are arranged at equal angular intervals around the eccentric axis C2. Each of the first hole portions 221a is fitted with a metal ring member 223a for suppressing abrasion of the outer circumferential side surface where the drive pin 251c makes contact.

1, a first oil passage (not shown) extending in the axial direction of the eccentric shaft C2 from the one axial end side to the other axial end side of the first rotor 22, Respectively.

The first oil passage 225a has a first oil return passage 11b formed on the bottom surface side of the main housing 11 and an oil passage 252a formed in the gap between the shaft 24 and the boss portion of the first side plate 25a. And the like. The first oil return passage 11b is a lubricant passage for guiding the refrigerator oil accumulated on the lower side of the inner space of the housing 10 toward the first oil passage 225a.

The first hole portions 221a of the transmission mechanism provided between the first rotor 22a and the intermediate side plate 25c and between the first rotor 22a and the first side plate 25a are connected to a first And is formed by both end portions in the axial direction of the oil passage 225a.

In other words, at least one first hole portion of the transmission mechanism provided between the first rotor 22a and the first side plate 25a, and at least one first hole portion of the transmission mechanism provided between the first rotor 22a and the intermediate side plate 25c At least one first hole portion 221a of the transmission mechanism communicates with each other through the first oil passage 225a.

As shown in Figs. 2 and 3, on the outer circumferential surface of the first rotor 22a, a first groove portion (first slit portion) 222a recessed toward the inner periphery over the entire axial direction is formed. A first vane 23a, which will be described later, is slidably fitted in the first groove portion 222a.

The first groove portion 222a is formed such that the surface of the first vane 23a on which the first vane 23a slides (the friction surface with the first vane 23a) is larger than the diameter of the first rotor 22a Lt; / RTI > More specifically, in the first groove portion 222a, the sliding surface of the first vane 23a is inclined in the rotating direction from the inner peripheral side to the outer peripheral side. Therefore, the first vane 23a fitted in the first groove portion 222a is also displaced in a direction inclined with respect to the radial direction of the first rotor 22a.

As shown in Fig. 3, in the axial center portion of the first rotor 22a, similarly to the first groove portion 222a, the first rotor 22a extends obliquely with respect to the radial direction, and the inner circumferential side of the first rotor 22a Side suction passage 224a for communicating the outer circumferential side (the first compression chamber Va side) with the first rotor-side suction passage 224a. Thus, the refrigerant introduced into the shaft-side suction passage 24d from the outside is guided to the first rotor-side suction passage 224a.

3, the outlet hole of the first rotor-side intake passage 224a is opened to the outer peripheral surface of the first rotor 22a on the rear side in the rotating direction with respect to the first groove portion 222a. Further, the first rotor-side suction passage 224a and the first groove portion 222a are partitioned from each other, and the respective internal spaces are formed so as not to communicate with each other.

The first vane 23a is a plate-like partitioning member for partitioning the first compression chamber Va formed between the outer circumferential surface of the first rotor 22a and the inner circumferential surface of the cylinder 21. The axial length of the first vane 23a is substantially the same as the axial length of the first rotor 22a. The outer peripheral side end portion of the first vane 23a is arranged slidably with respect to the inner peripheral surface of the cylinder 21. [

Therefore, in the first compression mechanism 20a of the present embodiment, the inner wall surface of the cylinder 21, the outer circumferential surface of the first rotor 22a, the plate surface of the first vane 23a, the first side plate 25a, The first compression chamber Va is formed by the space surrounded by the plate 25c. That is, the first vane 23a defines a first compression chamber Va formed between the inner circumferential surface of the cylinder 21 and the outer circumferential surface of the first rotor 22a.

The first side plate 25a is formed with a first discharge hole 251a through which the refrigerant compressed in the first compression chamber Va is discharged into the inner space of the housing 10. The refrigerant flowing out from the first discharge hole 251a to the inner space of the housing 10 flows back to the first compression chamber Va through the first discharge hole 251a in the first side plate 25a A first discharge valve composed of a reed valve for suppressing the flow of the refrigerant is disposed.

Next, the second compression mechanism 20 will be described. As described above, the basic configuration of the second compression mechanism 20b is the same as that of the first compression mechanism 20a. 1, the second rotor 22b has a cylindrical shape having dimensions substantially equal to the axial lengths of the portions constituting the second compression mechanism portion 20b of the shaft 24 and the cylinder 21 .

The eccentric axis C2 of the second rotor 22b and the eccentric axis C2 of the first rotor 22a are disposed coaxially with each other. Therefore, when viewed in the axial direction of the eccentric shaft C2, The outer circumferential surface of the rotor 22b and the inner circumferential surface of the cylinder 21 are in contact with each other at the contact point C3 shown in Figs. 2 and 3, like the first rotor 22a.

The first rotor 22a and the second rotor 22b are disposed between the second rotor 22b and the intermediate side plate 25c and between the second rotor 22b and the first side plate 25a. Mechanism is installed. Therefore, the second rotor 22b is formed with a plurality of circular second hole portions into which the plurality of drive pins 251c are inserted. The second hole portion is also fitted with the same ring member as the first hole portion 221a.

The driving pin 251c protruding from the intermediate side plate 25c toward the second rotor 22b is formed of the same member as the driving pin 251c protruding from the intermediate side plate 25c toward the first rotor 22b . That is, the driving pin 251c fixed to the intermediate side plate 25c protrudes in the central axis direction toward both the first rotor 22a side and the second rotor 22b side.

1, the second rotor 22b extends in the axial direction of the eccentric shaft C2 in the same manner as the first oil passage 225a of the first rotor 22a, And a second oil passage 225b penetrating from the one end side to the other end side is formed.

The second oil passage 225b is connected to the second oil return passage 12b formed in the sub housing 12 and the oil passage 252b formed in the gap between the shaft 24 and the boss portion of the second side plate 25b And is a lubricant passage for circulating refrigerator oil to be supplied. The second oil return passage 12b is a lubricant passage for guiding the refrigerator oil accumulated on the lower side of the inner space of the housing 10 to the second oil passage 225b side.

Both end portions in the axial direction of the second oil passage 225b form a second hole portion of the transmission mechanism, like the first oil passage 225a.

A second groove portion (second slit portion) 222b is formed on the outer circumferential surface of the second rotor 22b, as shown by the broken lines in Figs. 2 and 3, concaved toward the inner periphery over the entire axial direction . A second vane 23b is slidably fitted in the second groove portion 222b in the same manner as the first vane 23a of the first groove portion 222a.

As shown by the broken line in Fig. 3, the second rotor 22b is inclined radially inwardly similarly to the second groove portion 222b so as to extend from the inner circumferential side of the second rotor 22b to the inner circumferential side of the second rotor 22b. And a second rotor side suction passage 224b communicating with the outer peripheral side (the second compression chamber Vb side) is formed.

Therefore, in the second compression mechanism 20b of the present embodiment, the inner wall surface of the cylinder 21, the outer circumferential surface of the second rotor 22b, the plate surface of the second vane 23b, the second side plate 25b, The second compression chamber (Vb) is formed by the space surrounded by the plate (25c). That is, the second vane 23b defines a second compression chamber Vb formed between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the second rotor 22b.

The second side plate 25b is formed with a second discharge hole 251b for discharging the refrigerant compressed in the second compression chamber Vb to the inner space of the housing 10. The refrigerant flowing out from the second discharge hole 251b to the inner space of the housing 10 flows back to the second compression chamber Vb through the second discharge hole 251b in the second side plate 25b And a second discharge valve composed of a reed valve for suppressing the flow of the refrigerant.

In the second compression mechanism 20b of the present embodiment, as shown by the broken lines in FIGS. 2 and 3, the second vane 23b, the second rotor suction passage 224b, the second side plate 25b of the first side plate 25a are connected to the first vane 23a of the first compression mechanism portion 20a and the first rotor side suction passage 224a of the first compression mechanism portion 20a and the first discharge hole 251a, and the like.

Next, the operation of the compressor 1 of the present embodiment will be described with reference to Fig. 5 is an explanatory diagram continuously showing the change of the first compression chamber Va in accordance with the rotation of the cylinder 21 in order to explain the operating state of the compressor 1. Fig.

5, the positions of the first rotor-side intake passage 224a, the first vane 23a, and the like in a cross-sectional view equivalent to that of Fig. 3 are denoted by solid lines Respectively. 5, the positions of the second rotor-side intake passage 224b and the second vane 23b at the respective rotation angles? Are shown by broken lines. In Fig. 5, for the sake of clarity of illustration, reference numerals of respective constituent members are attached to cross-sectional views corresponding to the rotation angle [theta] of 0 = 0 deg.

First, when the rotation angle [theta] is 0 [deg.], The contact point C3 and the outer peripheral side end portion of the first vane 23a overlap. In this state, the first compression chamber Va having the maximum volume is formed on the front side in the rotational direction of the first vane 23a and the minimum volume (i.e., the volume is zero) is provided on the rear side in the rotational direction of the first vane 23a. The first compression chamber Va of the suction stroke of the suction stroke is formed.

Here, the 'first compression chamber Va' of the suction stroke 'means the first compression chamber Va which has a stroke for enlarging the volume, and the volume of the' first compression chamber Va of the compression stroke ' And the first compression chamber Va is a stroke for reducing the pressure in the first compression chamber.

As shown by the rotation angle [theta] = 45 DEG to 315 DEG in FIG. 5, as the rotation angle [theta] increases from 0 DEG, the cylinder 21, the first rotor 22a, The volume of the first compression chamber Va of the suction stroke formed on the rear side in the rotating direction of the first vane 23a is increased.

Accordingly, the low-pressure refrigerant sucked from the suction port 12a formed in the sub housing 12 flows from the housing-side suction passage 13a to the first shaft-side outlet hole 240a of the shaft-side suction passage 24d, And flows into the first compression chamber Va of the suction stroke in the order of the side suction passages 224a.

At this time, since the centrifugal force is applied to the first vane 23a due to the rotation of the rotor 22, the outer circumferential tip of the first vane 23a is pressed against the inner circumferential surface of the cylinder 21. Thus, the first vane 23a separates the first compression chamber Va of the suction stroke and the first compression chamber Va of the compression stroke.

When the rotation angle [theta] reaches 360 [deg.] (That is, when the rotation angle [theta] = 0), the first compression chamber Va of the suction stroke becomes the maximum volume. Further, when the rotation angle [theta] increases at 360 degrees, the first compression chamber Va and the first rotor-side intake passage 224a, which are increased in volume by the rotation angle [theta] . As a result, the first compression chamber Va of the compression stroke is formed on the front side in the rotating direction of the first vane 23a.

Further, as the rotational angle [theta] increases at 360 degrees, as shown by point hatching at the rotational angle [theta] in FIG. 5 = 405 DEG to 675 DEG, rotation of the first vane 23a The volume of the first compression chamber Va of the compression stroke formed on the front side in the direction is reduced.

As a result, the refrigerant pressure in the first compression chamber (Va) of the compression stroke rises. When the refrigerant pressure in the first compression chamber Va exceeds the valve opening pressure of the first discharge valve (i.e., the maximum pressure of the first compression chamber Va) determined by the refrigerant pressure in the internal space of the housing 10 , The refrigerant in the first compression chamber (Va) is discharged into the inner space of the housing (10) through the first discharge hole (251a).

In the above description of the operation, the change of the first compression chamber Va while the rotation angle [theta] changes from 0 [deg.] To 720 [deg.] For clarification of the operation mode of the first compression mechanism 20a has been described , Actually, the refrigerant compression stroke described when the rotation angle? And the rotation angle? Are changed from 360 degrees to 720 degrees, which is described when the rotation angle? Changes from 0 degrees to 360 degrees, Is performed at the same time.

Also, the second compression mechanism 20b operates similarly to compress and suck the refrigerant. At this time, in the second compression mechanism 20b, the second vane 23b, etc. are disposed at positions shifted by 180 degrees from the first vane 23a of the first compression mechanism 20a. Therefore, in the second compression chamber (Vb) in the compression stroke, the refrigerant is compressed and sucked at a rotation angle shifted by 180 degrees from the first compression chamber (Va).

Therefore, in this embodiment, the rotation angle [theta] of the cylinder 21 in which the refrigerant pressure in the first compression chamber Va reaches the maximum pressure and the refrigerant pressure in the second compression chamber Vb reach the maximum pressure The rotation angle [theta] of the cylinder 21 is also deviated by 180 degrees.

The refrigerant pressure in the second compression chamber Vb in the compression stroke rises and the refrigerant pressure in the second compression chamber Vb is lower than the valve opening pressure of the second discharge valve disposed in the second side plate 25b The refrigerant in the second compression chamber Vb is discharged to the inner space of the housing 10 through the second discharge hole 251b when the pressure in the second compression chamber Vb exceeds the maximum pressure of the second compression chamber Vb. The refrigerant discharged from the second compression mechanism portion 20b into the internal space of the housing 10 joins with the refrigerant discharged from the first compression mechanism portion 20a.

The combined refrigerant of the high-pressure gaseous refrigerant discharged from the first compression mechanism unit 20a and the high-pressure gaseous refrigerant discharged from the second compression mechanism unit 20b lowers the flow velocity in the inner space of the housing 10. Accordingly, the refrigerating machine oil discharged from the first and second discharge holes 251a and 251b together with the high-pressure gaseous refrigerant falls downward due to the action of gravity and is separated from the combined refrigerant.

The combined refrigerant separated from the refrigerating machine oil is discharged from the discharge port (11a) of the housing (10). On the other hand, the refrigerator oil separated from the combined refrigerant is stored in the lower side of the inner space of the housing 10. The refrigerator oil stored under the inner space of the housing 10 flows into the first and second oil passages 225a and 225b through the first and second oil return passages 11b and 12b and the like. Thus, the shaft 24 is supplied to the respective sliding portions of the first and second rotors 22a and 22b and the respective side plates 25a to 25c.

As described above, in the compressor 1 of the present embodiment, the refrigerant (fluid) can be sucked in the refrigeration cycle apparatus, compressed and discharged. In the compressor 1 of the present embodiment, since the compression mechanism 20 is disposed on the inner peripheral side of the electric motor 30, the compressor 1 as a whole can be downsized.

In the compressor 1 of the present embodiment, since the first rotor 22a (first compression mechanism 20a) and the second rotor 22b (second compression mechanism 20b) are provided, The chamber Va and the second compression chamber Vb can be formed. Therefore, the total discharge capacity of the first compression chamber (Va) and the second compression chamber (Vb) can be easily expanded according to the system to which the present invention is applied (the refrigerating cycle apparatus in this embodiment).

At this time, since the first rotor 22a and the second rotor 22b are arranged in the direction of the central axis of the cylinder 21, it is necessary to enlarge the outer diameter of the cylinder 21 in order to increase the total discharge capacity none. Therefore, the outer diameter of the stator 31 of the electric motor base 30 and the main housing 11 accommodating the stator 31 is not enlarged.

As a result, according to the compressor 1 of the present embodiment, it is possible to enlarge the capacity of the compression chambers Va and Vb without causing enlargement in the radial direction.

In the compressor 1 of the present embodiment, since the eccentric axis C2 of the first rotor 22a and the eccentric axis C2 of the second rotor 22b are arranged on the same axis, It is not necessary to form a portion having another eccentric shaft, so that the shaft 24 can be easily formed.

In the compressor 1 of the present embodiment, the maximum volumes of the first compression chamber Va and the second compression chamber Vb are substantially equal to each other, and the refrigerant in the first compression chamber Va is the maximum The rotation angle? Of the cylinder 21 reaching the pressure and the rotation angle? Of the cylinder 21 in which the refrigerant in the second compression chamber Vb reaches the maximum pressure are displaced by 180 °.

Thus, as shown in Fig. 6, it is possible to suppress an increase in torque fluctuation caused by enlarging the capacity of the compression chamber. Therefore, it is possible to effectively suppress the increase of noise or vibration as a whole of the compressor.

Here, Fig. 6 shows a comparison between the total torque fluctuation of the compressor 1 of the present embodiment and the torque fluctuation of the cylinder rotary compressor (single-cylinder cylinder compressor) having the same single compression mechanism section as that of the first compression mechanism section 20a Graph. The term "total torque fluctuation" refers to a change in the torque caused by the pressure fluctuation of the refrigerant in the first compression chamber (Va) of the first compression mechanism (20a) and a change in the torque generated in the second compression chamber ) Is the sum of the torque fluctuations caused by the pressure fluctuations of the refrigerant in the refrigerant.

The discharge capacity of the single-cylinder compressor shown in Fig. 6 corresponds to the total discharge capacity of the first compression chamber Va and the second compression chamber Vb of the compressor 1 of the present embodiment. The suction refrigerant pressure and the discharge refrigerant pressure of the single-cylinder compressor shown in Fig. 6 are set equal to the suction refrigerant pressure and the discharge refrigerant pressure with the compressor 1 of the present embodiment, respectively.

In the compressor 1 of the present embodiment, since the first and second oil passages 225a and 225b are formed in the first and second rotors 22a and 22b, the shaft 24, 2 rotors 22a, 22b and the respective sliding portions of the respective side plates 25a to 25c. As a result, the durability performance of the compressor 1 as a whole can be improved.

Particularly, the first and second oil passages 225a and 225b are formed so that the first and second rotors 22a and 22b located at the central portion in the center axis direction in the cylinder 21 and the first and second oil passages 225a and 225b, It is effective in that refrigeration oil can be introduced into the sliding portion of the plate 25c.

Further, since the compressor 1 of the present embodiment adopts the same structure as the so-called pin-and-hole type anti-rotation mechanism as the transmission mechanism, the transmission mechanism can be realized with a simple structure. Further, since the ring member 223a is fitted in the hole portion of the transmission mechanism, wear resistance of the hole portion can be improved. As a result, the durability performance of the compressor 1 as a whole can be improved.

In addition, the first and second hole portions 221a are formed at the axial end portions of the first and second oil passages 225a and 225b. Therefore, it is possible to reduce the space for disposing the transmission mechanism, thereby further reducing the size of the compressor 1 as a whole.

In the compressor 1 of the present embodiment, the suction passage for guiding the refrigerant sucked from the outside to the first and second compression chambers Va and Va is connected to the shaft side suction passage 24d and the first and second rotors Side suction passages 224a and 224b, and the like. Therefore, there is no possibility that the passage structure of the suction passage or the sealing structure is complicated when a part of the suction passage is formed on the first and second side plates 25a, 25b rotating together with the cylinder 21 .

Since the first and second discharge holes 251a and 251b are formed in the first and second side plates 25a and 25b so that the first and second compression mechanism portions 20a and 20b are connected to the housing 10, It is possible to easily realize a configuration in which refrigerant flows are connected in parallel in the interior of the compressor.

(Second Embodiment)

In this embodiment, an example in which the configuration of the compression mechanism section 20 is changed as shown in Fig. 7 will be described with respect to the first embodiment. 7 is a cross-sectional view corresponding to Fig. 3 described in the first embodiment, and shows a vertical section in the axial direction of the first compression mechanism 20a. In Fig. 7, the same or equivalent portions as those of the first embodiment are denoted by the same reference numerals. This also applies to Fig. 8 described in the following embodiments.

More specifically, in the first compression mechanism portion 20a of the present embodiment, the first hinge portion 231a is formed at the outer peripheral side end portion of the first vane 23a. The first hinge portion 231a is supported so as to be slidable in the circumferential direction in the hinge groove portion formed on the inner peripheral surface of the cylinder 21. [ Therefore, the vane 23 is not separated from the cylinder 21, and the inner peripheral side of the first vane 23a is slidingly displaced in the first groove portion 222a.

An arc-shaped portion having a diameter equal to the width dimension of the first groove portion 222a is formed in the inner peripheral side end portion of the first vane 23a. Thus, when the first vane 23a swings with the rotation of the cylinder 21, the contact between the inner circumferential side of the first vane 23a and the inner wall surface of the first groove portion 222a, that is, The sealing property between the inner peripheral side end of the vane 23a and the inner wall surface of the first groove portion 222a is improved.

The basic configuration of the second compression mechanism 20b is the same as that of the first compression mechanism 20a. Therefore, as shown by the broken line in Fig. 7, the outer peripheral side end portion of the second vane 23b is also supported so as to be swingable by the cylinder.

Other configurations and operations are the same as those of the first embodiment. Therefore, when the compressor 1 of the present embodiment is operated, it operates in the same manner as in the first embodiment, so that the refrigerant (fluid) can be sucked, compressed and discharged in the refrigerating cycle apparatus. Further, similarly to the first embodiment, the capacity of the compression chambers Va and Vb can be enlarged without increasing the size in the radial direction, and the increase in noise and vibration as the entire compressor can be suppressed.

(Third Embodiment)

In this embodiment, an example in which the configuration of the compression mechanism section 20 is changed as shown in Fig. 8 will be described with respect to the second embodiment. More specifically, in the first compression mechanism portion 20a of the present embodiment, the inner circumferential side of the first hinge portion 231a of the first vane 23a is formed on a flat plate.

A first shoe 232a having a circular shape in cross section when viewed in the axial direction of the central axis C1 is cut out (approximately semicircular shape) in the first groove portion 222a, Are arranged so as to sandwich the first vane 23a. The axial length of the first shoe 232a is approximately the same as that of the first rotor 22a and the first vane 23a. The basic configuration of the second compression mechanism 20b is the same as that of the first compression mechanism 20a.

Other configurations and operations are the same as those of the second embodiment. Therefore, when the compressor 1 of the present embodiment is operated, it operates in the same manner as in the third embodiment, so that the refrigerant (fluid) can be sucked in the refrigeration cycle apparatus, compressed and discharged. Further, similarly to the first embodiment, the capacity of the compression chambers Va and Vb can be enlarged without increasing the size in the radial direction, and the increase in noise and vibration as the entire compressor can be suppressed.

Since the shoe 232a is disposed in the compressor 1 of the present embodiment, the sealing property between the first and second vanes 23a and 23b and the inner wall surfaces of the first and second trench sections 222a and 222b Can be effectively improved. Thus, the compression efficiency of the compressor 1 can be improved.

(Other Embodiments)

The present disclosure is not limited to the above embodiment, and various modifications can be made within the scope not departing from the gist of the present disclosure as follows.

In the above-described embodiment, the cylinder rotation type compressor 1 is applied to the refrigeration cycle of the vehicle air conditioner. However, the application of the cylinder rotation type compressor 1 is not limited thereto. That is, the cylinder-rotation type compressor 1 is applicable to a wide variety of applications as a compressor for compressing various fluids.

In the above embodiment, the power transmission means of the cylinder rotary compressor 1 has been described as an example in which the same structure as that of the pin-and-hole type anti-rotation mechanism is employed, but the power transmission means is not limited thereto. For example, a configuration similar to that of the oldham ring type anti-rotation mechanism may be employed.

In the above embodiment, the motor base 30 having the stator disposed on the outer periphery side of the cylinder 21 integrally formed with the rotor has been described. However, the motor base 30 is not limited thereto. For example, the motor base and the cylinder 21 may be arranged in the direction of the center axis C1 of the cylinder 21, and the motor base and the cylinder 21 may be connected. The rotational driving force of the electric motor unit may be transmitted to the cylinder 21 via the belt without arranging the rotational center of the electric motor unit and the central axis C1 of the cylinder 21 on the same axis.

Claims (9)

A cylindrical cylinder 21 rotating around the central axis C1;
A cylindrical first rotor 22a and a second rotor 22b disposed inside the cylinder 21 and rotating about an eccentric shaft C2 eccentric to the center axis C1 of the cylinder 21, ;
A shaft 24 rotatably supporting the first rotor 22a and the second rotor 22b;
The first rotor 22a is slidably fitted in the first groove portion 222a formed in the first rotor 22a and the first compression chamber 22a formed between the outer circumferential surface of the first rotor 22a and the inner circumferential surface of the cylinder 21 A first vane 23a for partitioning the first vane 23a; And
The second rotor 22b is slidably fitted in the second groove portion 222b formed in the second rotor 22b so as to be slidably engaged with the second compression chamber 22b formed between the outer peripheral surface of the second rotor 22b and the inner peripheral surface of the cylinder 21 And a second vane (23b) for partitioning the first vane (Vb)
Wherein the first rotor (22a) and the second rotor (22b) are arranged in the direction of the center axis (C1) of the cylinder (21).
The method according to claim 1,
And the eccentric shaft of the first rotor (22a) and the eccentric shaft of the second rotor (22b) are disposed on the same axis.
3. The method according to claim 1 or 2,
The rotation angle? Of the cylinder 21 in which the fluid pressure in the first compression chamber Va reaches the maximum pressure and the rotation angle? Of the cylinder 21 in which the fluid pressure in the second compression chamber Vb reaches the maximum pressure ) Is shifted by 180 占 from the rotation angle (?) Of the cylinder-type compressor.
4. The method according to any one of claims 1 to 3,
The first rotor 22a and the second rotor 22b are respectively provided with a first oil passage 225a extending in the axial direction of the shaft 24 and allowing lubricant for lubricating the sliding portion to flow, (225b).
5. The method according to any one of claims 1 to 4,
The rotational driving force from the cylinder 21 to the first rotor 22a and the second rotor 22b so that the first rotor 22a and the second rotor 22b synchronously rotate with the cylinder 21. [ A transmission mechanism (251c, 221a) for transmitting the electric power; And
Is disposed between the first rotor (22a) and the second rotor (22b) to partition the first compression chamber (Va) and the second compression chamber (Vb) And a rotating intermediate side plate 25c,
The transmission mechanism includes a driving pin 251c projecting from the intermediate side plate 25c toward the first rotor 22a side and the second rotor 22b side in the central axis direction, And a first hole portion (221a) formed in the second rotor (22b) and into which the drive pin (251c) is fitted.
6. The method of claim 5,
And a ring member (223a) for suppressing abrasion of the outer peripheral side wall surface where the drive pin (251c) is contacted is fitted in the first and second hole portions (221a).
The method according to claim 5 or 6,
The first rotor 22a is provided with a first oil passage 225a which extends in the axial direction of the eccentric shaft C2 and through which lubricating oil for lubricating the sliding portion flows,
The first hole portion 221a is formed at an axial end portion of the first oil passage 225a,
The second rotor 22b is provided with a second oil passage 225b which extends in the axial direction of the eccentric shaft C2 and through which lubricating oil for lubricating the sliding portion flows,
And the second hole portion is formed at the axial end of the second oil passage (225b).
8. The method according to any one of claims 1 to 7,
Is disposed between the first rotor (22a) and the second rotor (22b) to partition the first compression chamber (Va) and the second compression chamber (Vb) A rotating intermediate side plate 25c;
A first side plate (25a) fixed to one axial end side of the cylinder (21) and partitioning the first compression chamber (Va) together with the intermediate side plate (25c); And
And a second side plate (25b) fixed to the other axial end side of the cylinder (21) and partitioning the second compression chamber (Vb) together with the intermediate side plate (25c)
The first rotor 22a is provided with a first rotor side intake passage 224a for introducing a fluid to be compressed into the first compression chamber Va,
The first side plate 25a is formed with a first discharge hole 251a for discharging the fluid to be compressed from the first compression chamber Va,
The second rotor 22b is provided with a second rotor side intake passage 224b for introducing the fluid to be compressed into the second compression chamber Vb,
The second side plate 25b is formed with a second discharge hole 251b for discharging the fluid to be compressed from the second compression chamber Vb,
The shaft 24 is further provided with a shaft side suction passage 24d for guiding the fluid to be compressed sucked from the outside to the first rotor side suction passage 224a and the second rotor side suction passage 224b Cylinder rotary compressor.
9. The method according to any one of claims 1 to 8,
And a motor (30) for rotating the cylinder (21)
The cylinder 21 is integrally formed with the rotor of the electric motor unit 30,
And the stator of the electric motor unit (30) is disposed on the outer peripheral side of the cylinder (21).

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