WO2016088326A1

WO2016088326A1 - Cylinder rotary compressor

Info

Publication number: WO2016088326A1
Application number: PCT/JP2015/005817
Authority: WO
Inventors: 善則村瀬; 小川　博史; 卓也石川
Original assignee: 株式会社デンソー
Priority date: 2014-12-02
Filing date: 2015-11-23
Publication date: 2016-06-09
Also published as: JP2016108955A

Abstract

A cylinder rotary compressor according to the present application has, inside an eccentrically rotating rotor (22), a rotor-side intake passage (22b) for guiding a coolant that has flowed out of a shaft-side intake passage (24b) to a compression space (V), the shaft-side intake passage (24b) being formed in a shaft (24). Additionally, the cylinder rotary compressor has, on the outer peripheral surface of the rotor (22), a circumferential direction intake passage (22c) for guiding a coolant that has flowed out of the rotor-side intake passage (22b) to the compression space (V) that has formed an intake stroke from an outlet of the rotor-side intake passage (22b). Accordingly, the coolant is allowed to quickly flow into the compression space (V) that has formed an intake stroke, and reductions in the pressure inside the compression space (V) are suppressed. As a result thereof, increases in energy loss of the cylinder rotary compressor are suppressed.

Description

Cylinder rotary compressor

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2014-244132 filed on Dec. 2, 2014, the disclosure of which is incorporated herein by reference.

The present disclosure relates to a cylinder rotary compressor that rotates a cylinder that forms a compression chamber therein.

Conventionally, a cylinder rotary type compressor that compresses and discharges a fluid by changing a volume of the compression chamber by rotating a cylinder that forms a compression chamber therein is known.

For example, in Patent Document 1, a cylindrical cylinder integrally formed with a rotor of an electric motor unit (electric motor unit), a rotor formed of a columnar member disposed inside the cylinder, and a rotor are formed. And a vane that is slidably fitted in the groove and partitions the compression chamber.

In this type of cylinder rotary compressor, the volume of the compression chamber is changed by displacing the vane by rotating the cylinder and the rotor in conjunction with different rotating shafts. Furthermore, in the cylinder rotation type compressor of patent document 1, the size reduction as the whole compressor is aimed at by arrange | positioning a compression mechanism part to the inner peripheral side of an electric motor part.

Incidentally, in the cylinder rotary compressor of Patent Document 1, a part of a suction passage that guides a fluid to be compressed sucked from the outside to a compression chamber is formed in a side plate that closes one end of the cylinder in the axial direction. However, since the side plate rotates together with the cylinder, if a part of the suction passage is formed in the side plate, the configuration of the suction passage and the sealing structure are likely to be complicated.

JP 2012-67735 A

The inventors of the present invention previously described in Japanese Patent Application No. 2013-119924 (hereinafter referred to as the prior application example) a shaft that rotatably supports the rotor and a suction passage formed inside the rotor, A cylinder rotary type compressor that introduces fluid into a compression chamber has been proposed. According to this, the fluid to be compressed can be guided into the compression chamber without causing complication of the passage configuration of the suction passage and the seal structure.

However, when the present inventors have studied the performance improvement of the cylinder rotary compressor, in the cylinder rotary compressor of the prior application, the compression chamber immediately after the suction stroke (stroke to increase the volume) is reached. As a result, it was found that the fluid pressure in the compression chamber immediately after the intake stroke was reduced. Such a pressure drop causes an increase in power consumed to drive the compressor, and increases energy loss of the compressor.

In view of the above points, the present disclosure aims to suppress an increase in energy loss of a cylinder rotary compressor.

According to one aspect of the present disclosure, a cylinder rotary compressor is a cylindrical cylinder that rotates about a central axis, and is disposed inside the cylinder and rotates about an eccentric shaft that is eccentric with respect to the central axis of the cylinder. A cylindrical rotor, a shaft that rotatably supports the rotor, and a compression chamber that is slidably fitted in a groove provided in the rotor and is provided between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder. A vane for partitioning. The shaft has a shaft-side suction passage through which the fluid to be compressed flowing from the outside flows. The rotor has a rotor-side suction passage that guides the fluid to be compressed flowing out from the shaft-side suction passage to the compression chamber. At least one of the rotor and the cylinder has a circumferential suction passage that guides the compression target fluid that has flowed out of the rotor-side suction passage from the outlet of the rotor-side suction passage to the compression chamber that is in the suction stroke.

According to this, since the circumferential suction passage is formed, it is possible to promptly flow the fluid to be compressed into the compression chamber that has become the suction stroke. Therefore, it is possible to suppress a pressure drop from occurring in the compression chamber immediately after the intake stroke, and to suppress an increase in energy loss of the cylinder rotary compressor.

In the present disclosure, the “compression chamber that has become the suction stroke” means a compression chamber that has become a stroke in which the volume is increased. Including meaning.

It is sectional drawing which is parallel to the axial direction of the compressor of 1st Embodiment of this indication, and shows a compressor. FIG. 2 is a sectional view taken along the line II-II in FIG. FIG. 3 is a sectional view taken along line III-III in FIG. It is an external appearance perspective view of the rotor of 1st Embodiment. It is explanatory drawing for demonstrating the operating state of the compressor of 1st Embodiment. It is a figure which shows the change of the volume of the compression chamber with respect to the rotation angle of the compressor of 1st Embodiment. It is a figure which shows the change of the refrigerant | coolant pressure in a compression chamber with respect to the rotation angle of the compressor of 1st Embodiment. It is explanatory drawing for demonstrating the operating state of the compressor of the comparative example of this indication. It is a graph which shows the change of the refrigerant | coolant pressure in a compression chamber with respect to the rotation angle of the compressor for a comparison. It is a sectional view perpendicular to the axial direction of the compressor of a 2nd embodiment of this indication, and showing a compressor. It is a sectional view perpendicular to the axial direction of the compressor of a 3rd embodiment of this indication, and showing a compressor. It is explanatory drawing for demonstrating the operating state of the compressor of 3rd Embodiment.

Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.
(First embodiment)
Hereinafter, the first embodiment of the present disclosure will be described with reference to FIGS. 1 to 9. A cylinder rotary compressor 1 (hereinafter simply referred to as a compressor 1) of the present embodiment is applied to a vapor compression refrigeration cycle apparatus that cools air blown into a vehicle interior by a vehicle air conditioner. In this refrigeration cycle apparatus, the refrigerant that is an example of the fluid to be compressed is compressed and discharged.

As shown in FIG. 1, the compressor 1 includes a compression mechanism portion 20 that compresses and discharges a refrigerant into a housing 10 that forms an outer shell thereof, and an electric motor portion (electric motor portion) that drives the compression mechanism portion 20. ) Is configured as an electric compressor containing 30.

First, the housing 10 is configured by combining a plurality of metal members, and has a sealed container structure that forms a substantially cylindrical space inside.

More specifically, as shown in FIG. 1, the housing 10 includes a bottomed cylindrical (cup-shaped) main housing 11, and a bottomed cylindrical sub-unit disposed so as to close the opening of the main housing 11. It is configured by combining the housing 12 and a disk-shaped lid member 13 arranged so as to close the opening of the sub-housing 12.

It should be noted that a seal member (not shown) made of an O-ring or the like is interposed in the contact portions of the main housing 11, the sub housing 12, and the lid member 13, so that the refrigerant does not leak from each contact portion.

On the cylindrical side surface of the main housing 11, there is a discharge port 11 a that discharges the high-pressure refrigerant pressurized 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 formed. A suction port 12 a that sucks low-pressure refrigerant (specifically, low-pressure refrigerant flowing out of the evaporator of the refrigeration cycle apparatus) from the outside of the housing 10 is formed on the cylindrical side surface of the sub-housing 12.

Between the sub housing 12 and the lid member 13, a housing side suction passage 13a for guiding the low pressure refrigerant sucked from the suction port 12a to the compression chamber V of the compression mechanism section 20 is formed. Further, a drive circuit (inverter) 30 a for supplying electric power to the motor unit 30 is attached to the surface of the lid member 13 opposite to the surface on the sub housing 12 side.

Next, the electric motor unit 30 has a stator 31 as a stator. The stator 31 includes a stator core 31a formed of a metal magnetic material and a stator coil 31b wound around the stator core 31a. The stator 31 is fixed to the inner peripheral surface of the cylindrical side surface of the main housing 11 by a method such as press fitting. Yes.

When electric power is supplied from the drive circuit 30a to the stator coil 31b via the sealing terminal (hermetic seal terminal) 30b, a rotating magnetic field that rotates the cylinder 21 disposed on the inner peripheral side of the stator 31 is generated. . The cylinder 21 is formed of a cylindrical metal magnetic material, and forms a compression chamber of the compression mechanism unit 20 as will be described later.

Furthermore, a magnet (permanent magnet) 32 is fixed to the cylinder 21 as shown in the sectional views of FIGS. Thereby, the cylinder 21 also has a function as a rotor of the electric motor unit 30. The cylinder 21 rotates around the central axis C1 by the rotating magnetic field generated by the stator 31.

That is, in the compressor 1 of this embodiment, the rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 are integrally configured. Of course, the rotor of the electric motor unit 30 and the cylinder 21 of the compression mechanism unit 20 may be configured as separate members and integrated by a method such as press fitting.

Next, the compression mechanism unit 20 will be described. The compression mechanism unit 20 includes a cylinder 21, a rotor 22, a vane 23, a shaft 24, and the like. The cylinder 21 is a cylindrical member that forms the compression chamber V therein, and has a function as a rotor of the electric motor unit 30 as described above, and rotates around the central axis C1.

The first and

second side plates

25a and 25b, which are closing members that close the opening end of the cylinder 21, are fixed to both ends of the cylinder 21 in the axial direction. Accordingly, the first and

second side plates

25 a and 25 b rotate together with the cylinder 21. In the present embodiment, the closing member disposed on the sub housing 12 side is referred to as a first side plate 25a, and the closing member disposed on the bottom surface side of the main housing 11 is referred to as a second side plate 25b.

The first and

second side plates

25a and 25b have a disk-shaped portion that extends in a direction substantially perpendicular to the rotation axis of the cylinder 21, and a boss portion that is disposed at the center of the disk-shaped portion and protrudes in the axial direction. is doing. Furthermore, a through-hole penetrating the front and back of the first and

second side plates

25a and 25b is formed in the boss portion.

A bearing mechanism (not shown) is disposed in each of these through holes, and the cylinder 21 is rotatably supported with respect to the shaft 24 by inserting the shaft 24 into the bearing mechanism. Further, both end portions of the shaft 24 are fixed to the housing 10 (specifically, the main housing 11 and the sub-housing 12). Therefore, the shaft 24 does not rotate with respect to the housing 10.

The shaft 24 is a substantially cylindrical member that rotatably supports the cylinder 21 (specifically, the first and

second side plates

25 a and 25 b fixed to the cylinder 21) and the rotor 22.

A small-diameter portion having a smaller outer diameter than the end portion on the sub-housing 12 side is provided in the central portion of the shaft 24 in the axial direction. The small diameter portion constitutes an eccentric portion 24c that is eccentric with respect to the central axis C1 of the cylinder 21. The rotor 22 is rotatably supported on the small diameter portion via a bearing mechanism (not shown). For this reason, when the rotor 22 rotates, the rotor 22 rotates around the eccentric shaft C2 that is eccentric with respect to the central axis C1 of the cylinder 21.

Further, as shown in FIG. 1, the shaft 24 is in communication with the housing side suction passage 13a, and a shaft side suction passage 24b for guiding the low-pressure refrigerant flowing from the outside to the compression chamber V side. 1. As shown in FIG. 3, a plurality (four in this embodiment) of shaft-side suction holes 24a are formed so as to extend in the radial direction and allow the shaft-side suction passage 24b and the compression chamber V to communicate with each other.

The rotor 22 is a hollow columnar member (cylindrical member) that is disposed inside the cylinder 21 and extends in the central axis direction of the cylinder 21. As shown in FIG. 1, the axial length of the rotor 22 is approximately the same as the axial length of the eccentric portion 24 c of the shaft 24 and the axial length of the cylindrical space formed inside the cylinder 21. Is formed.

Furthermore, the outer diameter dimension of the rotor 22 is formed smaller than the inner diameter dimension of the columnar space formed inside the cylinder 21. More specifically, the outer diameter of the rotor 22 is such that the outer peripheral surface of the rotor 22 and the inner peripheral surface of the cylinder 21 are 1 when viewed from the direction of the central axis C1 of the cylinder 21, as shown in FIG. It is set to contact at a contact point C3.

Between the rotor 22 and the first and

second side plates

25a and 25b, there is provided a power transmission unit for transmitting a rotational driving force from the first and

second side plates

25a and 25b rotating together with the cylinder 21 to the rotor 22. ing.

More specifically, for example, as shown in FIG. 2, the power transmission unit provided between the rotor 22 and the first side plate 25 a is a plurality of (on the first side plate 25 a side surface of the rotor 22 ( In the present embodiment, there are three (three) circular holes 221 and a plurality (three in the present embodiment) of driving pins 251 fixed to the first side plate 25a.

The plurality of drive pins 251 have a smaller diameter than the hole 221, protrude in the axial direction toward the rotor 22, and are fitted in the holes 221. Therefore, the drive pin 251 and the hole 221 constitute a mechanism equivalent to a so-called pin-hole type anti-rotation mechanism. The same applies to the power transmission unit provided between the rotor 22 and the second side plate 25b.

According to the power transmission unit of the present embodiment, when the cylinder 21 rotates around the central axis C1, the relative position (relative distance) between each drive pin 251 and the eccentric portion 24c of the shaft 24 changes. Due to the change in the relative position (relative distance), the side wall surface of the hole 221 of the rotor 22 receives a load in the rotational direction from the drive pin 251. As a result, the rotor 22 rotates around the eccentric axis C <b> 2 in synchronization with the rotation of the cylinder 21.

Here, in the power transmission unit of the present embodiment, power is sequentially transmitted to the rotor 22 by the plurality of drive pins 251 and the holes 221. Therefore, it is desirable that the plurality of drive pins 251 and the holes 221 be arranged at equiangular intervals around the eccentric axis C2. Further, in order to suppress wear on the side wall surface of the hole 221, a wear-inhibiting ring member or the like may be disposed on the side wall surface of the hole 221.

Further, as shown in FIGS. 2 and 3, a groove portion 22a is formed on the outer peripheral surface of the rotor 22 so as to be recessed toward the inner periphery over the entire axial direction. 23 is slidably fitted. More specifically, in the groove portion 22a of the present embodiment, the surface on which the vane 23 slides (the friction surface with the vane 23) is parallel to the radial direction of the rotor 22 when viewed from the axial direction of the eccentric shaft C2. Is formed.

As shown in FIG. 3, a rotor side suction passage 22 b that extends in the radial direction and communicates the inner peripheral side and the outer peripheral side of the rotor 22 is formed inside the central portion of the rotor 22 in the axial direction. The rotor-side suction passage 22b is a refrigerant passage that circulates the low-pressure refrigerant flowing out from the shaft-side suction hole 24a provided in the shaft 24 and guides it to the compression chamber V side.

Further, as is apparent from FIG. 3, the refrigerant outlet of the rotor side suction passage 22b opens to the outer peripheral surface of the rotor 22 on the rear side in the rotational direction with respect to the groove 22a. In other words, the refrigerant outlet of the rotor-side suction passage 22b opens closer to the wall surface on the rear side of the outer circumferential surface of the rotor 22 than the wall surface on the front side in the rotational direction of the groove 22a.

On the outer peripheral surface of the rotor 22, a circumferential suction passage 22c that guides the refrigerant from the outlet side of the rotor side suction passage 22b formed on the outer peripheral surface of the rotor 22 toward the groove portion 22a is formed. More specifically, as an example of the circumferential suction passage 22c, as shown in FIG. 4, it is formed by notching (shaving off) the axial central portion of the outer circumferential surface of the rotor 22 in the circumferential direction (rotating direction). Cutouts are used.

4 is an external perspective view of the rotor 22. In FIG. 4, the lower side of the rotor 22 is the side on which the first side plate 25a is disposed.

The vane 23 is formed of a plate-like member, and the axial length of the vane 23 is substantially the same as the axial length of the rotor 22. Further, a hinge portion 23 a is formed at the outer peripheral side end portion of the vane 23. The hinge portion 23a is supported in a groove portion formed on the inner peripheral surface of the cylinder 21 so as to be swingable in the circumferential direction. For this reason, the vane 23 does not leave the cylinder 21.

Therefore, in the compression mechanism unit 20 of the present embodiment, the compression chamber V is formed by the space surrounded by the inner wall surface of the cylinder 21, the outer peripheral surface of the rotor 22, and the plate surface of the vane 23. That is, the compression chamber V formed between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the rotor 22 is partitioned by the vane 23.

The low-pressure refrigerant sucked from the suction port 12a formed in the sub housing 12 is the housing side suction passage 13a → the shaft side suction passage 24b (→ the shaft side suction hole 24a) → the rotor side suction passage 22b (→ the circumferential suction). It flows in the order of the passage 22c) and is sucked into the compression chamber V.

The high-pressure refrigerant compressed in the compression chamber V flows out from the discharge hole 252 formed in the second side plate 25 b to the internal space of the housing 10 and is discharged from the discharge port 11 a formed in the main housing 11. The discharge hole 252 is formed so as to communicate with the compression chamber V displaced to a predetermined position.

Further, the second side plate 25b is provided with a discharge valve that suppresses the refrigerant flowing out from the discharge hole 252 to the internal space of the housing 10 from flowing back to the compression chamber V through the discharge hole 252. .

Next, the operation of the compressor 1 of this embodiment will be described with reference to FIG. FIG. 5 is an explanatory view continuously showing changes in the compression chamber V accompanying the rotation of the cylinder 21 in order to explain the operating state of the compressor 1. Furthermore, in the sectional view corresponding to each rotation angle θ in FIG. 5, the cylinder 21, the rotor 22, the vane 23, and the like in the sectional view equivalent to FIG. 3 are schematically shown.

Further, in FIG. 5, the reference numerals of the respective constituent members are attached to the cross-sectional view corresponding to the rotation angle θ = 0 of the cylinder 21 for clarity of illustration. Further, in FIG. 5, for the sake of clarification, the compression chamber V that is in the suction stroke (the process of expanding the volume) is indicated by the symbol Vs, and the compression chamber V is the compression process (the process of reducing the volume). The chamber V is indicated by the symbol Vd.

First, when the rotation angle θ is 0 °, the contact point C3 and the hinge portion 23a of the vane 23 overlap. In this state, most of the vanes 23 are accommodated in the grooves 22 a of the rotor 22. Further, a compression chamber Vs having a maximum suction stroke is formed on the front side in the rotation direction of the vane 23, and a compression chamber Vs having a minimum suction stroke (that is, a volume of 0) is formed on the rear side in the rotation direction of the vane 23. ing.

As the rotation angle θ increases from 0 °, the cylinder 21, the rotor 22, and the vane 23 are displaced as shown in the rotation angle θ = 30 ° to 330 ° in FIG. The volume of the compression chamber Vs in the suction stroke formed on the side increases. As a result, the low-pressure refrigerant that has flowed out of the shaft-side suction passage 24b flows into the compression chamber Vs in the suction stroke via the rotor-side suction passage 22b and the circumferential suction passage 22c.

When the rotation angle θ reaches 360 ° (that is, when the rotation angle θ returns to 0 °), the compression chamber Vs in the suction stroke on the front side in the rotation direction of the vane 23 becomes the maximum volume. Further, when the rotation angle θ increases from 360 °, the communication between the compression chamber Vs of the suction stroke and the rotor side suction passage 22b whose volume is increased at the rotation angle θ = 0 ° to 360 °, and the compression chamber of the suction stroke Communication between Vs and the circumferential suction passage 22c is blocked. Thereby, the compression chamber Vd of the compression stroke is formed on the front side in the rotation direction of the vane 23.

As the rotation angle θ increases from 360 °, the compression chamber Vd of the compression stroke formed on the front side in the rotation direction of the vane 23 as shown by the point hatching at the rotation angle θ = 390 ° to 690 ° in FIG. The volume of is reduced.

When the refrigerant pressure in the compression chamber Vd during the compression stroke exceeds the valve opening pressure of the discharge valve disposed in the second side plate 25b, the discharge valve opens, and the refrigerant in the compression chamber Vd during the compression stroke passes through the housing 10 It flows into the internal space. The high-pressure refrigerant that has flowed into the internal space of the housing 10 is discharged from the discharge port 11 a of the housing 10.

Therefore, in the compressor 1 of the present embodiment, as the rotation angle θ increases, the volume of the compression chamber V changes as shown in FIG. As shown in FIG. 7, in the suction stroke, the refrigerant pressure in the compression chamber V becomes equal to the low-pressure side refrigerant pressure of the cycle, and in the compression stroke, the refrigerant pressure in the compression chamber V becomes the high-pressure side refrigerant of the cycle. The pressure can be increased to a pressure equivalent to the pressure.

Here, in the above description, in order to clarify the operation mode of the compressor 1, the change in the compression chamber V while the rotation angle θ changes from 0 ° to 720 ° has been described. The refrigerant suction stroke described when θ changes from 0 ° to 360 ° and the refrigerant compression stroke described when the rotation angle θ changes from 360 ° to 720 ° are simultaneously performed when the cylinder rotates once. Done.

As described above, the compressor 1 of the present embodiment can suck, compress, and discharge a refrigerant that is an example of a fluid to be compressed in a refrigeration cycle. Furthermore, according to the compressor 1 of this embodiment, since the compression mechanism part 20 is arrange | positioned at the inner peripheral side of the electric motor part 30, size reduction as the compressor 1 whole can be achieved.

Further, according to the compressor 1 of the present embodiment, since the circumferential suction passage 22c is formed on the outer peripheral surface of the rotor 22, an increase in energy loss of the compressor 1 can be suppressed.

This will be described in detail with reference to FIGS. FIG. 8 is an explanatory diagram showing changes in the compression chamber V in the comparative compressor in which the circumferential suction passage 22c is not formed with respect to the compressor 1 of the present embodiment. More specifically, FIG. 8 shows a drawing corresponding to the rotation angles θ = 0 ° and θ = 30 ° of FIG.

Also in this comparative compressor, when the rotation angle θ is 0 °, the contact point C3 and the hinge portion 23a of the vane 23 overlap each other, and the minimum volume (that is, the rearward direction of the vane 23 in the rotation direction) , The compression chamber Vs of the suction stroke having a volume of 0) is formed. Further, as the rotation angle θ increases from 0 °, the volume of the compression chamber Vs in the suction stroke formed on the rear side in the rotation direction of the vane 23 increases as shown by the rotation angle θ = 30 ° in FIG. To do.

However, in the comparative compressor, since the circumferential suction passage 22c is not formed, the rotor-side suction passage 22b does not communicate with the compression chamber V in the suction stroke until the rotation angle θ increases to about 30 °. For this reason, as shown in FIG. 9, in the suction stroke of the comparative compressor, the refrigerant pressure in the compression chamber V decreases until the rotation angle θ increases to about 30 °. Such a pressure drop causes the energy loss of the compressor to increase.

On the other hand, in the compressor 1 of the present embodiment, the circumferential suction passage 22c is formed, so that the fluid to be compressed can be quickly flowed into the compression chamber V that has become the suction stroke. Therefore, it is possible to suppress a pressure drop from occurring in the compression chamber V immediately after the intake stroke, and to suppress an increase in energy loss of the cylinder rotary compressor.

Further, in the compressor 1 of the present embodiment, the notch formed by notching the outer peripheral surface of the rotor 22 functions as an example of the circumferential suction passage 22c. Can be formed. It is desirable that the circumferential suction passage 22c be formed as close as possible to the groove portion 22a from the outlet side of the rotor side suction passage 22b to the rear of the rotation within a processable range.
(Second Embodiment)
In the present embodiment, as shown in FIG. 10, an example in which the circumferential suction passage 21a is changed with respect to the first embodiment will be described.

Specifically, in the present embodiment, the circumferential suction passage 22c formed in the rotor 22 is abolished, and the axially central portion of the inner circumferential surface of the cylinder 21 is cut away (scraped off) in the circumferential direction (rotation direction). The notch formed by the above functions as an example of the circumferential suction passage 21a. FIG. 10 is a drawing corresponding to FIG. 3 of the first embodiment, and the same or equivalent parts as in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

Furthermore, the circumferential suction passage 21a is formed in a range overlapping with the circumferential suction passage 22c of the first embodiment when viewed from the radial direction. Other configurations and operations are the same as those in the first embodiment. Therefore, even in the compressor 1 in which the circumferential suction passage 21a is formed on the cylinder 21 side as in the present embodiment, the same effects as in the first embodiment can be obtained.
(Third embodiment)
In the present embodiment, as shown in the cross-sectional view of FIG. 11, an example will be described in which the groove 22d, the rotor-side suction passage 22b, and the vane 23b formed in the rotor 22 are changed with respect to the first embodiment.

Specifically, the groove portion 22d of the present embodiment has a sliding surface of the vane 23b (friction surface with the vane 23) with respect to the radial direction of the rotor 22 when viewed from the axial direction of the eccentric shaft C2. It is inclined. More specifically, in the groove 22d, the sliding surface of the vane 23b is inclined in the rotational direction from the inner peripheral side toward the outer peripheral side. For this reason, the vane 23 b fitted in the groove 22 d is also displaced in a direction inclined with respect to the radial direction of the rotor 22.

Furthermore, the rotor-side suction passage 22b is also inclined with respect to the radial direction of the rotor 22 when viewed from the axial direction of the eccentric shaft C2, similarly to the groove portion 22d. Moreover, the structure corresponding to the hinge part 23a of 1st Embodiment is not formed in the vane 23b of this embodiment. For this reason, the vane 23 b is disposed so that the outer peripheral end portion is slidable with respect to the inner peripheral surface of the cylinder 21. Other configurations are the same as those of the first embodiment.

Next, the operation of the compressor 1 of this embodiment will be described with reference to FIG. FIG. 12 is a drawing corresponding to FIG. 5 of the first embodiment, and the rotation angle θ is 0 ° (360 °), 90 ° (450 °), 180 ° (540 °), 270 ° (630 °). The state at the time of becoming is illustrated.

First, when the rotation angle θ is 0 °, the contact point C3 and the outer peripheral end of the vane 23b overlap. In this state, most of the vane 23 b is accommodated in the groove 22 d of the rotor 22. Further, similarly to the first embodiment, a compression chamber Vs having a maximum volume suction stroke is formed on the front side in the rotation direction of the vane 23b, and a minimum volume (that is, the volume is 0) is suctioned on the rear side in the rotation direction of the vane 23. A compression chamber Vs for the stroke is formed.

As the rotation angle θ increases from 0 °, the cylinder 21, the rotor 22, and the vane 23b are displaced as shown in the rotation angle θ = 90 ° to 270 ° in FIG. The volume of the compression chamber Vs in the suction stroke formed on the side increases. Then, the low-pressure refrigerant that has flowed out of the shaft-side suction passage 24b flows into the compression chamber Vs of the suction stroke through the rotor-side suction passage 22b and the circumferential suction passage 22c.

At this time, since the centrifugal force accompanying the rotation of the rotor 22 acts on the vane 23b, the outer peripheral end of the vane 23b is pressed against the inner peripheral surface of the cylinder 21. Thereby, the compression chamber V (Vs, Vd) formed between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the rotor 22 is partitioned by the vane 23b.

Further, as the rotation angle θ increases from 360 °, compression of the compression stroke formed on the front side in the rotation direction of the vane 23b as shown by the point hatching at the rotation angle θ = 450 ° to 630 ° in FIG. The volume of the chamber Vd is reduced. As in the first embodiment, the high-pressure refrigerant compressed in the compression chamber Vd in the compression stroke is discharged from the discharge port 11a of the housing 10.

As described above, according to the compressor 1 of the present embodiment, the refrigerant (fluid) can be sucked, compressed, and discharged. Furthermore, according to the compressor 1 of the present embodiment, since the circumferential suction passage 22c is formed, an increase in energy loss of the cylinder rotary compressor can be suppressed as in the first embodiment.

In the compressor 1 of the present embodiment, the outer peripheral side tip of the vane 23b is slid on the inner peripheral surface of the cylinder 21. According to this, unlike the configuration in which the hinge portion 23a of the vane 23 is swingably supported in the groove portion of the cylinder 21, there is no possibility that the vane 23 and the cylinder 21 are seized. Therefore, the reliability of the compressor 1 as a whole can be improved.

Further, in the compressor 1 of the present embodiment, the surface on which the vane 23b slides in the groove 22d is inclined with respect to the radial direction of the rotor 22 when viewed from the axial direction of the eccentric shaft C2. According to this, the stroke amount (movable range) of the vane 23b can be increased as compared with the case where the sliding surface of the vane 23b is formed in parallel with the radial direction. Therefore, the compression ratio of the compressor 1 can be increased.

However, as in this embodiment, if the surface of the groove 22d on which the vane 23b slides is inclined with respect to the radial direction of the rotor 22, the outlet of the rotor-side suction passage 22b and the suction stroke with the minimum volume are performed. The distance from the compression chamber V tends to be increased. Therefore, in the compressor 1 of the present embodiment, the pressure drop in the compression chamber V during the suction stroke, which has been described with reference to FIGS. 8 and 9 of the first embodiment, is likely to occur.

Therefore, in the compressor 1 of the present embodiment, the formation of the circumferential suction passage 22c is extremely effective for suppressing an increase in energy loss of the cylinder rotary compressor. Further, in the present embodiment, the rotor-side suction passage 22b is also inclined with respect to the radial direction of the rotor 22 in the same manner as the groove portion 22d, so that the outlet of the rotor-side suction passage 22b and the suction stroke of the minimum volume are reduced. The compression chamber V can be brought closer. As a result, it is possible to cause the refrigerant to flow into the compression chamber V that has become the suction stroke even more quickly.

The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present disclosure.

In the above-described embodiment, the example in which the cylinder rotary compressor 1 according to the present disclosure is applied to the refrigeration cycle device of the vehicle air conditioner has been described. However, the application of the cylinder rotary compressor 1 according to the present disclosure is limited to this. Not. That is, the cylinder rotary compressor 1 according to the present disclosure can be applied to a wide range of uses as a compressor that compresses various fluids.

In the above-described embodiment, the example in which the same structure as the pin-hole type rotation prevention mechanism is adopted as the power transmission unit of the cylinder rotary compressor 1 is described, but the power transmission unit is not limited to this. For example, you may employ | adopt the thing similar to the Oldham ring type rotation prevention mechanism.

In the above-described embodiment, the example in which the notch formed by cutting out the outer peripheral surface of the rotor 22 or the inner peripheral surface of the cylinder 21 functions as the

circumferential suction passages

21a and 22c has been described. 21a and 22c are not limited to this. For example, the rotor 22 and the cylinder 21 may be bored to form a circumferential suction passage.

In the above-described embodiment, the cylinder rotary compressor 1 including one

vane

23, 23b has been described, but the cylinder rotary compressor 1 including a plurality of

vanes

23, 23b may be used. In this case, since a plurality of compression chambers V are formed, a plurality of

circumferential suction passages

21a, 22c for promptly introducing the fluid to be compressed into each compression chamber V may be formed.

In addition, the constituent elements disclosed in the above embodiments may be appropriately combined within a practicable range. For example, the circumferential suction passage 21a described in the second embodiment may be applied to the compressor 1 of the third embodiment. Furthermore, in the compressor 1 described in the first and third embodiments, a circumferential suction passage 21 a may be formed in both the cylinder 21 and the rotor 22.

Although the present disclosure has been described based on the embodiments, it is understood that the present disclosure is not limited to the embodiments and structures. The present disclosure includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, as well as other combinations and forms including only one element, more or less, are within the scope and spirit of the present disclosure.

Claims

A cylindrical cylinder (21) rotating around a central axis (C1);
A cylindrical rotor (22) disposed inside the cylinder (21) and rotating about an eccentric shaft (C2) eccentric with respect to a central axis (C1) of the cylinder (21);
A shaft (24) rotatably supporting the rotor (22);
A compression chamber provided between the outer peripheral surface of the rotor (22) and the inner peripheral surface of the cylinder (21), which is slidably fitted into grooves (22a, 22d) provided in the rotor (22). (V) and vanes (23, 23b) for partitioning,
The shaft (24) has a shaft side suction passage (24b) through which a fluid to be compressed flowing from outside flows.
The rotor (22) has a rotor side suction passage (22b) for guiding the compression target fluid flowing out from the shaft side suction passage (24b) to the compression chamber (V).
At least one of the rotor (22) and the cylinder (21) causes the compression target fluid that has flowed out of the rotor side suction passage (22b) to enter the suction stroke from the outlet of the rotor side suction passage (22b). A cylinder rotary compressor having circumferential suction passages (21a, 22c) leading to the chamber (V).
The cylinder according to claim 1, wherein the circumferential suction passage (21a, 22c) includes a notch provided in at least one of an outer peripheral surface of the rotor (22) and an inner peripheral surface of the cylinder (21). Rotary compressor.
When viewed from the axial direction of the eccentric shaft (C2), the surface of the groove (22d) on which the vane (23b) slides is inclined with respect to the radial direction of the rotor (22). Item 3. The cylinder rotary compressor according to Item 1 or 2.
Furthermore, a power transmission unit (221, 251) for transmitting the rotation of the cylinder (21) to the rotor (22) is provided,
When viewed from the axial direction of the eccentric shaft (C2), the vane (23, 23b) is arranged such that its outer peripheral tip is slidable with respect to the inner peripheral surface of the cylinder (21). The cylinder rotation type compressor according to any one of claims 1 to 3.