WO2014024517A1

WO2014024517A1 - Vane compressor

Info

Publication number: WO2014024517A1
Application number: PCT/JP2013/059582
Authority: WO
Inventors: 関屋　慎; 雷人河村; 英明前山; 高橋　真一; 辰也佐々木; 幹一朗杉浦
Original assignee: 三菱電機株式会社
Priority date: 2012-08-06
Filing date: 2013-03-29
Publication date: 2014-02-13
Also published as: JP6016924B2; JPWO2014024517A1

Abstract

A vane compressor has: a substantially hollow cylindrical cylinder; a rotor shaft having a solid cylindrical rotor section which moves in a rotational manner within the cylinder and also having a rotating shaft section which transmits rotational force to the rotor section; and vanes disposed within the rotor section and having vane tip sections which are formed in a circular-arc shape facing outward. Out of the abovementioned elements, the cylinder is provided with an injection port for injecting a refrigerant into a compression chamber from the outside of the compressor. The circumferential width of the opening of the injection port is set to be less than or equal to the circumferential width of the vanes.

Description

Vane type compressor

This invention relates to a vane type compressor.

Compressors have long been required to improve heating and cooling capacity. For this purpose, generally known is a method of increasing the discharge capacity of the compressor and improving the heating and cooling capacity by providing an injection port in the compression chamber and injecting refrigerant from the outside into the compression chamber via the injection port. It has been. In the vane type compressor, for example, a structure as shown in Patent Document 1 has been proposed. Patent Document 1 discloses that a discharge port is increased by providing an injection port that opens to a compression chamber on a side surface of a cylinder and introducing a high-pressure refrigerant into the compression chamber.

On the other hand, in recent years, a vane compressor has also been improved in efficiency from the viewpoint of improving energy saving. For example, in Patent Document 2, the vane is rotated around the center of the inner peripheral surface of the cylinder, and the vane tip and the cylinder are separated from each other. The structure which reduces vane tip sliding loss by making non-contact is proposed.

From the above, as a method of simultaneously realizing energy saving improvement and heating and cooling capacity improvement, in a vane type compressor having a structure as shown in Patent Document 2, an injection port that opens to the compression chamber is provided on the side of the cylinder, and a high pressure It is optimal to introduce the refrigerant into the compression chamber to increase the discharge capacity.

Japanese Patent Laid-Open No. 61-64526 (page 22, FIGS. 6 to 9) International Publication No. 2012/023426 (Page 8, FIG. 2, FIG. 3 and Page 16, FIG. 9)

However, in the vane type compressor, when the injection port that opens to the compression chamber is provided on the side surface of the cylinder, the vane straddles the vane tip from the high pressure side compression chamber to the low pressure side compression chamber when the vane passes through the injection port. The refrigerant will leak. As a result, there is a problem that leakage loss increases and performance deteriorates.

The present invention has been made to solve the above problems, and minimizes the leakage of refrigerant from the high pressure side compression chamber to the low pressure side compression chamber when the vane passes through the injection port. The vane type compressor which can do is provided.

A vane compressor according to the present invention is installed in a cylindrical cylinder, a rotor shaft having a columnar rotor portion that rotates in the cylinder, a rotating shaft portion that transmits a rotational force to the rotor portion, and the rotor portion. And a plate-like vane portion that is held so as to rotate about the center of the inner peripheral surface of the cylinder and has a tip-like vane portion that faces the inner peripheral surface of the cylinder in a non-contact manner. It has an injection port, and the width of the opening formed on the cylinder inner peripheral surface side of the injection port is formed to be equal to or less than the width of the vane in the circumferential direction.

According to the vane type compressor of the present invention, the vane rotates around the center of the cylinder inner circumferential surface, and the distance from the vane tip to the cylinder inner circumferential surface is less than the width of the region where the distance is less than or equal to the minute distance. Therefore, even when the vane passes through the injection port, there is a region where the tip of the vane and the inner peripheral surface of the cylinder are separated from each other by a minute distance. It is possible to minimize the leakage of the refrigerant into the compression chamber, and it is possible to provide a highly efficient vane type compressor having an injection port.

Here, the vane tip can be opposed to the inner circumferential surface of the cylinder by a small distance because the vane rotates around the center of the inner circumferential surface of the cylinder, so the radius of the arc shape of the vane tip is increased. This is because it can be arbitrarily determined and can be made substantially equal to the radius of the inner peripheral surface of the cylinder.

On the other hand, in a general vane type compressor in which a vane as shown in Patent Document 1 rotates around the center of the rotor, the arc-shaped radius of the tip of the vane is the inner peripheral surface of the cylinder in order to always operate stably. It must be formed to be considerably smaller than the radius of (otherwise, the edge portion slides with the cylinder, not the arc portion of the vane tip, and the stable operation is impaired). Then, in patent document 1, the distance to the cylinder internal peripheral surface in a vane front-end | tip part will become large except a sliding location. For this reason, even if the circumferential width of the opening formed on the cylinder inner peripheral surface side of the injection port is reduced, refrigerant leakage from the high pressure side compression chamber to the low pressure side compression chamber increases. A highly efficient compressor cannot be realized.

It is a refrigerant circuit diagram which shows preferable Embodiment 1 of the air conditioning apparatus using the vane type compressor of this invention. It is a longitudinal cross-sectional view which shows Embodiment 1 of the vane type compressor of this invention. It is a disassembled perspective view of the compression element of the vane type compressor of FIG. FIG. 3 is a longitudinal sectional view taken along the line II in the vane type compressor of FIG. 2. It is a top view which shows an example of a 1st vane and a 2nd vane. It is a front view showing an example of the 1st vane and the 2nd vane. It is sectional drawing which shows rotation operation | movement of the

vane aligner parts

5c and 6c in the vane type compressor of FIG. It is sectional drawing which shows the compression operation of the vane type compressor of FIG. It is principal part sectional drawing which shows the periphery site | part of the vane part in FIG. It is principal part sectional drawing which shows the mode of the periphery site | part of a vane part when a vane front-end | tip part exists in the position periphery of an injection port. It is principal part sectional drawing which shows the mode of the periphery site | part of a vane part when a vane front-end | tip part exists in the position periphery of an injection port. It is principal part sectional drawing which shows the mode of the periphery site | part of a vane part when a vane front-end | tip part exists in the position periphery of an injection port. It is principal part sectional drawing which shows a mode when the conventional vane front-end | tip part opposes the opening part to the compression chamber of an injection port. It is a schematic diagram which shows an example of the shape of an injection port. It is a schematic diagram which shows another example of the shape of an injection port. It is sectional drawing which shows Embodiment 2 of the vane type compressor of this invention. FIG. 14 is a cross-sectional view taken along II in the vane type compressor of FIG. 13. FIG. 14 is a cross-sectional view showing another embodiment along II in the vane type compressor of FIG. 13. It is a schematic diagram which shows another embodiment of the vane front-end | tip part in the vane type compressor of this invention. It is a schematic diagram which shows another embodiment of the vane front-end | tip part in the vane type compressor of this invention.

Embodiment 1. FIG.
FIG. 1 is a refrigerant circuit diagram showing a preferred embodiment 1 of an air conditioner using a vane compressor of the present invention, and an air conditioner 500 will be described with reference to FIG. The air conditioner 500 includes a vane compressor 200, a condenser 201, a first expansion valve 202, a gas-liquid separator 203, an injection pipe 27, a second expansion valve 204, an evaporator 205, a four-way valve 206, and a flow rate adjustment. It consists of a valve 207 and a check valve 208. One end of the injection tube 27 is connected to the gas-liquid separator 203, and the other end communicates with the injection port 1 e of the vane compressor 200.

The low-pressure Ps refrigerant sucked into the vane compressor 200 from the suction pipe 26 is compressed by the vane compressor 200, and the high-pressure Pd refrigerant is discharged from the discharge pipe 24. Thereafter, the refrigerant passes through the four-way valve 206 and is cooled by the condenser 201 to be radiated and cooled. Then, the refrigerant is depressurized by the first expansion valve 202, enters a wet gas state, and then guided to the gas-liquid separator 203. The refrigerant guided to the gas-liquid separator 203 is separated into gas and liquid, and the gas is guided to the injection port 1e in the vane type compressor 200 through the injection pipe 27. On the other hand, the refrigerant liquid separated by the gas-liquid separator 203 is further decompressed by the second expansion valve 204. Thereafter, the refrigerant liquid is guided to the evaporator 205 and heated to a gas state, and then again sucked into the vane type compressor 200 through the suction pipe 26.

Here, a flow rate adjusting valve 207 is provided between the gas-liquid separator 203 and the injection pipe 27 so as to adjust the injection amount. When no injection operation is performed, the flow rate adjustment valve 207 is closed. A check valve 208 is provided between the flow rate adjustment valve 207 and the injection pipe 27. The check valve 208 prevents the gas from flowing backward from the compression element 101 toward the injection pipe 27 when the pressure in the compression element 101 in the vane type compressor 200 exceeds the intermediate pressure Pm of the refrigerant circuit. . When the pressure in the compression element 101 exceeds the intermediate pressure Pm of the refrigerant circuit, the check valve 208 blocks the gas flow, and the inflow of gas from the injection pipe 27 ends.

When the injection operation is not performed, the space from the injection port 1e to the check valve 208 of the vane type compressor 200 becomes a volume (dead volume) that becomes ineffective for gas compression. If the dead volume is large, the efficiency of the vane compressor 200 is reduced. Therefore, it is desirable to provide the check valve 208 as close to the vane compressor 200 as possible.

FIG. 2 is a longitudinal sectional view showing Embodiment 1 of the vane type compressor of the present invention, and the vane type compressor 200 will be described with reference to FIGS. 1 and 2. In FIG. 2, an arrow indicated by a solid line indicates a flow of fluid (gas refrigerant), and an arrow indicated by a broken line indicates a flow of refrigerating machine oil 25. The vane type compressor 200 in FIG. 2 includes a hermetic container 103, a compression element 101 housed in the hermetic container 103, an electric element 102 that is positioned above the compression element 101 and drives the compression element 101, and a hermetic container 103. The oil sump 104 is provided at the bottom of the inside and stores the refrigerating machine oil 25.

The electric element 102 that drives the compression element 101 is constituted by, for example, a brushless DC motor. The electric element 102 includes a stator 21 that is fixed to the inner periphery of the hermetic container 103, and a rotor 22 that is disposed inside the stator 21 and uses a permanent magnet. Electric power is supplied to the stator 21 from a glass terminal 23 fixed to the upper surface of the hermetic container 103 by welding. A suction pipe 26 is attached to the side surface of the sealed container 103, and a discharge pipe 24 is attached to the upper surface.

FIG. 3 is an exploded perspective view showing an example of the compression element 101 in the vane compressor 200 of FIGS. 1 and 2, and FIG. 4 is a II longitudinal sectional view of the vane compressor 200 of FIG. The compression element 101 will be described with reference to FIGS. The case where two vanes are provided in the vane type compressor 200 shown in FIGS. 2 to 4 is illustrated.
(1) Cylinder 1: The overall shape is cylindrical, and both ends in the axial direction are open. Here, the term “cylindrical” includes the case of a substantially cylindrical shape such as a slight concave portion. A part of the cylinder inner peripheral surface 1b is provided with a notch 1c penetrating in the axial direction and recessed in the circumferential direction of the cylinder inner peripheral surface 1b. A suction port 1a communicating with the suction pipe 26 is formed in the notch 1c. As shown in FIG. 4, the notch 1c is provided from the vicinity of the closest point 32 to a range of point B where the vane tip 5b of the first vane 5 and the cylinder inner peripheral surface 1b face each other. The cylinder 1 is provided with a discharge port 1d for discharging a fluid (gas). The discharge port 1d is provided on the side facing the frame 2 in the vicinity of the closest contact point 32 with the rotor portion 4a and on the opposite side of the suction port 1a with the closest contact point 32 interposed therebetween. Further, an injection port 1e is provided on the cylinder inner peripheral surface 1b at a position farther from the closest contact 32 than the discharge port 1d. The injection port 1 e penetrates in the radial direction and is connected to the injection tube 27 through the sealed container 103. Further, an oil return hole 1 f penetrating in the axial direction is provided in the outer peripheral portion of the cylinder 1.

(2) Frame 2: The section is substantially T-shaped, and the portion in contact with the cylinder 1 is substantially disk-shaped, and closes one opening (upper side in FIG. 2) of the cylinder 1. In addition, a circular recess 2a is formed on the opposing surface of the frame 2 facing the cylinder 1, and the recess 2a is formed so as to be substantially concentric with the cylinder inner peripheral surface 1b. A discharge port 2 d penetrating in the axial direction is provided in the frame 2, and the discharge port 2 d communicates with the discharge port 1 d of the cylinder 1. A discharge valve 41 and a discharge valve presser 42 for restricting the opening degree of the discharge valve 41 are attached to the surface of the discharge port 2d opposite to the cylinder 1. The frame 2 has a cylindrical main bearing portion 2c at the center.

(3) Cylinder head 3: The cross section is substantially T-shaped, the portion in contact with the cylinder 1 is substantially disk-shaped, and closes the other opening (lower side in FIG. 2) of the cylinder 1. A circular recess 3a is formed on the surface of the cylinder head 3 facing the cylinder 1, and the recess 3a is formed so as to be substantially concentric with the cylinder inner peripheral surface 1b. A cylindrical main bearing portion 3 c is provided at the center of the cylinder head 3.

(4) Rotor shaft 4: a cylindrical rotor portion 4a that rotates within the cylinder 1, and

rotating shaft portions

4b and 4c that transmit a rotational force to the rotor portion 4a. The rotor portion 4a and the

rotating shaft portion

4b, 4c has an integrated structure. The rotor portion 4a is formed with

bush holding portions

4d and 4e and

vane relief portions

4f and 4g that are substantially circular in cross section and penetrate in the axial direction. The bush holding part 4d and the vane relief part 4f communicate with each other, and the bush holding part 4e and the vane relief part 4g communicate with each other. Further, the bush holding portion 4 d, the bush holding portion 4 e, the vane escape portion 4 f, and the vane escape portion 4 g are formed at substantially symmetrical positions with respect to the center of the rotor shaft 4. Both end portions in the axial direction of the vane relief portion 4f and the vane relief portion 4g communicate with the concave portion 2a of the frame 2 and the concave portion 3a of the cylinder head 3, respectively. The rotating shaft portion 4 b is rotatably supported by the main bearing portion 2 c of the frame 2, and the rotating shaft portion 4 c is rotatably supported by the main bearing portion 3 c of the cylinder head 3. The rotor 4a rotates in the cylinder 1 by rotating in a state where the

rotating shafts

4b and 4c are supported by the

main bearings

2c and 3c. Further, as shown in FIG. 2, an oil pump 31 utilizing the centrifugal force of the rotor shaft 4 is provided at the lower end portion of the rotor shaft 4, and the oil pump 31 is provided at the shaft central portion of the rotor shaft 4. It communicates with the oil supply passage 4h extending in the direction. An oil supply path 4i is provided between the oil supply path 4h and the recess 2a, and an oil supply path 4j is provided between the oil supply path 4h and the recess 3a. An oil drain hole 4k (shown in FIG. 1) is provided at a position above the main bearing portion 2c of the rotary shaft portion 4b. The configurations of the oil pump 31 and the

oil supply passages

4h and 4j are described in detail in, for example, Japanese Patent Application Laid-Open No. 2009-264175.

(5) 1st vane 5: It attaches so that rocking | fluctuation with respect to the rotor part 4a, Comprising: The vane part 5a and the

vane aligner parts

5c and 5d are comprised. The vane part 5a is a substantially square plate-like member, and the tip part 5b is formed in a substantially arc shape. In particular, the vane tip 5b is configured such that, for example, an arc-shaped radius is substantially the same as the radius of the cylinder inner peripheral surface 1b. The

vane aligner portions

5c and 5d are members each formed in an arc shape. The vane aligner portion 5c is fixed to the end surface of the vane portion 5a on the frame 2 side, and the vane aligner portion 5d is a cylinder head of the vane portion 5a. It is fixed to the end face on the 3 side.

(6) Second vane 6: The second vane 6 is attached so as to be swingable with respect to the rotor portion 4a, and includes a vane portion 6a and

vane aligner portions

6c and 6d. The vane part 6a is a substantially square plate-like member, and the tip part 6b is formed in a substantially arc shape. In particular, the vane tip 6b is configured such that, for example, an arc-shaped radius is substantially the same (or the same) as the radius of the cylinder inner peripheral surface 1b. The

vane aligner portions

6c and 6d are members each formed in an arc shape. The vane aligner portion 6c is attached to the end surface of the vane portion 6a on the frame 2 side, and the vane aligner portion 6d is the cylinder head of the vane portion 6a. It is attached to the end face on the 3 side.
Here, the vane aligner portion 5c and the vane aligner portion 6c are accommodated in the recess 2a of the frame 2 and supported so as to be swingable along the vane aligner bearing portion 2b formed of the outer peripheral surface of the recess 2a. Similarly, the vane aligner portion 5d and the vane aligner portion 6d are accommodated in the recess 3a of the cylinder head 3, and are supported so as to be swingable along the vane aligner bearing portion 2b that is the outer peripheral surface of the recess 2a.

(7) Bush 7, 8: It is composed of a pair of substantially semi-cylindrical members. The pair of bushes 7 are inserted with the vane portion 5a sandwiched between the bush holding portions 4d of the rotor portion 4a. Similarly, the pair of bushes 8 is inserted with the vane portion 6a sandwiched between the bush holding portions 4e of the rotor portion 4a. The

bushes

7 and 8 swing together with the

vane portions

5a and 6a about the

centers

7a and 8a, respectively, and hold the

vane portions

5a and 6a so as to be movable in the longitudinal direction.

5A is a plan view showing an example of the first vane 5 and the second vane 6, and FIG. 5B is a front view showing an example of the first vane 5 and the second vane 6. Each

vane

5 and 6 is demonstrated with reference to FIG. 5B. The vane portion 5a and the

vane aligner portions

5c and 5d are attached so that the center line in the width direction of the vane portion 5a passes through the center of the arc forming the

vane aligner portions

5c and 5d. Similarly, the vane portion 6a and the

vane aligner portions

6c and 6d are attached such that the center line in the width direction of the vane portion 6a passes through the center of the arc forming the

vane aligner portions

6c and 6d. The arcs of the

vane aligner portions

5c, 5d, 6c, and 6d are formed so as to be concentric with the cylinder inner peripheral surface 1b (recessed

portions

2a and 3a).

The distance rv from the outer peripheral side of the

vane aligner portions

5c and 5d of the first vane 5 to the vane tip 5b is defined as ra for the vane

aligner bearing portions

2b and 3b and rc for the inner peripheral surface 1b of the cylinder (FIG. 4). Reference) has the following relationship (1). Note that the minute distance δ in the equation (1) indicates a gap between the vane tip 5b and the cylinder inner peripheral surface 1b.
[Equation 1]
rv = rc−ra−δ (1)

When centrifugal force due to rotation is applied to the

vanes

5 and 6, the

vanes

5 and 6 move in the radial direction toward the outside of the rotor portion 4a, and the

vane aligner portions

5c, 5d and 6c, 6d are respectively vane aligner bearings. It slides on the

parts

2b and 3b.

At this time, because of the relationship of the expression (1), the

vane tip portions

5b and 6b and the cylinder inner peripheral surface 1b rotate in a state of being separated by a minute distance δ. The

vanes

5 and 6 and the cylinder inner peripheral surface 1b maintain a minute distance δ, so that the

vanes

5 and 6 partition the cylinder 1 into three spaces (suction chamber 9, intermediate chamber 10, compression chamber 11). ) (See FIG. 4). By setting the minute distance δ to be as small as possible (to the production limit), gas leakage from the vane tip 5b can be minimized.

FIG. 6 is a cross-sectional view showing an example of the rotation operation of the

vane aligner portions

5c and 6c, and an operation example of the vane compressor 200 will be described with reference to FIG. In FIG. 6, when the first vane 5 is positioned at the closest point 32 where the rotor portion 4a of the rotor shaft 4 and the cylinder inner peripheral surface 1b are closest, the angle is defined as “angle 0 °”. Also, the state after “angle 180 °” is not shown because when “angle 180 °” is reached, at the “angle 0 °”, the first vane 5 and the second vane 6 are interchanged. Thereafter, the same compression operation is performed from “angle 0 °” to “angle 135 °”.

First, in FIG. 6, the rotating shaft portion 4b of the rotor shaft 4 receives rotational power from the driving portion of the electric element 102, and the rotor portion 4a rotates in the cylinder 1 around the rotating shaft. Along with the rotation of the rotor portion 4a, the first vane 5 and the second vane 6 attached to the rotor portion 4a rotate. Then, the

vanes

5 and 6 receive a radial centrifugal force due to rotation, respectively, and the

vane aligner portions

5c, 6c and 5d and 6d slide on the vane

aligner bearing portions

2b and 3b, and the vane

aligner bearing portions

2b and 3b. Rotate around the center. Then, the

vane parts

5a and 6a rotate about the center of the cylinder inner peripheral surface 1b different from the rotation axis as the rotation axis. As the rotor 4a rotates, the

vanes

5a and 6a swing around the

centers

7a and 8a of the

bushes

7 and 8 while changing their orientations so that the longitudinal directions thereof are directed toward the center of the cylinder 1, respectively. In other words, the longitudinal direction of the

vane portions

5a and 6a is maintained in the direction facing the center of the cylinder inner peripheral surface 1b regardless of the rotation angle of the rotor portion 4a. Accordingly, the

vanes

5 and 6 can always be held with a certain inclination with respect to the normal direction of the cylinder inner peripheral surface 1b or the normal direction of the cylinder inner peripheral surface 1b, and the

vane tip portions

5b and 6b The arc-shaped normal line and the normal line of the cylinder inner peripheral surface 1b can always perform the compression operation in a substantially coincident state.

FIG. 7 is a cross-sectional view showing the compression operation of the vane compressor 200, and an example of the compression operation of the vane compressor 200 will be described with reference to FIG. The angle shown in FIG. 7 is the same as the angle shown in FIG. First, at the “angle of 0 °”, the right intermediate chamber 10 partitioned by the closest contact 32 and the second vane 6 is in communication with the suction port 1a through the notch 1c, and gas is discharged from the suction port 1a. Is inhaled. On the other hand, the left space partitioned by the closest point 32 and the second vane 6 becomes the compression chamber 11 communicating with the discharge port 1d and the injection port 1e.

At “angle 45 °”, the space partitioned by the first vane 5 and the closest point 32 becomes the suction chamber 9. The intermediate chamber 10 partitioned by the first vane 5 and the second vane 6 is in communication with the suction port 1a through the notch 1c, as in the case of “angle 0 °”, and is used for gas suction. Continue. The volume of the intermediate chamber 10 is larger than that at the “angle 0 °”, and the volume of the compression chamber 11 partitioned by the second vane 6 and the closest point 32 is smaller than that at the “angle 0 °”. On the other hand, the gas in the compression chamber 11 is compressed and the pressure gradually increases. Further, the suction chamber 9 is in communication with the suction port 1a through the notch 1c. “Angle 45 °” indicates a case where the pressure in the compression chamber 11 is between the intermediate pressure Pm and the high pressure Pd.

At “angle 90 °”, the vane tip 5b of the first vane 5 overlaps with the point B on the cylinder inner peripheral surface 1b, so that the intermediate chamber 10 is not in communication with the suction port 1a. Therefore, the gas suction in the intermediate chamber 10 is completed. In this state, the volume of the intermediate chamber 10 is substantially maximum. On the other hand, the volume of the suction chamber 9 becomes larger than when the angle is 45 °, and the suction of gas from the suction port 1a is continued. Further, since the volume of the compression chamber 11 is further smaller than that at the “angle 45 °”, the pressure in the compression chamber 11 is further increased. Here, when the pressure in the compression chamber 11 exceeds the predetermined pressure Pd, the discharge valve 41 is opened, and the gas in the compression chamber 11 is discharged into the sealed container 103 through the

discharge ports

1d and 2d. The gas discharged into the sealed container 103 passes through the electric element 102 and is discharged to the outside (the high pressure Pd side of the refrigerant circuit in FIG. 1) from the discharge pipe 24 fixed (welded) to the upper part of the sealed container 103 ( (Indicated by the solid line in FIG. 2). Therefore, the pressure in the sealed container 103 is a discharge pressure of a predetermined pressure Pd. The “angle 90 °” indicates a case where the pressure in the compression chamber 11 is a high pressure Pd (or a case where the pressure exceeds the high pressure Pd).

At “angle 135 °”, the volume of the intermediate chamber 10 is smaller than that at “angle 90 °”, and the gas pressure increases. Further, the volume of the suction chamber 9 becomes larger than that at the “angle 90 °”, and the suction is continued. Here, the vane portion 6 a of the second vane 6 passes through the injection port 1 e, and the injection port 1 e is in communication with the intermediate chamber 10. For this reason, gas flows into the intermediate chamber 10 from the injection port 1e. On the other hand, the discharge port 1d remains in communication with the compression chamber 11, the discharge valve 41 is open, and the volume of the compression chamber 11 becomes even smaller than when the angle is 90 °. 11 is discharged. Thereafter, when the second vane 6 passes through the discharge port 1d, a little high-pressure Pd gas remains in the compression chamber 11 (a loss occurs). When the compression chamber 11 disappears at an “angle of 180 ° (= 0 °)”, the high-pressure Pd gas changes into a low-pressure Ps gas in the suction chamber 9. At “angle 180 °”, the suction chamber 9 moves to the intermediate chamber 10, the intermediate chamber 10 moves to the compression chamber 11, and the compression operation is repeated thereafter.

Next, the flow of the refrigerating machine oil 25 during the compression operation will be described. FIG. 8 is a cross-sectional view of the main part showing the peripheral portion of the vane portion 5 a of the first vane 5. In the figure, arrows indicated by solid lines indicate the flow of the refrigerating machine oil 25. In addition, although illustrated about the 1st vane 5, it is the same also about the 2nd vane 6. FIG. First, as shown by the broken line in FIG. 2, the refrigeration oil 25 is sucked up from the oil sump 104 by the oil pump 31 and sent out to the oil supply passage 4h. The refrigerating machine oil 25 sent out to the oil supply passage 4h is sent out to the recess 2a of the frame 2 and the recess 3a of the cylinder head 3 through the oil supply passage 4i and the oil supply passage 4j, respectively.

The refrigerating machine oil 25 fed to the

recesses

2a and 3a (see FIG. 2) lubricates the vane

aligner bearing portions

2b and 3b and is supplied to the

vane relief portions

4f and 4g communicating with the

recesses

2a and 3a. Since the pressure in the sealed container 103 is the discharge pressure that is the high pressure Pd, the pressure in the

recesses

2a and 3a and the

vane relief portions

4f and 4g is also the discharge pressure. A part of the refrigerating machine oil 25 fed to the

recesses

2 a and 3 a is supplied to the main bearing portion 2 c of the frame 2 and the main bearing portion 3 c of the cylinder head 3.

The pressure in the vane relief portion 4f is a discharge pressure, which is higher than the pressure in the suction chamber 9 and the intermediate chamber 10. For this reason, the refrigerating machine oil 25 is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force while lubricating the sliding surface between the side surface of the vane portion 5a and the bush 7. The refrigerating machine oil 25 is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force while lubricating the sliding portion between the bush 7 and the bush holding portion 4d of the rotor shaft 4. A part of the refrigerating machine oil 25 sent out to the intermediate chamber 10 flows into the suction chamber 9 while sealing the gap between the vane tip 5b and the cylinder inner peripheral surface 1b.

In FIG. 8, the case where the space partitioned by the first vane 5 is the suction chamber 9 and the intermediate chamber 10 has been shown, but the rotation is progressed so that the space partitioned by the first vane 5 is separated from the intermediate chamber 10. The same applies to the compression chamber 11. That is, even when the pressure in the compression chamber 11 reaches the same discharge pressure as the pressure of the vane escape portion 4f, the refrigerating machine oil 25 is sent out toward the compression chamber 11 by centrifugal force. Although the above operation is shown for the first vane 5, the same operation is performed for the second vane 6.

As shown in FIG. 2, after the refrigerating machine oil 25 supplied to the main bearing portion 2 c is discharged into the space above the frame 2 through the gap of the main bearing portion 2 c, the oil return provided on the outer peripheral portion of the cylinder 1. It is returned to the oil sump 104 through the hole 1f. Further, the refrigerating machine oil 25 supplied to the main bearing portion 3c is returned to the oil sump 104 through the gap of the main bearing portion 3c. In addition, the refrigerating machine oil 25 sent to the suction chamber 9, the intermediate chamber 10, and the compression chamber 11 through the

vane relief portions

4f and 4g is finally discharged together with the gas from the

discharge ports

1d and 2d to the space above the frame 2. After that, the oil is returned to the oil sump 104 through an oil return hole 1 f provided in the outer peripheral portion of the cylinder 1. Of the refrigerating machine oil 25 delivered to the oil supply passage 4 h by the oil pump 31, the surplus refrigerating machine oil 25 is discharged from the oil drain hole 4 k above the rotor shaft 4 into the space above the frame 2, and then the cylinder 1 Is returned to the oil sump 104 through an oil return hole 1f provided in the outer periphery of the oil reservoir.

FIGS. 9A to 9C are cross-sectional views showing the main parts of the surrounding portion of the vane portion 6a when the vane tip portion 6b is located around the position of the injection port 1e. Referring to FIGS. 9A to 9C, the vane tip portion is shown. The relationship between the width of 6b and the injection port 1e will be described. Although the second vane 6 is illustrated and described in FIGS. 9A to 9C, the same applies when the first vane 5 passes through the injection port 1e.

The circumferential width Tw of the opening formed on the cylinder inner peripheral surface 1b side of the injection port 1e is equal to or smaller than the width Tp of the region where the distance from the vane tip 6b to the cylinder inner peripheral surface 1b is a minute distance δ or less. Is formed. In particular, in FIGS. 9A to 9C, the arcuate radius of the vane tip 6b is configured to have a curvature substantially equal to (or the same as) the radius of the cylinder inner peripheral surface 1b, and the opening of the injection port 1e. The width Tw of the portion is equal to or less than the width Tp of the entire facing surface of the vane tip 6b.

Here, as described above, the vane portion 6a rotates in a state where the vane tip portion 6b and the cylinder inner peripheral surface 1b form a gap by a minute distance δ. Then, as shown in FIGS. 9A to 9C, the vane tip 6b is surely passed from the time when the second vane 6 enters the opening of the injection port 1e until the second vane 6 completely covers the opening and then passes through the opening. There is always a region where the cylinder inner peripheral surface 1b faces. Therefore, even when the vane tip 6b passes through the opening, a gap larger than the minute distance δ does not occur as in the case of passing through another region. Thereby, the leakage through the gap between the vane tip 6b and the cylinder inner peripheral surface 1b from the compression chamber 11 to the intermediate chamber 10 can be suppressed very little. Therefore, when each of the

vanes

5 and 6 passes through the injection port 1e, the leakage of fluid does not increase, and a highly efficient vane compressor 200 having the injection port 1e with very little loss can be obtained.

That is, conventionally, as shown in FIG. 10, the radius of the arc shape constituting the vane tip 6b of the second vane 6 is formed to be considerably smaller than the radius of the cylinder inner peripheral surface 1b. For this reason, the width Tw of the opening portion of the injection port 1e becomes larger than the width Tp of the region where the distance from the vane tip portion 6b to the cylinder inner peripheral surface 1b is a minute distance δ or less. Further, the gap between the vane tip 6b and the cylinder inner peripheral surface 1b is a contact position 51 between the vane tip 6b and the cylinder inner peripheral surface 1b (in the axial direction where the injection port 1e of the cylinder inner peripheral surface 1b is not provided). As the position and the vane tip 6b move away from each other, the size increases. Then, as shown by a broken line in FIG. 10, since a leakage path from the compression chamber 11 to the intermediate chamber 10 is formed via the injection port 1e, leakage through the gap between the vane tip 6b and the cylinder inner peripheral surface 1b occurs. Will increase.

On the other hand, in FIGS. 9A to 9C, since the leakage of fluid does not increase when each of the

vanes

5 and 6 passes through the injection port 1e, a highly efficient vane type compressor having an injection port with very little loss. 200 can be obtained. In particular, the radius of the arc shape constituting the vane tip 6b of the second vane 6 is substantially the same (or the same) as the radius of the cylinder inner peripheral surface 1b, and the

vane tips

5b, 6b and the cylinder The gap between the inner peripheral surface 1b is a minute distance δ over the entire width of the

vane tip portions

5b and 6b (see equation (1)). This means that all the surfaces of the vane tip 6b facing the cylinder inner peripheral surface 1b can be set to a minute distance δ. For this reason, the highly efficient vane type compressor 200 which has the injection port 1e with very little loss using the vane part 6a which has the width Tp of the opposing surface larger than the width Tw of the opening part of the injection port 1e can be obtained. .

Here, as long as the width Tw of the opening of the injection port 1e is equal to or less than the width of the vane, the cross-sectional shape of the injection port 1e may be an arbitrary shape. For example, the opening of the injection port 1e may be formed in a circular shape or an oval shape in accordance with the shape of the injection tube 27. Alternatively, as shown in FIG. 11, the opening of the injection port 1 e is formed in a rectangular shape, and may be formed in a long hole shape whose width in the height direction is larger than the width Tw in the circumferential direction. . Even in this case, since the circumferential width Tw of the injection port 1e is smaller than the vane width Tp, the leakage from the

vane tip portions

5b and 6b can be minimized. Furthermore, since the cross-sectional area of the injection port 1e can be increased by using the elongated hole shape as shown in FIG. 11, the upper limit value of the injection amount can be increased, and the discharge capacity can be increased. Note that the cross-sectional area of the injection pipe 27 is formed to be approximately the same as the cross-sectional area of the injection port 1e is increased.

Furthermore, as shown in FIG. 12, a plurality of openings of the injection port 1 e may be provided in the height direction of the cylinder 1. In FIG. 12, three circular injection ports 1 e are formed with openings, and each opening is connected to an injection pipe 27 via three branch pipes 28. Even in this method, the total cross-sectional area of the injection port 1e can be increased, and the discharge capacity can be increased. In this case as well, the diameter (width Tw) of the circle of the injection port 1e is equal to or less than the width Tp of the

vane tip portions

5b and 6b. Moreover, although the case where there are three injection ports 1e is illustrated, any number may be provided. Even in this case, as long as the maximum circumferential width of the injection port 1e is equal to or less than the width of the vane, the cross section may have any shape.

Embodiment 2. FIG.
FIGS. 13 to 15 are sectional views showing Embodiment 2 of the vane type compressor of the present invention, and the vane type compressor 300 will be described with reference to FIGS. In addition, in the vane type compressor 300 of FIGS. 13-15, the site | part which has the same structure as the vane type compressor 200 of FIGS. 1-12 is attached | subjected the same code | symbol, and the description is abbreviate | omitted. 13 to 15 is different from the vane compressor 200 in that a check valve is provided in the injection port 1e.

Specifically, as shown in FIG. 14, a check valve attachment 61 is attached to the cylinder 1 on the outer diameter side of the circular injection port 1 e. The check valve fitting 61 is provided with an injection flow passage 61a penetrating in the radial direction, and the injection flow passage 61a opens into a space 1g provided between the check valve fitting 61 and the injection port 1e. Further, a check valve 62 and a check valve presser 63 for restricting the opening degree of the check valve 62 are attached to the check valve attachment 61 on the space 1g side which is the inner diameter side of the injection flow path 61a. ing. The outer end of the injection flow path 61a is connected to the injection pipe 27. In FIG. 13, the injection port 1e and the injection flow path 61a have the same size.

When the pressure in the compression chamber 11 is lower than the intermediate pressure Pm of the refrigerant circuit, the check valve 62 is opened due to the pressure difference, and the injection flow path 61a, the space portion 1g, and the injection port 1e are connected from the injection pipe 27. The refrigerant flows into the compression chamber 11 through it. Note that the gas continues to flow from the injection port 1e until the pressure in the compression chamber 11 exceeds the intermediate pressure Pm of the refrigerant circuit. On the other hand, when the pressure in the compression chamber 11 is higher than the intermediate pressure Pm of the refrigerant circuit, the check valve 62 is closed due to the pressure difference, and the refrigerant does not flow into the compression chamber 11. Thus, since the check valve 62 has the same function as the check valve 208 in the refrigerant circuit of FIG. 1, the check valve 208 in the refrigerant circuit becomes unnecessary.

In this embodiment, since the check valve 62 is provided closer to the compression chamber 11 than in the first embodiment, the dead volume that is ineffective for gas compression can be reduced. Thereby, the fall of the efficiency when not performing injection driving | operation becomes small. Further, by providing the check valve 62 in the compressor, the refrigerant circuit has a simple configuration.

In addition, in FIG. 14, although the opening part of the injection port 1e has illustrated about the case where it is circular shape, as shown in FIG. 15, it may be formed in the shape of a rectangular long hole. Also in this case, the injection flow rate can be increased by increasing the diameter of the injection flow path 61a by the amount by which the cross-sectional area of the injection port 1e is increased.

13 to 15, a valve called a reed valve is shown as the check valve 62. However, the type of the valve is not limited to this, and the pressure in the compression chamber 11 is lower than the intermediate pressure Pm. It may be of any type as long as it opens in the case and closes in the case of higher than the intermediate pressure Pm.

The embodiments of the present invention are not limited to the above embodiments. For example, in the first and second embodiments, the case where the number of vanes is two has been described. However, even when the number of vanes is one or three or more, the same configuration is obtained and the same effect can be obtained.

Moreover, in the air conditioning apparatus 500 of FIG. 1, although the refrigerant circuit which injects a refrigerant | coolant to the compression chamber 11 using the gas-liquid separator 203 was shown, it is not limited to this, For example, international publication 2011 / 013199A1 The refrigerant circuit which injects a refrigerant | coolant using an internal heat exchanger as described in above may be sufficient. Moreover, in each said embodiment, although illustrated about the case where a fluid (refrigerant) is gas, it may be a liquid refrigerant or a two-phase refrigerant | coolant of a liquid and gas.

Further, in the first and second embodiments, the oil pump 31 using the centrifugal force of the rotor shaft 4 has been shown. However, any form of the oil pump 31 may be used, for example, a volume described in Japanese Patent Application Laid-Open No. 2009-62820. A shape pump may be used as the oil pump 31.

Further, the

vane tip portions

5b and 6b and the cylinder inner peripheral surface 1b are illustrated in the case of a so-called non-contact method in which a rotational movement is performed with a small distance δ, but the

vane tip portions

5b and 6b and the cylinder inner peripheral surface are illustrated. A so-called contact method in which 1b slides (δ = 0) may be used. Even in this case, leakage of fluid (gas) can be eliminated by setting the circumferential width Tw of the injection port 1e to be equal to or smaller than the width Tp of the

vane tip portions

5b and 6b.

Further, in FIGS. 9A to 9C, the case where the width Tw of the opening of the injection port 1e is equal to or less than the width Tp of the entire facing surface formed in the

vane tip portions

5b and 6b is illustrated. As described above, in the vane tip portion 5b (6b), it is only necessary to be equal to or smaller than the width Tp of the region (sliding region) that is the minute distance δ or less in the facing surface facing the cylinder inner peripheral surface 1b. In other words, the vane tip portion 5b may be formed substantially the same as the radius of the cylinder inner peripheral surface 1b over the entire surface of the opposing surface, and the region of the width Tp of the opposing surface is the area of the cylinder inner peripheral surface 1b. It may be formed substantially the same as the radius, and may have a curved surface with a different curvature in part.

5A and 5B illustrate the case of the

vanes

5 and 6 in which the longitudinal direction of the

vane portions

5a and 6a and the normal direction of the arc-shaped vane aligner portion are orthogonal to each other, as shown in FIG. It may be inclined by a predetermined angle.

1 cylinder, 1a intake port, 1b cylinder inner surface, 1c notch, 1d discharge port, 1e injection port, 1f oil return hole, 1g space, 2 frame, 2a recess, 2b vane aligner bearing, 2c main bearing 2d discharge port, 3 cylinder head, 3a recess, 3b vane aligner bearing part, 3c main bearing part, 4 rotor shaft, 4a rotor part, 4b rotary shaft part, 4c rotary shaft part, 4d bush holding part, 4e bush holding part 4f vane relief part, 4g vane relief part, 4h oiling path, 4i oiling path, 4j oiling path, 4k oiling hole, 5th vane, 5a vane part, 5b vane tip, 5c vane aligner part, 5d vane Aligner part, 6 second vane, 6a vane part, 6b Tip, 6c vane aligner, 6d vane aligner, 7 bush, 7a bush center, 8 bush, 8a bush center, 9 suction chamber, 10 intermediate chamber, 11 compression chamber, 21 stator, 22 rotor, 23 Glass terminal, 24 discharge pipe, 25 refrigerating machine oil, 26 suction pipe, 27 injection pipe, 28 branch pipe, 31 oil pump, 32 nearest point, 41 discharge valve, 42 discharge valve presser, 51 contact position, 61 check valve fitting , 61a injection flow path, 62 check valve, 63 check valve presser, 101 compression element, 102 electric element, 103 sealed container, 104 oil sump, 200, 300 vane compressor, 201 condenser, 202 first expansion Valve, 203 gas-liquid separator, 204 second expansion valve, 205 evaporator, 206 Four-way valve, 207 Flow regulating valve, 208 Check valve, 500 Air conditioner, Ra Radius of vane aligner part outer circumference (recesses 2a, 3a), rc Radius of cylinder inner peripheral surface, rv Vane tip from outer circumference of vane aligner part , The width of the tip of the vane (opposite surface at the tip of the vane), the width of the opening of the Tw injection port, and the δ minute distance.

Claims

A cylindrical cylinder;
A rotor shaft having a cylindrical rotor portion that rotates in the cylinder and a rotating shaft portion that transmits a rotational force to the rotor portion, and a rotor shaft that is installed in the rotor portion and rotates around the center of the inner peripheral surface of the cylinder. A vane having a plate-like vane portion that is held and has a tip portion facing the cylinder inner peripheral surface in a non-contact manner;
With
The cylinder has an injection port for injecting fluid on a side surface,
A vane type compressor, wherein a circumferential width of an opening formed on the cylinder inner peripheral surface side of the injection port is formed to be equal to or smaller than a circumferential width of the vane.
The vane compressor according to claim 1, wherein the vane is supported so as to be rotatable and movable with respect to the rotor portion.
3. The vane type according to claim 1, wherein the opening of the injection port is formed such that a length in a height direction of the cylinder is larger than a width in the circumferential direction. Compressor.
The vane compressor according to any one of claims 1 to 3, wherein a plurality of the openings of the injection port are provided in a height direction of the cylinder.
The vane compressor according to any one of claims 1 to 4, wherein the opening of the injection port is formed in a circular shape or an elliptical shape.
The tip of the vane is formed in an arc shape,
The vane type compressor according to any one of claims 1 to 5, wherein a radius of the arc shape at a tip portion of the vane is substantially equal to a radius of an inner peripheral surface of the cylinder.
The vane compressor according to any one of claims 1 to 6, wherein a check valve is provided in the injection port.