JP3157137B2 - Gas compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a gas compressor mounted on a vehicle as a part of a car air conditioner system,
In particular, noise and vibration caused by the pressure pulsation of the high-pressure refrigerant gas and noise caused by the increase in the surface pressure at the vane tip and wear of the vane tip or the inner wall of the cylinder can be effectively prevented.

[0002]

2. Description of the Related Art Conventionally, this kind of gas compressor has a cylinder 1 having a substantially elliptical inner circumference as shown in FIG.
Side blocks 2 and 3 are attached to both end surfaces of the cylinder 1, and a rotor 4 is housed inside the cylinder 1.

The rotor 4 is rotatably provided via a rotor shaft 5 integrally formed with the rotor 4 and bearings 6 and 7 for supporting the front and rear ends of the rotor shaft 5.
A plurality of vane grooves 8 are formed on the outer peripheral surface of the rotor 4.
), And a vane 9 is slidably mounted in the vane groove 8.

An assembled structure comprising the cylinder 1, side blocks 2, 3, rotor 4, vane 9 and the like as described above is a compressor body 10, and this compressor body 10 is housed in a casing 11 which is open at one end. Have been. A front head 12 is attached to an open end of the casing 11, and a suction chamber 13 formed between the front head 12 and the side block 2 is provided inside the front head 12.
The rear space between the closed end of the casing 11 and the rear side block 3 is configured as a discharge chamber 14.

As shown in FIG. 5, the inner peripheral side of the cylinder 1 is divided into a plurality of small chambers by the inner wall of the cylinder 1, the inner surfaces of the side blocks 2, 3 and the outer peripheral surface of the rotor 4, and the vane 9, and the partition is formed. The small chamber is referred to as a compression chamber 15, and the volume repeatedly changes with the rotation of the rotor 4.
When the volume of the compression chamber 15 changes, the low-pressure refrigerant gas is sucked from the suction chamber 13 to the compression chamber 15 when the volume increases, and when the volume decreases, the low-pressure refrigerant in the compression chamber 15 decreases. The compression of the gas and the discharge of the high-pressure refrigerant gas from the compression chamber 15 to the discharge chamber 14 are performed.

As shown in FIG. 6, the suction of the low-pressure refrigerant gas into the compression chamber 15 is performed by the suction passage 21 provided in the front side block 2, the cylinder 1 and the rear side block 3. Suction passage 21 provided in the
21. The high-pressure refrigerant gas compressed in the compression chamber 15 flows through the discharge hole 22 of the cylinder 1 and the discharge valve 23 shown in FIG. The high-pressure refrigerant gas in the discharge chamber 24 that has flowed in this way further passes through the discharge passage 25 of the rear side block 3 and then flows into the discharge chamber 14 attached to the side block 3 as shown in FIG. To the discharge chamber 14 via the oil separator 16. Then, the high-pressure refrigerant gas in the discharge chamber 14 is discharged outside the machine via an external discharge port (not shown) of the casing 11.

The bottom of the discharge chamber 14 is an oil sump 17. The oil in the oil sump 17 is acted upon by the discharge pressure of the high-pressure refrigerant gas discharged into the discharge chamber 14. The lubrication of the bearing 7 is performed by pressure-feeding the oil from the third oil hole 18 to the bearing 7 on the rear end side of the rotor shaft 5. The oil in the oil sump 17 is diverted from the oil hole 18 in the rear side block 3 to the oil hole 18 in the cylinder 1, and then diverted to the oil hole 18 in the front side block 2.
, And is fed to the bearing 6 at the tip end side of the rotor shaft 5 to lubricate the bearing 6.

The oil that has reached the bearings 6 and 7 as described above is squeezed and depressurized when passing through the gap between the bearings 6 and 7, and then a pair of oils are provided on the rotor-side end surfaces of the side blocks 2 and 3. Is supplied to the back pressure chamber 20 at the bottom of the vane 9 through the saliage grooves 19, 19, and the pressure of the oil supplied to the back pressure chamber 20 pushes the vane 9 from the bottom toward the inner wall of the cylinder 1. It acts on the bottom of the vane 9 as back pressure (hereinafter referred to as “vane back pressure”).

That is, during the operation of the gas compressor, the total force of the vane back pressure due to the oil in the vane back pressure chamber 20 and the centrifugal force due to the rotation of the rotor 4 acts on the vane 9, and this total force causes the vane 9 to move. It is pressed against the inner wall of the cylinder 1.

[0010]

However, according to the conventional gas compressor as described above, the high-pressure refrigerant gas discharged into the discharge chamber 14 is discharged to the outside of the apparatus through the external discharge port of the casing 11. Since the pressure pulsation of the released gas is large, a loud noise or vibration may be generated in the vehicle equipped with this device based on the pressure pulsation of the released gas.

According to the conventional gas compressor, the vane 9 passes over the inlet 22a of the discharge hole 22 while being pressed against the inner wall of the cylinder 1. However, when the tip of the vane 9 reaches the inlet 22a of the discharge hole, The contact length between the tip of the vane 9 and the inner wall of the cylinder 1 is greatly reduced by the opening area of the discharge hole inlet 22a. For this reason, the discharge hole inlet 2 at the tip of the vane 9
2a, the surface pressure at the tip of the vane 9 increases, and the vane 9
The sliding friction between the tip and the inner wall of the cylinder 1 increases, and the vane tip 1 or the inner wall of the cylinder 1 is severely worn.
Noise such as loud contact noise may be generated.

Further, in the conventional gas compressor, the discharge chamber 24 is provided with a notch 24a on the outer peripheral surface side of the cylinder 1, a portion of the casing 11 on the outer peripheral surface side of the cylinder 1, and side blocks 2, 3 on the front and rear sides. The high-pressure refrigerant gas in the compression chamber 15 is discharged into such a discharge chamber 24.
Since the high-pressure refrigerant gas discharged into the inside directly collides with the inner surface of the casing 11 which is the inner wall of the discharge chamber 24 immediately after the discharge, noise due to the direct collision of this kind of discharged gas is also generated.

The present invention has been made in view of the above circumstances, and has as its object to generate noise and vibration generated due to pressure pulsation of high-pressure refrigerant gas, and to generate pressure due to an increase in surface pressure at the tip of a vane. It is an object of the present invention to provide a gas compressor which can effectively prevent noise and wear of vane tips or cylinder inner walls, has low noise and low vibration, and has excellent wear resistance.

[0014]

In order to achieve the above object, an invention according to a first aspect of the present invention comprises a cylinder having a substantially elliptical inner circumference, a side block attached to an end face of the cylinder, and an inner side of the cylinder. A rotor provided rotatably through a rotor shaft and its bearing, a vane groove formed on the outer peripheral surface of the rotor, a vane slidably mounted in the vane groove, and the cylinder, The partition is formed by a side block, a rotor, and a vane, and the volume of the compression chamber is repeatedly changed by the rotation of the rotor. By the volume change of the compression chamber, the low-pressure refrigerant gas sucked from the suction chamber is compressed to become a high-pressure refrigerant gas. And a discharge chamber provided on the outer peripheral surface side of the cylinder, and the compression chamber is provided in the cylinder. A discharge passage having one end opened to the discharge chamber side, one end opened to the discharge chamber side, a discharge passage opened at one end to the discharge chamber side, and the other end opened to the discharge chamber side. A side discharge hole formed in the block and having one end opened to the compression chamber side and the other end opened to the discharge passage side ;
After passing through the cylinder discharge hole and discharge chamber,
A first passage for the high-pressure refrigerant gas to the passage, and a direct passage from the compression chamber.
High pressure passing through the side discharge holes and reaching the discharge passage
A second flow path for refrigerant gas, wherein the first flow path and the second flow path are a high-pressure refrigerant gas flow after passing through the first flow path and a high-pressure refrigerant flow after passing through the second flow path The present invention is characterized in that there is a difference in a flow path length required to cancel each pressure pulsation of the gas flow with each other.

The invention according to claim 2 is characterized in that a throttle is provided in the middle of the first flow path .

According to the present invention, in the process of discharging the high-pressure refrigerant gas in the compression chamber to the discharge chamber side, the high-pressure refrigerant gas flow passes through two flow paths, that is, the cylinder discharge hole, the discharge chamber, and the discharge passage, and is discharged. The high-pressure refrigerant gas flow after passing through these two flow paths is once divided into a flow path reaching the chamber side and a flow path passing through the side discharge holes and the discharge passage and reaching the discharge chamber side. To join.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a gas compressor according to the present invention will be described below in detail with reference to FIGS.

The basic structure of the gas compressor according to the present embodiment, for example, as described with reference to FIGS. 4 and 5, has a cylinder 1 having a substantially elliptical inner circumference. Indicates that the side blocks 2 and 3 are attached, and that the rotor shaft 5 and its bearings 6 and 7 are provided inside the cylinder 1.
The rotor 4 is provided rotatably through the rotor. A vane groove 8 is formed on the outer peripheral surface of the rotor 4.
A vane 9 is slidably mounted in the vane groove 8, and an inner wall of the cylinder 1, inner surfaces of the side blocks 2 and 3, an outer peripheral surface of the rotor 4, and a vane 9
When the compression chamber 15 is formed by partitioning the refrigerant chamber, and when the refrigerant gas is confined in the compression chamber 15 and the volume of the compression chamber 15 changes in size due to the rotation of the rotor 4, the volume change causes the suction to occur. The suction of the low-pressure refrigerant gas from the chamber 13 to the compression chamber 15, the compression of the low-pressure refrigerant gas in the compression chamber 15, and the discharge of the high-pressure refrigerant gas from the compression chamber 15 to the discharge chamber 14 are performed in the same manner as before. The same reference numerals are given to the same members as those in the related art, and the detailed description thereof will be omitted.

In the gas compressor of this embodiment, as described above, the high-pressure refrigerant gas is discharged from the compression chamber 15 to the discharge chamber 14 (see FIGS. 4 and 5). Are constituted by cylinder discharge holes 30 and side discharge holes 31 as shown in FIG.

The cylinder discharge hole 30 is formed in the abdomen of the body of the cylinder 1. The inlet 30a of the cylinder discharge hole 30 is open to the compression chamber 15, while the outlet 30b of the cylinder discharge hole 30 is connected to the cylinder 30. , Is opened to the discharge chamber 24 on the outer peripheral surface side of the cylinder 1. Although not shown, a discharge valve that opens and closes by the high-pressure refrigerant gas pressure in the compression chamber 15 and a valve support thereof are provided on the outlet 30 b side of the cylinder discharge hole 30.

The discharge chamber 24 is defined by a notch 24a on the outer peripheral surface of the cylinder 1, a portion of the casing 11 on the outer peripheral surface of the cylinder 1, and side blocks 2, 3 on the front and rear sides. Are connected to the discharge chamber 14 through a discharge passage 25 formed in the rear side block 3. Further, the discharge passage 25 is constituted by a small hole portion 25a and a large hole portion 25b, and is provided such that the upstream side (discharge chamber 24 side) has a small diameter and the downstream side (discharge chamber 14 side) has a large diameter. ing.

The side discharge hole 31 is formed in the rear side block 3. The inlet 31 a of the side discharge hole 31 is open to the compression chamber 15 side like the cylinder discharge hole 30. Exit 31b of discharge hole 31
Unlike the cylinder discharge hole 30, the discharge hole 25 is opened in the thick hole portion 25 b of the discharge passage 25. Although not shown, on the outlet 31b side of the side discharge hole 31, similarly to the cylinder discharge hole outlet 30b, a discharge valve that opens and closes with high-pressure refrigerant gas pressure in the compression chamber 15 and a valve support thereof are provided. . That is, in the case of the present embodiment, the compression chamber 15
Directly communicates with the discharge passage 25 through the side discharge holes 30
The cylinder discharge hole 30 and the discharge chamber 24
And is configured to communicate with the discharge passage 25.
You.

An oil separator 16 attached to the rear side block 3 is disposed downstream of the discharge passage 25.

Therefore, the high-pressure refrigerant gas in the compression chamber 15 is discharged from the compression chamber 15 to the discharge chamber 14, and is discharged to the cylinder discharge holes 30, the discharge chamber 24, and the discharge passage 25.
A flow path R1 (hereinafter, also referred to as a “first flow path”) to reach the discharge path 25 through the side discharge holes 31 .
(Hereinafter also referred to as “second flow path”), and then the two high-pressure refrigerant gas flows merge before the oil separator 16 (see FIG. 4). The discharged refrigerant gas passes through the oil separator 16 and is discharged into the discharge chamber 14. The first flow path R1 and the first
The two flow paths R2 are based on the difference in the flow path length, as described later.
High pressure refrigerant gas flow after passing through the first flow path R1 and the second flow path R2
Cancel each pressure pulsation of the high-pressure refrigerant gas flow after passing through
Therefore, both flow paths R1 and R2 have such a high height.
Of the flow path length necessary to cancel the pressure pulsation of the compressed refrigerant gas flow
Have differences. When the high-pressure refrigerant gas is discharged to the discharge chamber 14 side as described above , the volume of the compression chamber 15 is near the minimum, and the refrigerant gas pressure in the compression chamber 15 causes the cylinder discharge port outlet 30b and the side discharge port This is when the discharge valve (not shown) of the outlet 31b is opened.

The gas compressor according to the present embodiment has a discharge port 22 provided only in the cylinder 1 in the prior art.
Are distributed in two places of the cylinder 1 and the side block 3 as the cylinder discharge holes 30 and the side discharge holes 31. In dispersing the discharge holes, from the viewpoint of securing the discharge amount of the high-pressure refrigerant gas as in the related art. The opening area of each of the cylinder discharge holes 30 and the side discharge holes 31 is substantially equal to that of the conventional discharge holes 31. Therefore, in the conventional gas compressor and the gas compressor of the present embodiment, the discharge amount of the high-pressure refrigerant gas is the same, but the diameter of the cylinder discharge hole 30 of the present embodiment is smaller than that of the conventional discharge hole 22. I have.

Next, the operation of the gas compressor configured as described above will be described with reference to FIG.

According to this gas compressor, when the rotor 4 is rotated by the start of operation, the volume of the compression chamber 15 changes in size, and the volume change of the compression chamber 15 causes the low-pressure refrigerant from the suction chamber 13 to the compression chamber 15 to change. Gas suction and compression of the low-pressure refrigerant gas in the compression chamber 15 are performed (see FIGS. 4 and 5). A part of the high-pressure refrigerant gas compressed in the compression chamber 15 is discharged from the compression chamber 15 to the discharge chamber 14 through the flow path R1 and is discharged to the discharge chamber 14 through the flow path R2.

That is, when the volume of the compression chamber 15 becomes close to the minimum, the discharge valves of the cylinder discharge hole outlet 30b and the side discharge hole outlet 31b are opened by the high-pressure refrigerant gas pressure in the compression chamber 15 which has been compressed due to the reduced volume. As a result, the compression chamber 1 is discharged from both the cylinder discharge holes 30 and the side discharge holes 31.
5 allows the high-pressure refrigerant gas to flow out. After flowing into the discharge chamber 24, the high-pressure refrigerant gas flowing out of the cylinder discharge hole 30 reaches the oil separator 16 in the discharge chamber 14 through the discharge passage 25, while flowing out of the high-pressure refrigerant gas from the side discharge hole 31. The gas immediately reaches the oil separator 16 in the discharge chamber 14 via the discharge passage 25.

[0029] In summary, the high-pressure refrigerant gas in the compressor 15 is in the process of discharging the discharge chamber 14 side from the discharge chamber 15, the
Once divided into two flows of a first flow path R1 and a second flow path R2 ,
Thereafter, the two high-pressure refrigerant gas flows are separated by the oil separator 16.
Join in front of. At this time, the first flow path R1 and the second flow path R
2, the flow path length is different as described above.
At the junction point P before 16 , a phase shift occurs as a wave between the high-pressure refrigerant gas flow after passing through the first flow path R1 and the high-pressure refrigerant gas flow after passing through the second flow path R2. Two high-pressure refrigerant gas streams with different phases are synthesized at the junction P
Since the respective pressure pulsation in both flow paths R1, R2 it it flows high-pressure refrigerant gas stream is reliably canceled out at the meeting point P.
Therefore, a high-pressure refrigerant gas flow having a small pressure pulsation is obtained downstream of the junction P, and the high-pressure refrigerant gas flow having a small pressure pulsation is discharged into the discharge chamber 14 through the oil separator 16. The high-pressure refrigerant gas in the discharge chamber 14 is discharged to the outside of the machine through an external discharge port of the casing 11.

During the operation of the gas compressor, the vane 9 always has two cylinder forces, namely, the centrifugal force due to the rotation of the rotor 4 and the vane back pressure supplied to the back pressure chamber 20 at the bottom of the vane 9. 1 It is pressed against the inner wall. Therefore, during the discharge process of the high-pressure refrigerant gas as described above, the vane 9 passes over the inlet 30 a of the cylinder discharge hole 30 while being pressed against the inner wall of the cylinder 1. At this time, in the gas compressor of the present embodiment, the conventional discharge holes 22 are distributed to two places of the cylinder 1 and the side block 3 to form the cylinder discharge holes 30 and the side discharge holes 31, and the total discharge hole opening on the cylinder 1 side When the vane 9 passes over the cylinder discharge port inlet 30b, the contact length between the tip of the vane 9 and the inner wall of the cylinder 1 becomes longer, and as a result, The increase in the applied surface pressure is small, and the sliding wear and contact noise between the tip of the vane 9 and the inner wall of the cylinder 1 are also reduced.

As described above, in the gas compressor of the present embodiment, in the process in which the high-pressure refrigerant gas in the compression chamber 15 is discharged to the discharge chamber 14 side, the high-pressure refrigerant gas flow is divided into two flow paths, The high-pressure refrigerant gas flowing through the two flow paths R1 and R2 is once divided into a flow path R1 and a flow path R2.
It is configured such that it merges with the trouble of the oil separator 16 on the side. Therefore, due to the difference between the lengths of the two flow paths R1 and R2, a phase shift occurs as a wave between the high-pressure refrigerant gas flow after passing through the flow path R1 and the high-pressure refrigerant gas flow after passing through the flow path R2. Since two different high-pressure refrigerant gas streams are synthesized at the junction P, each pressure pulsation of the high-pressure refrigerant gas flowing through the two flow paths R1 and R2 is canceled at the junction P, and on the downstream side of the junction P, A high-pressure refrigerant gas flow with small pressure pulsation is obtained. Therefore, the pressure pulsation of the high-pressure refrigerant gas discharged from the discharge chamber 14 to the outside of the apparatus can be greatly reduced by the effect of the interference type silencer, and the generation of noise and vibration due to this kind of pressure pulsation can be prevented.

According to the gas compressor of the present embodiment,
Discharge hole 22 conventionally provided only in cylinder 1
Are distributed to two places of the cylinder 1 and the side block 3 as the cylinder discharge holes 30 and the side discharge holes 31, so that the total discharge hole opening area on the cylinder 1 side is reduced as compared with the related art. When the vane 9 passes over the cylinder discharge port inlet 30a, the contact length between the tip of the vane 9 and the inner wall of the cylinder 1 increases, so that the surface pressure at the tip of the vane 9 rises little, and The sliding abrasion and the contact noise of the vane 9 are also reduced, and the generation of abrasion and noise due to the increase in the surface pressure at the tip of the vane 9 can be effectively prevented.

Further, in the gas compressor according to the present embodiment, the high-pressure refrigerant gas in the compression chamber 15 is discharged from the compression chamber 15 to the cylinder by the amount of the high-pressure refrigerant gas discharged to the discharge chamber 14 through the side discharge holes 31. Since the flow rate of the high-pressure refrigerant gas flowing into the discharge chamber 24 through the discharge holes 30 is reduced, the sound of collision between the inner wall of the discharge chamber 24 and the high-pressure refrigerant gas is reduced. Have been.

FIG. 2 shows another embodiment of the gas compressor according to the present invention. The difference between the gas compressor shown in FIG. Is that a throttle 40 is provided in the middle of a flow path R1 that passes through the discharge passage 25 and reaches the discharge chamber 14 side.
b is formed thinner than that of the above embodiment.

When the throttle 40 is provided in the middle of the flow path R1 as described above, the high-pressure refrigerant gas temporarily stops in the discharge chamber 24, and the discharge chamber 24 changes the wave characteristics of the high-pressure refrigerant gas flow. It functions as an inflatable silencer. For this reason, the high-pressure refrigerant gas flow after passing through the flow path R1 and the flow path R2
And the high-pressure refrigerant gas flow after passing through the two flow paths R1,
Not only does a phase shift due to the difference in R2 length occur, but also a difference in wave characteristics due to the effect of the expansion type muffler in the discharge chamber 24. Thus, two high-pressure refrigerant gas flows having different wave characteristics are combined at the junction P. In this case, the pressure pulsations of the high-pressure refrigerant gas flow flowing through the flow path R1 and the high-pressure gas flow flowing through the flow path R2 are offset at the confluence point P.
The same effect as the above embodiment can be obtained.

FIG. 3 is a measured value showing the noise characteristics of the gas compressor shown in FIGS. 1 and 2. The broken line in FIG. 3 shows the noise characteristics of the gas compressor shown in FIG. 1, and the solid line in FIG. Flow path R1
9 shows noise characteristics of a gas compressor provided with a throttle 40 therein. When the overall value is calculated by integrating the decibel value up to 20 kHz based on the actual measurement value in FIG. 3 and compared, it is found that the gas compressor provided with the throttle 40 in the flow path R1 has lower noise. can get. Note that the measurement conditions of the actual measurement value are such that the compressor rotation speed is 2600 rpm
m, discharge pressure 2.6MPaG, suction pressure 0.2MP
aG, degree of superheat is 10 deg, and microphone position is 30 cm lateral to the compressor body.

[0037]

As described above, in the gas compressor according to the present invention, during the process in which the high-pressure refrigerant gas in the compression chamber is discharged to the discharge chamber side, the high-pressure refrigerant gas flows into the first flow path and the second flow path. 2 channels
And then the high-pressure refrigerant gas flows after passing through the two flow paths merge at the discharge chamber side, and the two flow paths are connected to the high-pressure refrigerant gas.
Has differences in flow path length required to offset flow pulsations
It is configured as follows. For this reason, the pressure pulsation of the high-pressure refrigerant gas flow flowing through each of the two flow paths is ensured at the AC point from the difference in the flow path lengths of the first and second flow paths as described above.
Offset . Therefore, the pressure pulsation of the high-pressure refrigerant gas discharged from the discharge chamber to the outside of the unit can be significantly reduced, and a low-noise, low-vibration gas compressor that prevents generation of noise and vibration due to this kind of pressure pulsation. Can be provided.

According to the gas compressor of the present invention,
Discharge holes, which were conventionally only provided in cylinders, are now distributed as cylinder discharge holes and side discharge holes at two locations: cylinder and side block. For this reason,
Since the total discharge hole opening area on the cylinder side can be made smaller than before, the contact length between the vane tip and the cylinder inner wall becomes longer when the vane passes over the cylinder discharge hole inlet. The rise in surface pressure applied to the tip is small, and the sliding wear and contact noise between the tip of the vane and the inner wall of the cylinder are also reduced.This makes it possible to effectively prevent the generation of wear and noise due to the increase in surface pressure at the tip of this kind of vane. Also in terms of
A gas compressor having low noise and excellent wear resistance can be provided.

Further, in the gas compressor according to the present invention, the high pressure refrigerant gas in the compression chamber is discharged from the compression chamber to the cylinder discharge port by the amount of the high pressure refrigerant gas discharged to the discharge chamber through the side discharge hole. Since the flow rate of the high-pressure refrigerant gas flowing into the discharge chamber through the discharge chamber is reduced, the collision noise between the inner wall of the discharge chamber chamber and the high-pressure refrigerant gas is reduced, and in this respect, a low-noise gas compressor can be provided.

[Brief description of the drawings]

FIG. 1 is an explanatory view of a main part of an embodiment of a gas compressor according to the present invention.

FIG. 2 is an explanatory view of a main part of another embodiment of the gas compressor according to the present invention.

FIG. 3 is a noise characteristic diagram of the gas compressor shown in FIGS. 1 and 2;

FIG. 4 is a sectional view of a conventional gas compressor.

FIG. 5 is a sectional view of the cylinder taken along line AA in FIG. 3;

FIG. 6 is an explanatory view of a discharge passage of a high-pressure refrigerant gas in the conventional gas compressor shown in FIG.

[Explanation of symbols]

 Reference Signs List 1 cylinder 2 front side block 3 rear side block 4 rotor 5 rotor shaft 6, 7 bearing 8 vane groove 9 vane 10 compressor body 11 casing 12 front head 13 suction chamber 14 discharge chamber 15 compression chamber 16 oil separator Reference Signs List 17 oil reservoir 18 oil hole 19 salary groove 20 back pressure chamber 21 suction passage 22 discharge hole 23 discharge valve 23a valve support 24 discharge chamber 24a notch 25 discharge passage 25a pore 25b thick hole 30 cylinder discharge hole 30a cylinder discharge hole Inlet 30b Cylinder discharge hole outlet 31 Side discharge hole 31a Side discharge hole inlet 31b Side discharge hole outlet 40 Restrictor R1 flow path R2 flow path P High pressure refrigerant gas junction

────────────────────────────────────────────────── ─── Continuation of front page (56) References JP-A-64-8390 (JP, A) JP-A-9-250483 (JP, A) JP-A-5-149254 (JP, A) JP-A-4- 358792 (JP, A) JP-A-61-53473 (JP, A) JP-A-4-252889 (JP, A) JP-A-7-12708 (JP, A) Japanese Utility Model Publication No. 56-49277 (JP, U) Japanese Utility Model Showa 57-16881 (JP, U) Japanese Utility Model Showa 54-74303 (JP, U) Japanese Utility Model Showa 63-136290 (JP, U) Japanese Utility Model Hei 1-334716 (JP, Y2) Japanese Utility Model Hei 7-12708 (JP, Y2) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04C 18/30-18/352 F04C 29/06

Claims (2)

(57) [Claims] A cylinder having a substantially elliptical inner periphery;
Side block attached to the end face of the
Inside the rotor and rotating through the rotor shaft and its bearings.
A rotatably provided rotor and an outer peripheral surface of the rotor.
And a slidably mounted vane groove.
Vane, cylinder, side block, rotor and
And vanes, and
The rotation of the compressor repeatedly changes the size of the volume.
Low-pressure refrigerant gas sucked from the suction chamber
A gas pressure comprising a compression chamber for compressing and producing a high-pressure refrigerant gas
In the compressor, a discharge chamber provided on the outer peripheral surface side of the cylinder,
Open end and open the other end to the discharge chamber side
One end is opened to the cylinder discharge hole and the discharge chamber side, and the other end is set to the discharge chamber side.
A discharge passage having an opening;
Open to the compression chamber side and open the other end to the discharge passage side.
Side discharge holeWhen, From the compression chamber to the cylinder discharge hole and discharge chamber
A first passage of high-pressure refrigerant gas passing through the discharge passage, The compression chamber directly passes through the side discharge holes and discharges
A second flow path for the high-pressure refrigerant gas reaching the outlet passage, The first flow path and the second flow path Is the height after passing through the first flow path.
Pressure of the high pressure refrigerant gas flow after passing through the second flow path and the high pressure refrigerant gas flow
Have different flow path lengths needed to offset force pulsations
A gas compressor characterized by: 2. The gas compressor according to claim 1, wherein a throttle is provided in the middle of the first flow path.