JP2002371965A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor reducing power required for operating a compressor by preventing over-compression of high pressure coolant gas, and preventing noise of the compressor and breakage of a valve plate generated by over-compression. SOLUTION: A discharge valve 37 is disposed at a discharging chamber side opening end 16b of a discharge hole 16 opening to a compression chamber 9 side at one end and opening to a discharge chamber 7 side at the other end. The discharge valve 37 comprises a valve plate 32 elastically deforming so as to block the discharge chamber side opening end 16b of the discharge hole 16 by pressure in the compression chamber 9 and open the discharge chamber side opening end 16b of the discharge hole 16 when the pressure in the compression chamber 9 exceeds pressure in the discharge chamber 7, a pressure supply passage 41 communicating from a spot facing surface 36 of the valve plate 32 into the compression chamber 9, and an over-compression releasing means 35 releasing the pressure in the compression chamber 9 to the discharge chamber 7 side by sliding the valve plate 32 to the discharge chamber 7 side with pressure supplied from the pressure supply passage 41 when high pressure coolant gas in the compression chamber 9 is over-compressed. The pressure over-compressed in the compression chamber 9 is released from the discharge chamber side opening end 16b of the discharge hole 16 and a clearance 51 on a lower surface of a valve seat 31 to the discharge chamber 7 side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas compressor, and more particularly, to a vane rotary type gas compressor used for a car air conditioner system or the like.

[0002]

2. Description of the Related Art Conventionally, a vane rotary type gas compressor shown in FIG. 5 is known.

As shown in FIG. 1, the gas compressor includes a compressor groove C, a compressor case 1 surrounding the compressor groove C, and a front head 2. The compressor case 1 is closed by a front head 2 and accommodates a compressor groove C connected to the electromagnetic clutch 3. A low pressure is applied between the front side block 4 attached to one end surface of the compressor groove C and the front head 2. Is formed, and a high-pressure discharge chamber 7 is formed between the rear side block 5 attached to the other end surface of the compression mechanism C and the compressor case 1.

The compressor groove C has a substantially cylindrical cylinder 8 having an inner periphery between the front side block 4 and the rear side block 5. The inner periphery is partitioned by the cylinder 8, the front side block 4 and the rear side block 5. In the compression chamber 9 having a substantially elliptical cylindrical shape, a rotor 11 is horizontally mounted.
The rotor 11 is integrally provided with a rotor shaft 12 penetrating between the end faces thereof. The rotor shaft 12 is rotatable by a bearing 10 on the front side block 4 side and a bearing (not shown) on the rear side block 5 side. Supported.

As shown in FIG. 6, a plurality of slit-shaped vane grooves 13 are formed on the outer peripheral surface of the rotor 11, and a vane 14 is slidably mounted in each of the vane grooves 13. Are provided so as to be able to protrude and retract from the outer peripheral surface of the rotor 11 toward the inner peripheral surface of the cylinder 8.

A plurality of discharge holes 16 are formed at predetermined positions on the outer periphery of the cylinder 8, and a discharge valve 17 for opening and closing the discharge holes 16 is provided on the discharge hole 16 on the side of the discharge chamber 18. The discharge valve 17 is, as shown in FIG.
6, a valve plate 21 provided so as to cover the opening end of the valve plate 6, and the valve plate 2
A valve support 22 for regulating the amount of one warp is sequentially arranged.

As shown in FIG. 1, a plurality of mounting holes 8a are formed at predetermined positions on the outer periphery of the cylinder 8 to mount the discharge valve 17, and through holes 21a are formed in the valve plate 21 and the valve support 22. , 22a are drilled, and the bolts 20 are inserted through the through holes 21a, 22a sequentially and screwed into the mounting holes 8a of the cylinder 8,
The valve plate 21 and the valve support 22 are attached and fixed to the discharge chamber 16 of the discharge hole 16 on the outer periphery of the cylinder 8.

In the gas compressor having the above-described structure, the compression chamber 9 repeatedly changes its volume by rotating the rotor 11 in the direction of arrow A in FIG. The compressed high-pressure refrigerant gas is discharged to the discharge chamber 7 side.

When the volume of the compression chamber 9 increases, the low-pressure refrigerant gas in the suction chamber 6 is sucked into the compression chamber 9 through the suction passage 15 of the cylinder 8, and as the volume of the compression chamber 9 decreases, the pressure in the compression chamber 9 decreases. When the low-pressure refrigerant gas is compressed and the volume of the compression chamber 9 is minimized, the pressure in the compression chamber 9 increases due to the pressure of the compressed high-pressure refrigerant gas, and the pressure in the compression chamber 9 increases in the discharge chamber chamber 18. When the pressure is exceeded, the distal end portion 21b of the valve plate 21 that opens and closes the discharge hole 16 of the cylinder 8 is lifted to open the discharge hole 16, and the high-pressure refrigerant gas in the compression chamber 9 is discharged from the discharge hole 16 and the outside of the cylinder 8 Chamber room 1
8, the fluid is discharged to the discharge chamber 7 via the discharge passage 19 and the wire mesh 24 of the oil separator 23.

At the end of the compression step, the pressure in the compression chamber 9 decreases, and the pressure difference between the compression chamber 9 and the discharge chamber chamber 18 causes the distal end 21b of the valve plate 21 to elastically deform toward the compression chamber 9. The airtightness is maintained by closing the discharge holes 16 to prevent backflow of the high-pressure refrigerant gas to the compression chamber 9 side, thereby preventing re-compression of the high-pressure refrigerant gas.

However, the valve plate 21 does not elastically deform even if the pressure in the compression chamber 9 reaches a predetermined pressure because the valve plate 21 sticks to the valve seat of the discharge hole 16 with an oil film or the like.
Remains closed, so that the compression operation is performed until the pressure of the high-pressure refrigerant gas in the compression chamber 9 becomes higher than usual, that is, when over-compression occurs, the power required for the operation of the compressor Increase.

In addition, due to the overcompression, a vibration wave is generated in the discharge jet of the high-pressure refrigerant gas which is compressed at a pressure higher than usual in the compression chamber 9 and is discharged from the discharge hole 16, and a fluid noise is generated. The discharge jet of the high-pressure refrigerant gas collides with each part of the compressor to generate a collision noise, and the fluid noise and the collision noise cause noise during the operation of the compressor.

The over-compressed high-pressure refrigerant gas acts on the discharge valve 17 separating the compression chamber 9 and the discharge chamber chamber 18 so that the high-pressure refrigerant gas discharged from the discharge hole 16 discharges the high-pressure refrigerant gas. The tip 21b of the valve plate 21 may be destroyed by an impact at the time of colliding with the valve plate 21 constituting 17.

[0014]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to prevent over-compression of high-pressure refrigerant gas and to improve the operation of a compressor. An object of the present invention is to provide a gas compressor capable of reducing required power and preventing compressor noise generated due to overcompression, breakage of a valve plate, and the like.

[0015]

To achieve the above object, a gas compressor according to the present invention is characterized in that a low-pressure refrigerant gas in a suction chamber is sucked and compressed, and the compressed high-pressure refrigerant gas passes through a discharge valve. A gas compressor having a compression chamber that discharges to the discharge chamber side, wherein one end is opened to the compression chamber side, and the other end is opened to the discharge chamber side. The discharge chamber is closed by the compression chamber pressure, and when the compression chamber pressure exceeds the discharge chamber pressure, the valve plate is elastically deformed so as to open the discharge hole. A pressure supply path communicating with the pressure chamber, and when the high-pressure refrigerant gas in the compression chamber is over-compressed, the pressure supplied by the pressure supply path causes the valve plate to slide toward the discharge chamber to reduce the pressure in the compression chamber to the discharge chamber. Overcompression release means to escape to the side It is characterized in that.

The over-compression release means is constituted by a bolt supporting the valve plate and an elastic body interposed between the bolt and the valve plate.

As described above, when the high-pressure refrigerant gas in the compression chamber is over-compressed, there is provided an over-compression opening means for releasing the pressure in the compression chamber to the discharge chamber side. Since the discharge hole is opened to the discharge chamber side from the discharge chamber side opening end of the discharge hole, or through a pressure supply passage communicating from the compression chamber to the counterbore surface of the valve seat,
It is possible to prevent overcompression in which the pressure of the high-pressure refrigerant gas in the compression chamber is excessively compressed.

[0018]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

The basic structure of the gas compressor according to the present invention,
That is, as shown in FIGS. 5 and 6, the compressor groove C connected to the electromagnetic clutch 3 is provided in the compressor case 1.
And a low-pressure suction chamber 6 is formed between the front head 2 and the front side block 4 attached to one end face of the compressor groove C, and the rear side block 5 attached to the other end face of the compression mechanism C. A high-pressure discharge chamber 7 is formed between the compressor case 1 and the compressor groove C.
Means front side block 4 and rear side block 5
, A cylinder 8, a front side block 4, a rear side block 5
A rotor 11 is laterally suspended in the compression chamber 9 having an inner peripheral substantially elliptical cylindrical shape partitioned by a slit, and a plurality of slit-shaped vane grooves 13 are formed on the outer peripheral surface of the rotor 11.
Are provided with vanes 14 so as to be slidable and provided so as to be able to protrude and retract from the outer peripheral surface of the rotor 11 toward the inner peripheral surface of the cylinder 8, respectively. The point that the low pressure refrigerant gas sucked from the suction chamber 6 side is compressed and the compressed high pressure refrigerant gas is discharged to the discharge chamber 7 side is the same as the conventional example because the volume is repeatedly changed. The same members as those described above are denoted by the same reference numerals, and detailed description thereof will be omitted.

In the gas compressor according to the present embodiment, the high-pressure refrigerant gas compressed in the compression chamber 9 has a discharge valve 37 provided in a discharge chamber 18 formed by cutting out the outer peripheral surface of the cylinder 8. The discharge valve 37 is discharged through the discharge chamber 7 through the discharge chamber 37, and is characterized by the structure of the discharge valve 37.

That is, as shown in FIG. 1, the discharge valve 37 has one end opened to the compression chamber 9 side and the other end opened to the discharge chamber 7 side at the discharge chamber 7 side open end. The discharge valve 37 is disposed in the discharge chamber 7 of the discharge hole 16.
A valve seat 31 and a valve plate 32 are sequentially arranged at the edge of the side opening end 16b. The valve plate 32 comes into contact with the valve seat 31 and is elastically deformed toward the compression chamber 9 by the pressure in the compression chamber 9 to discharge. The opening 16b of the hole 16 on the side of the discharge chamber 7 is closed, and the pressure in the compression chamber 9 is reduced.
When the internal pressure is exceeded, the pressure in the compression chamber 9 raises the distal end portion 32b of the valve plate 32 to open the discharge chamber 7 side opening end 16b of the discharge hole 16.

Further, the valve seat 31 constituting the discharge valve 37 is provided.
A pressure supply passage 41 communicating with the inside of the compression chamber 9 is formed in the counterbore surface 36 of the compression chamber 9. When the high-pressure refrigerant gas in the compression chamber 9 is overcompressed, the pressure in the compression chamber 9 is reduced.
And is supplied to the counterbore surface 36 of the valve seat 31 via the.

When the high-pressure refrigerant gas in the compression chamber 9 is over-compressed, the discharge valve 37 increases the pressure in the compression chamber 9.
It is configured to have over-compression release means for releasing to the side.

That is, as shown in the figure, the over-compression release means includes a valve seat 31, a valve plate 32,
Connect the valve support 33 to the opening end 1 of the discharge hole 16 on the discharge chamber 7 side.
A spring is attached below the bolt 34 for supporting and fixing the edge of the elastic member 6b as an example of the elastic body 35.

On the other hand, a mounting hole 8a for mounting the discharge valve 37 is formed at a predetermined position on the outer peripheral surface of the cylinder 8,
The valve seat 31, the valve plate 32, and the valve support 33 are provided with through holes 31a, 32a, 33a, respectively.
The valve seat 31, the valve plate 32, and the valve support 33 are discharged in a state where they are urged by the elastic body 35 by being sequentially inserted through the a, 32a, and 31a and screwed into the mounting hole 8a on the outer peripheral surface of the cylinder 8. Opening end 16b of hole 16 on discharge chamber 7 side
It is attached and fixed to the edge of.

In the figure, a member denoted by reference numeral 33 is a valve support, which is disposed on the valve plate 32 and
It is formed so as to regulate the amount of warpage.

Next, the operation of the gas compressor having the above configuration will be described with reference to FIGS.

The rotation of the rotor 11 causes the compression chamber 9 to rotate.
Repeatedly compresses the low-pressure refrigerant gas sucked from the suction chamber 6 side and discharges the compressed high-pressure refrigerant gas to the discharge chamber 7 side. The low-pressure refrigerant gas in the compression chamber 9 is sucked into the compression chamber 9 through the suction passage of the cylinder 8, and as the volume of the compression chamber 9 decreases, the low-pressure refrigerant gas in the compression chamber 9 is compressed. When the pressure is minimized, the pressure in the compression chamber 9 rises due to the pressure of the compressed high-pressure refrigerant gas, and the pressure in the compression chamber 9 exceeds the pressure in the discharge chamber 7. Discharge valve 3 arranged at open end 16b
The high-pressure refrigerant gas in the compression chamber 9 is discharged from the discharge chamber 16, the discharge chamber chamber 18 outside the cylinder 8, and the discharge chamber 7 on the discharge chamber 7 side. The fluid is discharged to the discharge chamber 7 via the passage 19 and the wire mesh 24 of the oil separator 23.

At the end of the compression step, when the pressure in the compression chamber 9 falls and falls below the pressure in the discharge chamber 18,
Due to the pressure difference between the compression chamber 9 and the discharge chamber chamber 18, the valve plate 32 abuts on the valve seat 31, and the distal end portion 32 b of the valve plate 32 is elastically deformed toward the compression chamber 9 and the discharge hole 16 is formed on the discharge chamber 7 side. Close the open end 16b.

The valve plate 32 of the discharge valve 37 is normally urged by the elastic body 35 and pressed against the edge of the opening 16b of the discharge hole 16 on the discharge chamber 7 side. Even if the pressure in the compression chamber 9 reaches a predetermined pressure due to, for example, the oil film 32 sticking to the valve seat 31 of the discharge hole 16, the valve plate 32 does not elastically deform, and the discharge valve 37 remains closed. When an over-compression state is created in which the compression operation is performed until the pressure of the high-pressure refrigerant gas in the compression chamber 9 becomes higher than usual, the pressure excessively compressed in the compression chamber 9 becomes Discharge port 1 communicating from the discharge chamber chamber 18 to the discharge chamber 1
6 acts on the lower surface of the distal end portion 32b of the valve plate 32 of the discharge valve 37 that closes the opening end 16b of the discharge hole 16 on the discharge chamber 7 side.

Further, since the pressure supply passage 41 communicating from the inside of the compression chamber 9 to the counterbore surface 36 of the valve seat 31 constituting the discharge valve 37 is formed, the pressure in the overcompressed compression chamber 9 is reduced. The pressure is supplied to the counterbore surface 36 of the valve seat 31 via the pressure supply path 41 and acts on the lower surface of the valve seat 31.

As described above, the valve plate 32 is attached and fixed by the bolt 34 to which the elastic body 35 having an elastic force is attached, so that the pressure applied to the lower surface of the valve seat 31 makes the valve seat 31 elastic. Discharge chamber 7 against body 35
The valve plate 3 pushed upward and abutted on the upper part of the valve seat 31
2. The valve support 33 is simultaneously pushed up to the discharge chamber 7 side.

As described above, when the valve plate 32 closing the opening end 16b of the discharge hole 16 on the side of the discharge chamber 7 rises and moves away from the opening end 16b of the discharge hole 16 on the side of the discharge chamber 7, the discharge chamber of the discharge hole 16 is formed. The side opening end 16b is opened, and a gap 51 communicating between the lower surface of the valve seat 31 and the counterbore surface 36 is formed on the discharge chamber 7 side. 16
Of the compression chamber 9 is released from the discharge chamber chamber 18 to the discharge chamber 7 side.

When the pressure over-compressed in the compression chamber 9 in the manner described above is released from the interior of the compression chamber 9 to the discharge chamber 7 side, FIG.
As shown in the figure, the valve seat 31 and the valve plate 3 constituting the discharge valve 37 are provided.
2. The valve support 33 returns to a state in which it is pressed against the edge of the opening 16b of the discharge hole 16 on the discharge chamber 7 side by the return force of the elastic body 35, and the valve plate 32 opens the opening of the discharge hole 16 on the discharge chamber 7 side. Close end 16b.

[0035]

As described above in detail, according to the gas compressor of the present invention, the discharge valve releases the pressure in the compression chamber to the discharge chamber side when the high-pressure refrigerant gas in the compression chamber is over-compressed. The pressure which is configured so as to include the compression opening means, and which is overcompressed in the compression chamber, passes through the discharge chamber side opening end of the discharge hole or the pressure supply path communicating from the compression chamber to the counterbore surface of the valve seat. As a result, the pressure of the high-pressure refrigerant gas in the compression chamber can be prevented from being excessively compressed, and the power required for operating the compressor can be reduced. And at the same time, it is possible to prevent the noise of the compressor caused by the over-compression, the breakage of the valve plate, and the like.

[Brief description of the drawings]

FIG. 1 is an enlarged sectional view showing a configuration of a discharge valve in a gas compressor according to the present invention.

FIG. 2 is an enlarged sectional view showing a state of a discharge valve at the time of overcompression.

FIG. 3 is an enlarged cross-sectional view illustrating a state of a discharge valve when overcompression is released.

FIG. 4 is an enlarged sectional view showing a state of a discharge valve at the end of overcompression release.

FIG. 5 is a sectional view showing a configuration of a conventional gas compressor.

FIG. 6 is a sectional view taken along line VI-VI of FIG. 5;

FIG. 7 is an enlarged perspective view of the discharge valve shown in FIG.

[Explanation of symbols]

 Reference Signs List 6 suction chamber 7 discharge chamber 8 cylinder 9 compression chamber 16 discharge hole 16a discharge chamber side open end of discharge hole 16b discharge chamber side open end of discharge hole 31 valve seat 32 valve plate 33 valve support 34 bolt 35 elastic body (spring) 36 Counterbore surface 37 Discharge valve 41 Pressure supply path 51 Clearance

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tohru Takahashi 1-8-1, Nakase, Mihama-ku, Chiba-shi, Chiba Prefecture Inside Seiko Instruments Inc. (72) Inventor Toshinari Matsuura 1-8-1, Nakase, Mihama-ku, Chiba-shi, Chiba F term (reference) in Seiko Instruments Inc. 3H003 AA05 AB07 AC03 BA00 CC01 CC11 3H029 AA05 AA17 AB01 BB21 BB41 BB44 CC09 CC15 3H040 AA07 BB11 CC10 CC14 DD01 DD28

Claims (2)

[Claims] 1. A gas compressor having a compression chamber for sucking and compressing low-pressure refrigerant gas on a suction chamber side and discharging the compressed high-pressure refrigerant gas to a discharge chamber side via a discharge valve. One end is opened at the discharge chamber side, and the other end is opened at the discharge chamber side. The discharge hole is closed at the discharge chamber side opening end, and the compression chamber pressure closes the discharge hole. When the pressure exceeds, a valve plate that elastically deforms to open the discharge hole, a pressure supply path communicating from the counterbore surface of the valve plate to the compression chamber, An over-compression release means for sliding the valve plate to the discharge chamber side by the pressure supplied by the pressure supply path to release the pressure in the compression chamber to the discharge chamber side. 2. The over-compression release means is constituted by a bolt supporting the valve plate and an elastic body interposed between the bolt and the valve plate.
3. The gas compressor according to claim 1.