JPH0979156A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce generation of a noise caused by this delivery pulsation by restraining delivery side pulsation without enlarging the whole device and without largely increasing production cost. SOLUTION: Delivery passages 40 and 41 whose passage lengths are equal to each other are connected to respective windows 37 and 38 leading to a delivery hole of a cylinder chamber, and the respective tail end sides of these delivery passages 40 and 41 are connected to a common passage 49. When the cylinder chamber is operated, delivery pulsations are respectively generated in a part of delivery valve upstream of the two windows 37 and 38, and in these pulsations, phases are different by a half wave. However, as mentioned above, the delivery passages 40 and 41 to be respectively connected to the windows 37 and 38 are equal in a passage length, and in the delivery passages 40 and 41, the respective tail end sides are connected to the common passage 49. Therefore, since its pulsations negate each other when passing through the common passage 49, its delivery pulsations are hardly transmitted outside.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art FIG. 8 shows a cross section of a schematic structure of a conventional vane rotary type gas compressor. FIG.
Is viewed from the direction of arrow XX in FIG. This gas compressor is slidably held by five slits (not shown) radially provided on the rotor 2 when the rotor 2 integrally fixed to the rotor shaft 1 is rotationally driven by a prime mover (not shown). The formed five vanes 3 rotate while contacting the inner peripheral wall of the cylinder chamber 4 to compress the refrigerant gas.

An intake port 7 for sucking a refrigerant gas to be compressed from an evaporator (not shown) is formed in an upper portion of a suction chamber 6 provided in the front head 5. In the front head 5, two suction holes 8 and 9 are formed at point-symmetrical positions so that the suction chamber 6 and the cylinder chamber 4 communicate with each other. Therefore, the refrigerant gas sucked from the suction port 7 of the suction chamber 6 is introduced into the cylinder chamber 4 via the suction chamber 6 and the suction holes 8 and 9 as shown by an arrow A. ing.

Cylinder chamber 4 in the rear side block 10
Two discharge holes (not shown) corresponding to the above-mentioned suction holes 8 and 9 of the cylinder chamber 4 are formed at two points of point symmetry on the side, and a discharge valve (not shown) is formed in each discharge hole. ) Is provided. As shown in FIG. 9, the discharge holes communicate with windows 11 and 12 formed in the rear side block 10, and are further connected to discharge passages 13 and 14 formed between the rear side block 10 and the oil separator block 15. The discharge passage 13 and the discharge passage 14 are commonly connected on the terminal side,
An oil separator 17 for separating the lubricating oil in the refrigerant gas is arranged at the common connection portion 16.

In such a conventional vane rotary type gas compressor, when the rotor 2 is rotationally driven by the prime mover (not shown) to operate the vane 3, as shown by an arrow A,
The refrigerant gas sucked into the suction chamber 6 from the suction port 7 is first sucked into the cylinder chamber 4 via the suction hole 8 and compressed, and then discharged from the window 12 corresponding to the suction hole 8. In parallel with this operation, when the suction of the intake hole 8 of the cylinder chamber 4 is completed, the suction of the refrigerant gas from the suction hole 9 to the cylinder chamber 4 is started and the compression is started. The refrigerant gas is discharged from the window 11 corresponding to.
Therefore, the refrigerant gas discharged from the windows 11 and 12 has different discharge timings and is intermittent.

In this way, the compressed refrigerant gas discharged from the window 11 or the window 12 is supplied to the oil separator 17 via the discharge passage 13 or the discharge passage 14. In the oil separator 17, the lubricating oil in the refrigerant gas is separated, and only the refrigerant gas is discharged from the discharge port 19 of the discharge chamber 18 to the outside as shown by an arrow B.

[0007]

By the way, the discharge gas from the two windows 11 and 12 of the cylinder chamber 4 is not constant in pressure because it is intermittent as described above. Higher-order pressure fluctuations have occurred. Therefore, in the discharge valve portion of the two windows 11 and 12, the number of vanes 3 is five, so that one rotation of the rotor 2 results in five vanes.
Each discharge pulsation occurs.

The two discharge pulsations generated in the windows 11 and 12 of the cylinder chamber 4 are out of phase with each other by a half wavelength, but this is because the discharge gas is smoothly discharged.
This is because the discharge timing of the discharge gas from 12 is designed as such. Therefore, the two pulsating refrigerant gases are discharged into the discharge passage 13, the discharge passage 14, and the oil separator 1.
7, and the discharge pulsation due to the fifth-order component of the compressor rotation number should not be transmitted to the outside because they cancel each other out through the discharge chamber 19 and the discharge chamber 18.

However, as shown in FIG.
Since the distance (length) between the discharge passage 14 and the discharge passage 14 is different, the above-described discharge pulsation cannot be effectively canceled. For this reason, there is a problem that the discharge pulsation is transmitted to the outside to generate noise, and in order to solve this problem, it is generally considered to use a silencer, but in this case, the silencer of the entire device is used. The size increases and the production cost increases significantly, which causes new problems.

Therefore, it is an object of the present invention to suppress the pulsation on the discharge side without increasing the overall size of the apparatus and to greatly increase the production cost, and to reduce the noise generated due to this discharge pulsation. .

[0011]

According to the present invention, gas is sucked from two suction ports provided at point-symmetrical positions by rotary motion of a plurality of vanes at different timings, and the sucked gas is rotated by the vane. A gas compression unit that compresses each gas by a volume change accompanying movement and discharges each compressed gas from two discharge ports corresponding to the two suction ports at different timings, and two discharge ports of the gas compression unit. The above object is achieved by providing the gas compressor with two discharge passages connected to each other and having the same passage length, and a common passage commonly connected to each terminal end side of the two discharge passages.

[0012]

According to the present invention, during the operation of the gas compressing section, discharge pulsations corresponding to the number of vanes occur at the two discharge ports of the gas compressing section, and the phases of these two discharge pulsations are shifted by a half wavelength. However, the two discharge passages respectively connected to the two discharge ports have the same passage length, and the terminal ends of the two discharge passages are connected to the common passage. Therefore, the discharge pulsations generated at the two discharge ports of the gas compression unit cancel each other out when passing through the common passage, so that the discharge pulsations are less likely to be transmitted to the outside.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to FIGS. FIG. 1 shows a cross section in which a part of the gas compressor of the embodiment of the present invention is omitted. FIG.
Is viewed from the direction of the arrow Y-Y in FIG.

As shown in FIG. 1, the gas compressor according to the embodiment of the present invention includes a gas compression section 21, a casing 22 surrounding the gas compression section 21, and a front head 23. One end side of the casing 22 is open, and a front head 23 is attached so as to seal the opening.

The gas compression section 21 has a cylindrical cylinder block 24 having an inner peripheral surface with an elliptical cross section in the axial direction, and a control plate rotatably mounted on the left end surface of the cylinder block 24 as described later. 25 and cylinder block 2
4 and the rear side block 26 fixed to the right end surface of the cylinder 4,
7 are formed.

Inside the cylinder chamber 27, there are five vanes 2 slidably held in slits (not shown).
A rotor 30 having 9 is housed. This rotor 3
0 is integrally attached to the rotor shaft 31, and the rotor shaft 3
The left and right sides of 1 are rotatably supported by shaft bearing holes 23a and 26a formed in the front head 23 and the rear side block 26, which have a diameter slightly larger than the rotor shaft 31. The end of the rotor shaft 31 is connected to a prime mover (not shown). When the rotor 31 is driven to rotate, the five vanes 29 rotate while contacting the inner peripheral wall of the cylinder chamber 27 to compress the refrigerant gas. Is configured to.

A suction chamber 32 is formed in the front head 23, and an intake port (not shown) for sucking a refrigerant gas to be compressed from an evaporator (not shown) is formed in the suction chamber 32.
Is provided. The boss portion 23b formed on the cylinder block 24 side of the front head 23 is substantially disc-shaped and has the fitting hole in the center thereof.
Is rotatably fitted within a predetermined angle via a bearing 28. Recessed openings (not shown) are formed at predetermined positions on the periphery of the control plate 25, which are opposed to each other. As shown in FIG. 1, the front head 23 is provided with a suction chamber 32, which engages with the recess opening of the control plate 25 and adjusts the recess opening position according to the rotation of the control plate 25. It is configured so that the compression volume of the cylinder chamber 27 can be adjusted.

The rear side block 26 is fixed to the cylinder block 24 by bolts 48, as shown in FIG. Cylinder chamber 27 in the rear side block 26
Two discharge holes (not shown) are formed at the two point symmetrical positions on the side corresponding to the opening of the recess of the control plate 25.
A discharge valve (not shown) is provided in each of the discharge holes. As shown in FIG. 2, each of the discharge holes communicates with windows 37 and 38 formed in the rear side block, and a discharge passage 40 formed between the rear side block 26 and the oil separator block 39 as described below. , 41,
The discharge passage 40 and the discharge passage 41 are commonly connected on the terminal side, and an oil separator (filter) 42 for separating lubricating oil in the refrigerant gas is arranged in the common passage 49. The discharge passage 40 and the discharge passage 41 are formed to have the same passage length.

Rear side block 26 and casing 22
A space surrounded by and forms a discharge chamber 44 having a discharge port (not shown) communicating with the outside. An oil sump 46 for storing lubricating oil is formed at the bottom of the discharge chamber 44, and the lubricating oil in the oil sump 46 is supported by the shaft bearing holes 23a, 26a.
Lubricating oil supply passages 47 for supplying the oil and the like are formed inside the rear side block 26, the cylinder block 24, and the front head 23, respectively.

Next, details of the configuration of the rear side block 26 will be described. FIG. 3 shows a cross section of the rear side block, and FIG. 4 shows a right side surface of the rear side block. The rear side block 26 has a substantially disc shape having a predetermined thickness,
A shaft bearing hole 2 for bearing the above-mentioned rotor shaft 31 in the center thereof
6a is provided. Also, the rear side block 26
4, windows 37 and 38 are bored in the thickness direction at predetermined positions which are point-symmetrical with respect to each other. The windows 37 and 38 are connected to the respective start ends of the discharge passage grooves 261 and 262. ing.
The respective end sides of the both window grooves 261 and 262 are connected to the oil separator 4
One end of the two is extended toward the recess 263 which is housed, and is commonly connected by the recess 263. Groove 26 for discharge passage
1 and the discharge passage groove 262 are formed such that the groove lengths are equal.

The discharge passage groove 261 is opposed to a discharge passage groove 391 provided in an oil separator block 39, which will be described later, to form a discharge passage 40 shown in FIG.
Further, the discharge passage groove 262 faces the discharge passage groove 392 provided in the oil separator block 39, which will be described later, thereby forming the discharge passage 41 shown in FIG.

At a predetermined position of the rear side block 26,
A plurality of mounting holes 264 for mounting the rear side block 26 on the left end surface of the cylinder block 24 with bolts 48, and a screw hole 265 for mounting the oil separator block 39 on the rear side block 26 are provided.

Next, the details of the structure of the oil separator block 39 will be described. FIG. 5 shows an oil separator block 39.
6 shows the left side surface of the oil separator block 39, and FIG. 7 shows the right side surface of the oil separator block 39.

The oil separator block 39 includes a discharge passage groove 391 that forms a discharge passage 40 facing the discharge passage groove 261 provided in the rear side block 26, and a discharge passage groove 391 that is also provided in the rear side block 26. Groove 262
Discharge passage groove 392 that forms the discharge passage 41 facing the discharge passage 41.
Are provided. Then, both discharge passage grooves 39
The respective terminal ends of 1 and 392 extend toward a cylindrical portion 394 serving as a common passage in which the oil separator 42 is accommodated, and are commonly connected to this cylindrical portion 394. Discharge passage groove 391
The discharge passage groove 392 and the discharge passage groove 392 are formed to have the same groove length. The upper side and the lower side of the cylindrical portion 394 are open. A recess 395 for accommodating the central portion of the rear side block 26 is formed on the lower side of the oil separator block 39, and the oil separator block 3 is formed.
An attachment hole 396 for attaching the block 39 to the rear side block is formed at a predetermined position of 9.

Next, the operation of the embodiment of the present invention constructed as above will be described. Now, when the rotor 30 is rotationally driven by an unillustrated prime mover and the vanes 29 are operated, the refrigerant gas sucked into the intake chamber 32 from the unillustrated intake port first passes through the recessed opening of the control plate 25 to the cylinder chamber. After being sucked into 27 and compressed, it is discharged from the window 38 (see FIG. 2). In parallel with this operation, when the suction from the recess opening of the control plate 25 of the cylinder chamber 27 ends, the suction of the refrigerant gas from the other recess opening of the control plate 25 to the cylinder chamber 27 is started and the compression is started. When this compression is completed, the refrigerant gas is discharged from the window 37. Therefore, the refrigerant gas discharged through the windows 37 and 38 has different discharge timings and is intermittent.

In this way, the compressed refrigerant gas discharged from the window 37 or the window 38 is supplied to the oil separator 42 via the discharge passage 40 or the discharge passage 41. In the oil separator 42, the lubricating oil in the refrigerant gas is separated and the refrigerant gas is discharged to the outside from the discharge port (not shown) of the discharge chamber 44.

During operation of such a gas compressor, the discharge chamber 4 is provided between the discharge chamber 44 and the shaft bearing holes 23a and 26a.
There is a high pressure difference on the 4th side. Therefore, the discharge chamber 4
The lubricating oil in the oil sump 46 of No. 4 flows to the shaft bearing holes 23a and 26a via the lubricating oil supply passage 47, and is used for lubricating the sliding portion.

By the way, the discharge gas from the windows 37 and 38 leading to the two discharge holes of the cylinder chamber 27 is not constant in pressure because it is intermittent as described above, and the rotor 3
Higher-order pressure fluctuations corresponding to a rotation speed of 0 occur. For this reason, in the discharge valve portions of the two windows 37 and 38, since the vanes 3 are composed of five sheets, the discharge pulsation is generated five times for each rotation of the rotor 30.

Further, the phases of the two discharge pulsations generated in the windows 37 and 38 leading to the discharge holes of the cylinder chamber 27 are shifted by half a wavelength. However, the two discharge passages 40 and 41 respectively connected to the two discharge ports 37 and 38 have the same passage length, and the two discharge passages 40 and 41 are connected to the common passage 49 at their respective terminal ends. Therefore, the discharge pulsations generated in the two windows 37 and 38 of the cylinder chamber 27 cancel each other out when passing through the common passage 49, and therefore the discharge pulsations are less likely to be transmitted to the outside.

As described above, according to the present embodiment, the discharge passages 40 and 41 having the same passage length are connected to the windows 37 and 38 communicating with the discharge holes of the cylinder chamber 27, and the discharge passages 40 and 41 are connected. Since the respective end sides are connected to the common passage 49, the discharge pulsations generated in the windows 37 and 38 of the cylinder chamber 27 and having different phases by half a wavelength cancel each other out when passing through the common passage 49. Pulsations are difficult to transmit to the outside. Therefore, in this embodiment, the pulsation on the discharge side can be suppressed and the generation of noise due to the discharge pulsation can be reduced without increasing the size of the entire apparatus and significantly increasing the production cost.

In the above embodiment, the gas compressor in which the compression capacity of the cylinder chamber 27 is variable has been described.
The present invention can also be applied to a gas compressor in which the compression capacity of the cylinder chamber 27 is fixed. In the above embodiment, the discharge passage 4
0 and the discharge passage 41 are commonly connected on the terminal side to the common passage 4
9 is provided and the common passage 49 is used as the place for arranging the oil separator 42, but the passage for arranging the oil separator 42 separately from the common passage 49 may be connected to the common passage 49. .

[0032]

As described above, according to the gas compressor of the present invention, two discharge passages having the same passage length are connected to each of the two discharge ports of the gas compressing section, and each end of these two discharge passages is connected. Since the sides are connected to the common passage, the discharge pulsations generated at the two discharge ports of the gas compression unit and having different phases by half wavelength cancel each other out when passing through the common passage. It is hard to convey. Therefore, according to the present invention, it is possible to suppress the pulsation on the discharge side without increasing the size of the entire apparatus and to greatly increase the production cost, and to reduce the noise generated due to the discharge pulsation.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a gas compressor that is an embodiment of the present invention.

FIG. 2 is a view of the gas compressor seen from the direction of the arrow Y-Y in FIG.

FIG. 3 is a sectional view of a rear side block.

FIG. 4 is a right side view of the rear side block.

FIG. 5 is a cross-sectional view of an oil separator block.

FIG. 6 is a left side view of the oil separator block.

FIG. 7 is a right side view of the oil separator block.

FIG. 8 is a cross-sectional view of a schematic configuration of a conventional vane rotary type gas compressor.

9 is a diagram viewed from the direction of arrow XX in FIG.

[Explanation of Codes] 21 Gas Compressor 22 Casing 23 Front Head 24 Cylinder Block 25 Control Plate 26 Rear Side Block 27 Cylinder Chamber 29 Vane 30 Rotor 31 Rotor Shaft 32 Suction Chamber 34, 35 Suction Hole 37, 38 Window 39 Oil Separation Block 40, 41 Discharge passage 42 Oil separator 44 Discharge chamber 49 Common passage

Claims (1)

[Claims] 1. A gas is sucked from two suction ports at different timings by the rotational movement of an odd number of vanes,
Each of the sucked gases is compressed by a volume change caused by the rotational movement of the vane, and each of the compressed gases is discharged from two discharge ports provided at point symmetrical positions corresponding to the two suction ports at different timings. A gas compression part to be discharged, two discharge passages connected to each of the two discharge ports of the gas compression part and having the same passage length, and a common passage commonly connected to each end side of the two discharge passages. A gas compressor comprising: