JP4071532B2 - Gas compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gas compressor, and more particularly to a gas compressor in which a suction resistance when refrigerant gas is sucked into a compression chamber is reduced and a gas density is improved.
[0002]
[Prior art]
Gas compressors are used for indoor air conditioning and refrigeration. As shown in FIG. 5, the gas compressor 50 has a left side wall of the front head 9 in contact with a circular cylindrical opening end 54 formed at the right end of the case 52.
[0003]
The front head 9 is formed with a suction port 51 that sucks refrigerant gas from an evaporator (not shown) connected to the outside, and a suction chamber 15 that communicates with the suction port 51 and is a low-pressure space having a relatively large volume. Yes.
[0004]
The gas compressor 50 has a compressor body 1. The compressor body 1 includes a cylinder 4 interposed between a low pressure side block 2 and a high pressure side block 3, and a rotor 5 is rotatably disposed in the cylinder 4.
[0005]
FIG. 6 is a cross-sectional view taken along the line AA in FIG. However, in FIG. 6, the low-pressure side block inlets 61A and 61B are virtually shown on the same drawing for convenience as shown by the alternate long and short dash lines on the same drawing. It is a thing.
[0006]
The compressor body 1 is inserted inside the case 52. The peripheral wall portion of the low-pressure side block 2 separates a slight gap from the inner wall of the case 52, and the peripheral edge portion of the right end is in contact with the left side wall of the front head 9. Further, a triangular groove 67 is cut out at the corner of the peripheral edge of the right end and is sealed by an O-ring 69.
[0007]
The rotor 5 is integrally provided with a rotating shaft 6 penetrating between the end faces, and the rotating shaft 6 is rotatably fitted in bearing holes 7 and 8 provided in both side blocks 2 and 3, respectively. . The rotary shaft front end side 6 a protrudes from the bearing hole 7 and is further extended to penetrate the front head 9.
[0008]
A seal chamber 10 is provided on the outer periphery of the rotary shaft front end side 6 a, and lubricating oil is supplied to the seal chamber 10 through a bearing gap G between the bearing hole 7 and the rotary shaft 6.
[0009]
FIG. 7 is a cross-sectional view taken along the line BB in FIG. A vane groove 12 is formed in the radial direction on the outer peripheral surface of the rotor 5, and a vane 13 is slidably mounted in the vane groove 12. The vane 13 is urged against the inner wall of the cylinder 4 by centrifugal force and hydraulic pressure at the bottom of the vane groove when the rotor 5 rotates.
[0010]
The cylinder 4 is partitioned into a plurality of small chambers by a pair of side blocks 2 and 3, a rotor 5, and vanes 13, 13. These small chambers are called compression chambers 14, 14..., And the volume of the chamber is repeatedly changed by the rotation of the rotor 5.
[0011]
In such a compressor body 1, when the rotor 5 rotates and the volume of the compression chambers 14, 14... Changes, the low-pressure refrigerant gas in the suction chamber 15 leading to the suction port 51 is sucked and compressed by the volume change. . At this time, the refrigerant gas is branched from the suction chamber 15 into the low-pressure side block suction ports 61A and 61B and then sucked into the compression chamber 14, respectively.
[0012]
A discharge chamber 19 is formed by the high-pressure side block 3 and the case 52. An oil separator 18 projects from the side wall of the high-pressure side block 3 toward the discharge chamber 19. The compressed high-pressure refrigerant gas is discharged into the discharge chamber 19 through the discharge port 16, the discharge valve 17, the oil separator 18, and the like.
[0013]
At this time, the oil separator 18 separates the oil from the high-pressure refrigerant gas, and the separated oil is collected at the bottom of the discharge chamber 19 to form an oil reservoir 20 for the lubricating oil. The high-pressure refrigerant gas from which oil has been separated is sent from the discharge port 53 to an external condenser (not shown).
[0014]
Further, salai grooves 35 and 36 communicating with the bottom of the vane groove are disposed around the rotary shaft 6 facing the rotor 5 of the low-pressure side block 2 and the high-pressure side block 3. Lubricating oil is supplied to the salai grooves 35 and 36 from the oil reservoir 20 through lubricating oil passages 37 and 38.
[0015]
On the other hand, power from an external drive source such as an engine or a motor (not shown) is transmitted to the transmitted portion by a belt (not shown). A bearing is incorporated in the transmitted portion.
[0016]
Next, the compression stroke in the compression chamber 14 will be described.
In the suction process until the volume of the compression chamber 14 reaches the maximum from the minimum, the refrigerant gas in the suction chamber 15 passes through the suction passage 41 such as the cylinder 4 and the low-pressure side block 2 and the high-pressure side block 3 that communicate with the suction passage 41. The air is sucked into the compression chamber 14 through a suction port (not shown). Then, when the volume of the compression chamber 14 becomes near the maximum, the compression chamber 14 is separated from the suction port and becomes a sealed space, and the low-pressure refrigerant gas is confined in the compression chamber 14.
[0017]
Next, when the volume of the compression chamber 14 that is the sealed space is shifted from the maximum to the minimum, the low-pressure refrigerant gas in the compression chamber 14 is compressed according to the volume reduction amount. Further, when the volume of the compression chamber 14 becomes near the minimum, the discharge valve 17 attached to the discharge port 16 of the cylinder 4 is opened by the pressure of the compressed high-pressure refrigerant gas. Then, the high-pressure refrigerant gas in the compression chamber 14 flows out from the discharge port 16 to the discharge chamber 45 formed on the outer peripheral surface side of the cylinder 4.
[0018]
The high-pressure refrigerant gas that has flowed into the discharge chamber 45 passes through a discharge passage (not shown) of the high-pressure side block 3 and then is discharged into the discharge chamber 19 through the oil separator 18.
[0019]
[Problems to be solved by the invention]
By the way, in the conventional structure of the suction chamber 15 and the low pressure side block suction ports 61A and 61B, two low pressure side block suction ports are opened to the suction chamber 15 which is one low pressure space. For this reason, in this low-pressure space, two refrigerant gas flows are generated, vortices are generated, or the flows interfere with each other, and the refrigerant gas suction resistance increases.
[0020]
Further, since the suction chamber 15 is a low pressure space having a cross-sectional area larger than the passage area of the suction port 51 and the low pressure side block suction ports 61A and 61B, the suction chamber in which the sucked refrigerant gas is the low pressure space. The time staying at 15 is long.
[0021]
Therefore, during the residence time, the refrigerant gas in the adjacent high-pressure space (the refrigerant gas on the outer periphery of the compression chamber 14 and the cylinder 4 is high in a pressurized state) passes through the low-pressure side block 2. It will be heated. As a result, the suction gas density may be reduced.
[0022]
The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a gas compressor in which the suction resistance when refrigerant gas is sucked into the compression chamber is reduced and the gas density is improved. And
[0023]
[Means for Solving the Problems]
For this reason, the present invention performs the compression of the refrigerant gas by the rotation of the rotating shaft on which the rotor is disposed, the front head formed with the suction port through which the refrigerant gas is sucked by the rotation of the rotating shaft, and the rotation of the rotating shaft. A cylinder in which a compression chamber is formed; a low-pressure side block disposed on the suction side of the cylinder; a high-pressure side block disposed on the discharge side of the cylinder; and the compression chamber on the low-pressure side block A plurality of low-pressure side block inlets that are formed so as to penetrate therethrough, and suction passages that branch from the suction port to the front heads and communicate with the low-pressure side block suction ports. passage after being straightened extended in straight pipe, an outlet end facing said low-pressure side side block suction port is extended in a straight pipe to the outlet end from the suction port tentative While has the the inhalation passage end surface with a predetermined inclination to be close to 90 degrees than the angle at the intersection of the low pressure side side block of time, and the feature that it is formed with a gentle curve without a step To do.
[0024]
By making the passage from the suction port to each low-pressure side block suction port independent as a suction passage, the refrigerant gas sucked from the suction port is smoothly sucked into the compression chamber without interfering with each other. Is done.
[0025]
Further, the refrigerant gas does not stay between the suction port of the front head and the low-pressure side block suction port, and heating by the refrigerant gas in the high-pressure space such as the adjacent compression chamber can be prevented. Accordingly, it is possible to prevent the suction gas density from being lowered.
The opening area at the outlet end of the suction passage is reduced. For this reason, the opening surface of the outlet end can be substantially aligned with the opening of the low-pressure side block suction port. And since the position can be aligned, the flow of the refrigerant gas becomes smoother. Moreover, it is easy to manufacture by extending the suction passage into a straight tube.
In addition, since the positioning can be performed more accurately, the refrigerant gas is less likely to stay between the suction port of the front head and the low-pressure side block suction port, and the influence of heating by the refrigerant gas in the adjacent high-pressure space is further reduced. Can be prevented.
[0026]
Further, the present invention is characterized in that the suction port has a depth enough to incorporate a check valve for preventing a back flow of the refrigerant gas.
[0032]
Furthermore, the present invention is characterized in that the cross-sectional area and length of each of the suction passages are adjusted so that the respective pipe resistances are equal.
[0033]
By equalizing the pipe resistance, the sucked refrigerant gas is evenly divided, the flow does not interfere further, and the refrigerant gas is sucked into the compression chamber with the same density. Accordingly, the amount of work in each compression chamber becomes equal, and torque fluctuations and the like can hardly be generated.
[0034]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a first embodiment of the present invention will be described. FIG. 1 shows a configuration diagram of a first embodiment of the present invention. 2 shows a cross-sectional view taken along the line CC in FIG.
The same elements as those in FIG. 5 to FIG.
[0035]
In the gas compressor 60 of FIG. 1, the suction port 51 is formed in two stages of a cylindrical head 51a and a cylindrical body 51b having a slightly smaller cross-sectional area than the head 51a. The body 51 b is extended to the vicinity of the rotating shaft 6 and not to contact the rotating shaft 6 as compared with the conventional gas compressor 50.
[0036]
One end of cylindrical suction passages 65A and 65B is connected to both sides of the body portion 51b in a “C” shape. The suction passages 65A and 65B are elongated in a straight tube shape, and the outlet ends are opened in an elliptical shape so as to communicate with the low-pressure side block suction ports 61A and 61B of the low-pressure side block 2.
[0037]
According to this configuration, by making the passages from the suction port 51 to the two low-pressure side block suction ports 61A and 61B independent of each other, the flow of the refrigerant gas sucked from the suction port 51 does not interfere with each other. The refrigerant gas is smoothly sucked into the compression chamber 14.
[0038]
Further, the refrigerant gas does not stay between the suction port 51 of the front head 9 and the low-pressure side block suction ports 61A and 61B, and heating by the refrigerant gas in the adjacent high-pressure space can be prevented. Accordingly, it is possible to prevent the suction gas density from being lowered.
[0039]
Since the body 51b of the suction port 51 is extended downward, a high-pressure refrigerant gas is discharged from the compression chamber 14 to the outside through the suction port 51 when the gas compressor 60 is stopped. In order to prevent backflow, a check valve (not shown) can be incorporated.
[0040]
Further, it is desirable that the passage length and the cross-sectional area of the suction passage 65A and the suction passage 65B coincide with each other. However, when the passage lengths of the suction passage 65A and the suction passage 65B are different, it is desirable to adjust the cross-sectional area so that the pipe line resistance becomes equal.
[0041]
For example, in the first embodiment of the present invention, as shown in FIG. 2, in order to avoid the position of the bolt 63, the suction port 51 is disposed slightly to the left of the center of the drawing, and the length of the suction passage 65A is increased. This is longer than the length of the suction passage 65B. At this time, the cross-sectional area of the suction passage 65A is formed wider than the cross-sectional area of the suction passage 65B so that the pipe resistances are equal to each other.
[0042]
As a result, the sucked refrigerant gas is equally divided, the flows do not interfere with each other, and the refrigerant gas is sucked into the compression chamber 14 with the same density. Accordingly, the amount of work in each compression chamber 14 becomes equal, and torque fluctuations and the like can hardly be generated.
[0043]
Next, a second embodiment of the present invention will be described. In FIG. 3, the block diagram of 2nd Embodiment of this invention is shown. Moreover, in FIG. 4, the DD arrow directional cross-sectional view in FIG. 3 is shown.
The same elements as those in FIG. 5 to FIG.
[0044]
In the gas compressor 70 of FIG. 3, the trunk portion 51c of the suction port 51 is configured with a short length, and the suction passages 71A and 71B branch diagonally downward in a “C” shape from directly below the trunk portion 51c. Is formed.
[0045]
That is, the suction passages 71A and 71B are arranged in a straight tube shape from one end connected to the body portion 51c along a plane perpendicular to the rotary shaft 6, and then the suction side of the low-pressure side block from the middle. It is gently curved toward the low-pressure side block suction ports 61A and 61B so as to communicate with the ports 61A and 61B.
[0046]
That is, the suction passages 71A, 71B are the suction passages 71A, 71A, when the outlet end facing the low-pressure side block suction ports 61A, 61B is assumed to extend straight from the suction port 51c to the outlet end. 71B is formed with a predetermined inclination so as to be closer to 90 degrees than the angle at which it intersects the end face of the low-pressure side block 2.
[0047]
According to such a configuration, the outlet end portion of the front head 9 which is the other end of the suction passages 71A and 71B has a circular opening surface as compared with the case of the first embodiment of the present invention (see FIG. 2) as shown in FIG. Formed close to.
[0048]
Therefore, the opening surface can be substantially aligned with the openings of the low-pressure side block suction ports 61A and 61B, and the flow of the refrigerant gas becomes smoother by the amount of the alignment.
[0049]
Further, the refrigerant gas is less likely to stay between the suction port 51 of the front head 9 and the low-pressure side block suction ports 61A and 61B, and the heating by the refrigerant gas in the adjacent high-pressure space can be further prevented. .
[0050]
【The invention's effect】
As described above, according to the present invention, since the suction passages are provided independently, the refrigerant gas sucked from the suction port is smoothly sucked into the compression chamber without interfering with each other. The
[Brief description of the drawings]
1 is a configuration diagram of a first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line CC in FIG. 1. FIG. 3 is a configuration diagram of a second embodiment of the present invention. A cross-sectional view taken along the line D-D of FIG. 5 [FIG. 5] A conventional gas compressor FIG. 6 A cross-sectional view taken along the line A-A in FIG. 5 A cross-sectional view taken along the line B-B in FIG. Explanation】
DESCRIPTION OF SYMBOLS 1 Compressor main body 2 Low pressure side block 3 High pressure side block 4 Cylinder 5 Rotor 6 Rotating shaft 9 Front head 14 Compression chamber 15 Suction chamber 18 Oil separator 19 Discharge chambers 65A, 65B, 71A, 71B Suction passages 60, 70 Gas Compressor 51 Suction port 52 Case 61A, 61B Low pressure side block suction port

Claims (3)

A rotating shaft on which the rotor is disposed;
A front head formed with a suction port through which refrigerant gas is sucked by rotation of the rotary shaft;
A cylinder formed with a compression chamber for compressing refrigerant gas by rotation of the rotating shaft, a low-pressure side block disposed on the suction side of the cylinder,
A high-pressure side block disposed on the discharge side of the cylinder;
A plurality of low-pressure side block suction ports formed through the low-pressure side block corresponding to the compression chamber;
A suction passage that branches off from the suction port and communicates with the low-pressure side block suction port on the front head;
When the suction passage is straightly extended by a straight pipe, the outlet end facing the low-pressure side block suction port is assumed to extend straight from the suction port to the outlet end. A gas compressor characterized in that the suction passage is formed with a gentle curve without a step while having a predetermined inclination so that the suction passage is closer to 90 degrees than an angle intersecting the end face of the low-pressure side block. .   The gas compressor according to claim 1, wherein the suction port has a depth enough to incorporate a check valve for preventing the refrigerant gas from flowing back. The gas compressor according to claim 1 or 2 , wherein each of the suction passages is adjusted in cross-sectional area and length so that the respective pipe resistances are equal.

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