JP2001329981A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor suitable for reducing the total cost of the compressor without impairing the oil separation performance necessary for the compressor and keeping the oil separation performance constant for a long time. SOLUTION: As a means for separating a lubricating oil component in a high pressure refrigerant gas, an oil separator 20 having pipe structure comprising only a discharge pipe 30 integratedly formed in a side block 3 is adopted. The discharge pipe 30 has a discharge route for the high pressure refrigerant gas, which does not make a detour from a discharge chamber 18 to just before the inner wall of a compressor case 1, and the lubricating oil component is separated by striking the high pressure refrigerant gas just after coming out of a cylinder discharge hole 16 to the discharge chamber 18 against the inner wall of the compressor case 1 through the discharge pipe 30 with high flow speed kept.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas compressor incorporated in an air conditioner system of a vehicle or the like, and more particularly, to reducing the cost of the entire compressor without impairing oil separation performance required for the compressor. Thus, the oil separation performance can be kept constant for a long period of time.

[0002]

2. Description of the Related Art Conventionally, this kind of gas compressor has a cylinder 2 having a substantially elliptical inner circumference inside a compressor case 1 as shown in FIG. Blocks 3 and 4 are attached.

[0003] In the case of the gas compressor shown in the figure, a compressor case 1 is formed of a housing 1-1 having an open end and a front head 1-2 attached to the open end thereof. A discharge chamber 5 and a suction chamber 6 are provided therein. The discharge chamber 5 is provided between the inside sealed end of the compressor case 1 (the inside sealed end of the casing 1-1) and one side block 3. The suction chamber 6 is provided between the inner side of the front head 1-2 and the other side block 4, respectively.

A rotor 7 is horizontally mounted inside the cylinder 2, and the rotor 7 is rotatably supported via a rotor shaft 8 of its axis and bearings 9 of the side blocks 3 and 4. As shown in FIG. 12, a plurality of slit-shaped vane grooves 11 are radially formed on the outer peripheral surface side of the rotor 7,
One vane 12 is mounted in each of the vane grooves 11, and the vanes 12 are provided so as to be able to protrude and retract from the outer peripheral surface of the rotor 7 toward the inner wall of the cylinder 2.

[0005] Inside the cylinder 2, the inner wall of the cylinder 2, the inner surfaces of the side blocks 3 and 4, the outer peripheral surface of the rotor 7 and the vanes 12
It is divided into multiple compartments by both sides on the tip side,
The partitioned small chamber is a compression chamber 13, and the compression chamber 13 in such a cylinder 2 repeats a change in volume by the rotation of the rotor 7 in the direction of arrow A in FIG.

When the volume of the compression chamber 13 changes, when the volume increases, the low-pressure refrigerant gas in the suction chamber 6 is released from the cylinder 2.
And the suction ports 15 of the side blocks 3 and 4.
Through the compression chamber 13. And the compression chamber 13
When the volume of the compression chamber 1 begins to decrease, the compression chamber 1
The refrigerant gas of No. 3 starts to be compressed. Thereafter, when the volume of the compression chamber 13 becomes close to the minimum, the pressure of the compressed high-pressure refrigerant gas opens the reed valve 17 of the cylinder discharge hole 16 provided in the cylinder 1 elliptical minor diameter portion. As a result, the high-pressure refrigerant gas in the compression chamber 10 is discharged from the cylinder discharge holes 16.
To the discharge chamber 18 in the outer space of the cylinder 1
Further, it is guided to the discharge chamber 5 side through the gas passage 19 and the oil separator 20. At this time, the high-pressure refrigerant gas discharged into the discharge chamber 18 contains lubricating oil in a mist state, and the lubricating oil component is mixed with the oil separating filter 21 made of a wire mesh or the like of the oil separator 20. Separated by collision.

[0007] As shown in FIG. 13, the lubricating oil component separated as described above is supplied to the oil sump 22 at the bottom of the discharge chamber 5.
It is dropped and stored. Further, the pressure of the high-pressure refrigerant gas discharged into the discharge chamber 5 acts on the oil reservoir 22, and the oil in the oil reservoir 22 on which the discharge pressure Pd acts acts on the side blocks 3 and 4 and the cylinder 1. Oil hole 2
3, through the gaps in the bearing 9 and through the sali-grooves 24 formed on the cylinder-facing surfaces of the side blocks 3 and 4 in that order, and are supplied to the back pressure chamber 25 at the bottom of the vane 12.

However, according to the conventional gas compressor, as shown in FIG. 11, the gas passage 19 for guiding the high-pressure refrigerant gas containing the lubricating oil to the oil separator 20 side is formed by the side block 3 and the oil separator 20. The side block 3 and the oil separator 20 are configured as separate components because of the relationship with the structure formed between the mounting mating surfaces. For this reason, the oil separator fastening bolt 26 for attaching the oil separator 20 to the side block 3
Not only do many parts such as (see FIG. 13) and the seal member at the attachment site are required, but also a process of assembling the oil separator 20 to the side block 3 on the compressor production line is required. However, there are various factors that increase the cost, resulting in an increase in the cost of the entire compressor.

In the conventional gas compressor described above, FIG.
As shown in (1), since the oil separator 20 is fixed to the side block 3 with the oil separator fastening bolt 26, a problem due to the loosening of the oil separator fastening bolt 26, for example, the oil separator fastening bolt 26 is loosened. The gap between the mounting surfaces of the side block 3 and the oil separator 20 is increased, and the gas passage 19 is opened.
There is also a problem that the high-pressure refrigerant gas before oil separation leaks out of the breach to the outside of the gas passage 19 to cause a decrease in oil separation performance, and a constant oil separation performance cannot be maintained for a long time. .

[0010]

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has as its object to firstly reduce the number of parts and the number of assembling steps related to an oil separator. To provide a gas compressor suitable for reducing the cost of the entire apparatus, and secondly, to provide a gas having a highly reliable oil separator capable of maintaining a constant oil separation performance required for the compressor for a long period of time. An object of the present invention is to provide a compressor.

[0011]

In order to achieve the above object, the present invention provides a cylinder disposed in a compressor case, side blocks mounted on both end surfaces of the cylinder, and an inner seal of the compressor case. A discharge chamber provided between the end and one of the side blocks, a cylinder discharge hole for discharging a high-pressure refrigerant gas containing lubricating oil compressed in the compression chamber in the cylinder to a discharge chamber in an outer space of the cylinder; An oil separator for separating a lubricating oil component in the high-pressure refrigerant gas guided from the chamber to the discharge chamber side, wherein the oil separator is formed integrally with the one side block and the discharge chamber And a discharge pipe having one end opened to the side and the other end opened toward the inner wall of the compressor case.

The present invention is characterized in that the discharge pipe forms a discharge route of high-pressure refrigerant gas from the discharge chamber to just before the inner wall of the compressor case without detour.

The present invention is characterized in that the discharge pipe is a straight pipe extending linearly from the discharge chamber toward the inner wall of the compressor case.

According to the present invention, the discharge pipe has one end opening toward the discharge chamber and the other end opening toward the inner wall portion of the compressor case, which is the closest position immediately after the discharge pipe has left the discharge chamber. It is characterized by the following.

[0015] The present invention is characterized in that the one side block and the discharge pipe are formed as an integral part of a casting.

According to the present invention, the means for integrally forming the one side block with the discharge pipe is provided with a pipe press-in hole communicating with the discharge chamber in the one side block, and the discharge pipe is provided in the pipe press-in hole. Is press-fitted at one end.

According to the present invention, the means for integrally forming the discharge pipe in the one side block is provided with a screw hole communicating with the discharge chamber in the one side block, Form a screw part,
The screw portion and the screw hole are engaged and fastened and fixed.

According to the present invention, the distance from the compressor inner wall side opening end of the discharge pipe to the compressor inner wall is as follows:
Assuming that the distance is L and the inner diameter of the opening end of the discharge pipe on the compressor case inner wall side is D, the following relational expression (1) is obtained.
Is satisfied. ^{(ΠD 2/4) ≦ πDL} ... formula (1)

The present invention relates to a compressor for the discharge pipe.
The open area of the open end of the case inner wall side is S ₁, Discharge pipe discharge
The opening area of the opening end on the exit chamber side is S₂And if
The ratio of the opening areas satisfies the following expression (2).
Things. S₁/ S₂≧ 0.7 Equation (2)

In the present invention, the high-pressure refrigerant gas compressed in the compression chamber in the cylinder is discharged to the discharge chamber in the outer space of the cylinder through the discharge hole of the cylinder. It collides with the inner wall of the compressor case through the discharge pipe, and the collision separates the lubricating oil component in the high-pressure refrigerant gas.

[0021]

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.

FIG. 1 is a sectional view showing an embodiment of a gas compressor according to the present invention. The basic structure of this gas compressor, for example, a cylinder 2 in a compressor case 1 is shown in FIG.
Are disposed, side blocks 3 and 4 are attached to both end surfaces of the cylinder 2, and a discharge chamber 5 is provided between one of the side blocks 3 and the inside sealed end of the compressor case 1. Since the high-pressure refrigerant gas compressed in the compression chamber 13 in the cylinder 2 is discharged to the discharge chamber 18 in the cylinder outer space through the cylinder discharge hole 16 as in the related art, the same members as those are denoted by the same reference numerals. However, detailed description thereof is omitted.

In the gas compressor of the present embodiment, FIG.
As shown in FIG. 5, the high-pressure refrigerant gas discharged into the discharge chamber 18 contains lubricating oil in a mist state,
The lubricating oil-containing high-pressure refrigerant gas is guided to the discharge chamber 5 side. In the present embodiment, as a means for separating a mist-like lubricating oil component from the high-pressure refrigerant gas, an oil separator having the following pipe structure is used. 20 are adopted.

The oil separator 20 of this embodiment comprises a discharge pipe 30 formed integrally with the side block 3 as a part of the rear side block 3, and this discharge pipe 30 is provided on the discharge chamber 18 side. One end is opened and the other end is opened toward the inner wall of the compressor case 1. In the present embodiment, a straight pipe 30-1 is used as such a discharge pipe 30. The straight pipe 30-1 is formed integrally with one of the side blocks 3 and the discharge chamber 18
From the compressor case 1 toward the inner wall. One end 30a of the discharge pipe 30 is open to the discharge chamber 18 side, but the other end 30b of the discharge pipe 30, that is, the open end of the discharge pipe 30 on the compressor case inner wall side is in front of the compressor case inner wall 1b. Is formed to reach.

That is, in the present embodiment, the straight high-pressure refrigerant gas having no detour from the discharge chamber 18 to immediately before the compressor case inner wall 1b is employed by employing the discharge pipe 30 in the form of the straight pipe 30-1 as described above. Is formed.

As described above, the structure for avoiding the bypass of the discharge route is employed because the flow velocity of the high-pressure refrigerant gas is prevented from lowering due to the bypass, and the high-pressure refrigerant gas having a high flow velocity collides with the inner wall 1b of the compressor case. This is because the lubricating oil component in the refrigerant gas can be effectively separated.

In this embodiment, as described above, the other end 30b of the discharge pipe 30 is connected to the inner wall 1b of the compressor case.
However, in order to improve the oil separation performance, a high-pressure refrigerant gas having a flow velocity as fast as possible is caused to collide with the inner wall of the compressor case 1. This is to cause more high-pressure refrigerant gas to collide with the inner wall of the compressor case 1.

That is, when the flow rate of the high-pressure refrigerant gas is compared immediately after leaving the discharge pipe 30 with a position farther away from the discharge pipe 30, the flow rate of the high-pressure refrigerant gas is highest immediately after leaving the discharge pipe 30. Therefore, in order to cause the high-pressure refrigerant gas having a high flow velocity to collide with the inner wall 1b of the compressor case, it is preferable that the other end 30b of the discharge pipe 30 be configured to reach just before the inner wall 1b of the compressor case.
If the distance L from the other end 30b of the discharge pipe 30 to the inner wall 1b of the compressor case is too long, the discharge pipe 3
It is considered that a part of the high-pressure refrigerant gas ejected from 0 diffuses into the discharge chamber 5 before colliding with the inner wall 1b of the compressor case, and the collision amount of the high-pressure refrigerant gas with the inner wall 1b of the compressor case is reduced. Therefore, in order to cause more high-pressure refrigerant gas to collide with the inner wall 1b of the compressor case, it is preferable to shorten the distance from the other end 30b of the discharge pipe 30 to the inner wall 1b of the compressor case.

By the way, from the viewpoint of improving the oil separation performance only, as described above, the other end 3 of the discharge pipe 30 is used.
The shorter the distance L from 0b to the inner wall 1b of the compressor case, the better. However, if the distance L is too short,
There is a problem that the power of the gas compressor increases and the cooling capacity decreases. This is because when the high-pressure refrigerant gas blows out from the other end 30b of the discharge pipe, the inner wall of the compressor case 1
It is considered that this is because b becomes a large resistance and the amount of high pressure refrigerant gas ejected and discharged from the other end 30b of the discharge pipe decreases accordingly. Therefore, the distance L has a certain lower limit from the relationship between the power of the gas compressor and the cooling capacity. Hereinafter, the lower limit of the distance L will be described.

From a basic point of view, if a discharge passage for the high-pressure refrigerant gas equal to or larger than the opening area can be secured at the other end 30b of the discharge pipe serving as the discharge port for the high-pressure refrigerant gas, It is considered that the discharge of the high-pressure refrigerant gas from the other end 30b of the pipe is smooth, and the increase in the power of the gas compressor and the decrease in the cooling capacity are small enough to cause no problem.

Therefore, between the other end 30b of the discharge pipe and the inner wall 1b of the compressor case, there is a cylindrical gap having the same diameter as the inner diameter D of the other end 30b of the discharge pipe. Is the discharge flow path of the high-pressure refrigerant gas, so the outer peripheral surface area of the cylindrical void (= πDL)
Is at least the opening area of the other end 30b of the discharge pipe (= πD
^2/4) and to be equal to or greater than, i.e. be configured so as to satisfy the following equation (1), there is no problem of reduced power increase and cooling capacity of the gas compressor. ^{(ΠD 2/4) ≦ πDL} ... Equation (1) D: inside diameter of the discharge pipe and the other end 30b L: distance from the discharge pipe and the other end 30b to the compressor case inner wall 1b

Therefore, from the above equation (1), the distance L from the other end 30b of the discharge pipe to the inner wall 1b of the compressor case is obtained.
Is D / 4. The upper limit of the distance L is determined from the relationship with the oil separation performance required for the gas compressor. This is because, as described above, as the distance L increases, the collision amount of the high-pressure refrigerant gas to the inner wall 1b of the compressor case decreases, and the oil separation performance decreases.

Next, the opening area of the other end (opening end on the inner wall side of the compressor case) 30b of the discharge pipe 30 is set to "S ₁ ",
One end (discharge chamber side open end) 30 of the discharge pipe 30
a is defined as “S ₂ ”, and the ratio of the opening areas (S ₁
/ S ₂ ), the opening area ratio (S ₁ /
S ₂ ) preferably satisfies the following expression (2). S ₁ / S ₂ ≧ 0.7 Equation (2)

This is theoretically based on the opening area ratio (S₁/
S₂) Is 1 or less, it is a discharge port for high-pressure refrigerant gas.
The opening at the other end 30b of the discharge pipe is
Since it is narrower than the opening, high pressure
Refrigerant gas is difficult to discharge, reducing the discharge flow rate of high-pressure refrigerant gas
Therefore, the power of the gas compressor increases and the cooling capacity decreases.
In particular, the opening area ratio (S₁/
S₂) Is 0.7 or less, such a gas compressor
The phenomenon of increase in power and decrease in cooling capacity occurred remarkably
It is. The opening area ratio (S₁/ S₂) Is 1 or more
In the case, the other end 3 of the discharge pipe which is the discharge port of the high-pressure refrigerant gas
0b must be wider than the opening at one end 30a of the discharge pipe.
High pressure refrigerant gas is discharged from the other end 30b of the discharge pipe.
Current and the discharge flow rate of high-pressure refrigerant gas decreases.
No elephants are produced, so the power of the gas compressor increases and
The ability does not decrease. Therefore, the opening area ratio
(S ₁/ S₂) Has a lower limit of 0.7,
Opening area ratio (S₁/ S₂For the upper limit of),
There are only design limitations arising from the relationship with the law, and theoretically
Is unlimited.

As described above, in order to integrally form the discharge pipe 30 with the one side block 3, the one side block 3 and the discharge pipe 30 may be integrally formed by casting. 30 and one side block 3 are formed as an integral part of a casting.

Referring to FIG. 13, also in the gas compressor of the present embodiment, the intake / compression process is completed within the range of 0 ° to 180 ° in terms of the rotation angle of the rotor 7,
This intake / compression process is the next 180-360 ° (0 °)
Since the structure is complete even within the range, the cylinder discharge holes 16
And a discharge chamber including a discharge chamber 18 and the like.
As shown in FIG. 2, in the present embodiment, the discharge pipe 30 is also connected to the rotor shaft 8 because of the fact that there are two discharge units including such a discharge chamber 18.
Are installed at positions 180 ° opposite to each other in total, two in total.

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

According to the gas compressor of the present embodiment, as shown in FIG. 1, the high-pressure refrigerant gas compressed in the compression chamber 13 (see FIG.
The high-pressure refrigerant gas immediately after the discharge collides with the inner wall of the compressor case 1 through the discharge pipe 30 at a high flow rate, and the collision causes the lubricating oil component in the high-pressure refrigerant gas to be discharged. Are separated.

Further, in the gas compressor of the present embodiment, as shown in FIG.
Since the two discharge pipes 30, 30 are provided at opposing positions, the high-pressure refrigerant gas discharged from the two discharge pipes 30, 30 may collide with each other. The lubricating oil component in the refrigerant gas is separated.

The lubricating oil component separated as described above is dropped and stored in the oil reservoir 22 at the bottom of the discharge chamber 5 as in the prior art. The high-pressure refrigerant gas after oil separation flows out and is supplied from the discharge chamber 5 to the external air-conditioning system through the external discharge port 1a of the compressor case 1.

As described above, in the gas compressor of the present embodiment, the oil separator 20 having the pipe structure including the discharge pipe 30 formed integrally with the side block 3 is employed. In terms of structure, unlike the conventional oil separator 20 structure shown in FIG. 12, the oil separation filter 21, the oil separator fastening bolt 26, and a sealing member such as an O-ring are not required, and the number of these components can be reduced. The oil separator assembling process on the compressor manufacturing line can be reduced.

According to the gas compressor of the present embodiment,
Since the side block 3 and the discharge pipe 30 are formed as an integrated casting, the oil separator fastening bolts 26 like the conventional oil separator 20 are loosened, and high-pressure refrigerant gas leaks before oil separation. There is no such part, and the discharge pipe 30 forms a discharge route of the high-pressure refrigerant gas that does not detour from the discharge chamber 18 to immediately before the inner wall of the compressor case 1. 1 and the like, it is possible to effectively separate the lubricating oil component in the high-pressure refrigerant gas from the collision with the inner wall, and it is possible to keep the oil separation performance constant for a long period of time.

FIG. 3 shows the results of a comparison test of the oil separation performance of the product of the present invention and the comparative example. FIG. 3A shows the compressor case when the compressor rotation speed (hereinafter abbreviated as “Nc”) = 800 rpm. FIG. 4B shows the result of examining the oil amount in the compressor case when Nc = 7000 rpm.

Here, the subject of the test will be briefly described.
The product of the present invention has an oil separator structure having two discharge pipes as in the above embodiment. Comparative Example 1 has a shape in which two discharge pipes are integrated into one piece in the middle, Comparative Example 2
Is an oil separator having an oil separating filter provided with a conventional oil separating filter made of a wire mesh.

According to the results of the comparative test shown in FIG. 3, the product of the present invention, the one having the discharge pipe structure as in Comparative Examples 1 and 2, and the one having the oil separating filter structure made of the conventional wire mesh as in Comparative Example 3 were different. The oil amount in the compressor case is smaller in the former case than in the former case, but the oil amount in the compressor case is the largest in the present invention, and the oil amount is A value close to that of the separation filter structure (Comparative Example 3) was shown. From this, when the discharge pipe of the oil separator is structured, it can be said that the form including two discharge pipes as in the present invention is a more optimal shape for improving the oil separation performance.

FIG. 4 shows the product of the present invention as described above.
It is a test result performed to investigate the correlation between the diameter of the discharge pipe and the oil separation performance, and the correlation between the distance from the other end of the discharge pipe to the inner wall of the compressor case and the oil separation performance.

In the drawing, φ10, φ7, and φ4 indicate the diameters of the discharge pipes. FIG. 3A shows Nc = 70.
The result of examining the oil amount in the compressor case as the oil level at 0 rpm and the discharge pressure Pd = 10 kgf / cm ² G is shown. FIG. 2B shows Nc = 700 rpm and the discharge pressure Pd = 15 kgf / cm ^2. FIG. 3 (c) shows the result of examining the oil amount in the compressor case as the oil level in the case of G, where Nc = 7000 rpm and discharge pressure Pd = 21 k.
The results of examining the oil amount in the compressor case at gf / cm ² G as the oil level are shown. In addition,
In each of the figures (a), (b), and (c), the oil level in the compressor case of the conventional product is plotted, and the horizontal axis position compares the oil level with the others. Therefore, there is no concept of the distance between the inner wall of the compressor case and the end of the pipe because there is no pipe in the conventional product.

As can be seen from the test results shown in FIG. 4, when the oil amount in the compressor case is compared for each diameter of the discharge pipe, the oil amount in the compressor case becomes the largest when the φ7 discharge pipe is used. I understand. Therefore,
A discharge pipe near φ7 is optimal for improving oil separation performance.

From the test results shown in FIG. 4, the distance L from the other end 30b of the discharge pipe to the inner wall 1b of the compressor case is shown.
Considering the correlation between the oil amount and the oil separation performance, in this test, when the distance L is 5 mm, the oil amount in the compressor case is significantly larger than that of the conventional product (the conventional gas compressor shown in FIG. 12). It can be understood that the oil amount in the compressor case tends to decrease as the distance L increases. Further, it can be seen that the distance L must not exceed the range of 10 to 15 mm in order to obtain an oil separation performance superior to the conventional product (see FIG. 4 (c)). Therefore, if the distance is in the range of 5 mm to 10 mm, oil separation performance superior to the conventional product can be surely obtained.

Further, it has been found that if the distance from the other end of the discharge pipe to the inner wall of the compressor case is constant, the length of the discharge pipe does not affect the oil separation performance.

FIG. 5A shows a test result of examining the correlation between the diameter of the discharge pipe and the power of the gas compressor in the above-described product of the present invention, and FIG. ,
FIG. 3C shows the results of a test performed to examine the correlation between the diameter of the discharge pipe and the flow rate of the refrigerant in the refrigeration cycle, and FIG. Note that the refrigerant flow rate of the refrigeration cycle is closely related to the cooling capacity of the gas compressor.The cooling capacity is high when the refrigerant flow rate of the refrigeration cycle is high, and the cooling capacity is low when the flow rate is low. As a method for determining the cooling capacity, the refrigerant flow rate of the refrigeration cycle was measured.

In the figure, the φ10 pipe is the other end (opening end on the inner wall side of the compressor case) 30b having an opening diameter of 10 mm.
mm using a discharge pipe 30 mm.
φ7 pipe and φ3 pipe have the same opening diameter of 7m each
m, 3 mm.
In this case, the opening diameter of one end (opening end on the discharge chamber side) 30a of any of the discharge pipes 30 is 10 mm.
It is. The test conditions shown in FIG.
00 rpm, discharge pressure Pd = 1.37 Mpa (14 kg
f / cm ² G), suction pressure Ps = 0.196 Mpa (2
kgf / cm ² G), superheat degree SH = 10 deg, supercool degree SC = 5 deg.

As apparent from FIG. 5 (a), it was found that the power of the gas compressor was smaller when a thick discharge pipe (φ10 pipe) was used. Also, as is clear from FIG. 3B, the use of a thick discharge pipe (φ10 pipe) increases the refrigerant flow rate of the refrigeration cycle.
It can be seen that the cooling capacity of the gas compressor is higher when a thick discharge pipe (φ10 pipe) is used.

Also, referring to FIG.
Considering the power and cooling capacity of the gas compressor based on the ratio between the opening area of b and the opening area of one end 3a of the discharge pipe,
In the case of a φ10 pipe having an opening area ratio of 1.0, which is the maximum, it is found that the power of the gas compressor is the smallest and the cooling capacity of the gas compressor is the best, and the opening area ratio is 0.7 ( Opening area ratio when using φ7 pipe)
It can be seen that the power gradually increases and the cooling capacity of the gas compressor gradually decreases as the ratio decreases to 0.3 (opening area ratio when a φ3 pipe is used). Therefore, from the experimental results, it is preferable that the opening area ratio be in the range of 0.7 to 1.0 in order to prevent an increase in power of the gas compressor and a decrease in cooling capacity.

In the above-described embodiment, the side block 3 and the discharge pipe 30 are integrally formed by casting. However, such a means for integrally forming the side block 3 and the discharge pipe 30 may be formed integrally with the casting. For example, FIG.
And the screw fastening structure shown in FIG. 7 can be adopted.

In the press-fitting structure shown in FIG. 6, a pipe press-in hole 31 communicating with the discharge chamber 18 is provided in one side block 3, and the discharge pipe 3 is inserted into the pipe press-in hole 31.
This is a structure in which one end 30a of the “0” is press-fitted.

In the screw fastening structure shown in FIG. 7, a screw hole 32 communicating with the discharge chamber 18 is provided in one side block 3, and a screw portion 33 is formed on the outer peripheral surface of one end 30a of the discharge pipe 30. 33 and the screw hole 32 are engaged and fastened and fixed.

In the above embodiment, the discharge pipe 30 in the form of a straight pipe 30-1 is employed as means for avoiding the detour of the discharge route and for causing the high-pressure refrigerant gas having a high flow velocity to collide with the inner wall of the compressor case 1. Instead, as shown in FIG. 8, a discharge pipe 30 having a shorter length than that of the above embodiment can be employed. In the case of this structure, one end 30a of the discharge pipe 30 opens to the discharge chamber 18 side as in the above-described embodiment, but the discharge pipe 30
The other end 30b of the discharge chamber 1 as shown in FIG.
Compressor case 1 at the closest position immediately after exiting 8
It is configured to open toward the inner wall portion (see FIG. 10). This is because, as described above, by shortening the distance to the inner wall of the compressor case 1, more high-pressure refrigerant gas collides with the inner wall of the compressor case 1 at a high flow rate.

[0059]

As described above, the gas compressor according to the present invention employs an oil separator having a pipe structure consisting of only a discharge pipe integrally provided in a side block. This eliminates the need for oil separation filters, oil separator fastening bolts, O-rings, and other sealing members as in conventional oil separators, reducing the number of these parts and assembling the oil separator on the compressor production line. The number of steps can be reduced, and the cost of the entire apparatus can be reduced.

Further, according to the gas compressor according to the present invention, as described above, since one side block and the discharge pipe are formed as an integrated product, the loosening of bolts as in the conventional oil separator can be prevented. Since there is no part where the high-pressure refrigerant gas leaks out before oil separation, and the discharge pipe forms a discharge route for the high-pressure refrigerant gas from the discharge chamber to just before the inner wall of the compressor case, the discharge route of the high-pressure refrigerant gas is formed on the inner wall of the compressor case. Since the high-pressure refrigerant gas having a high flow velocity collides, the lubricating oil component in the high-pressure refrigerant gas can be effectively separated, and the oil separation performance can be maintained constant for a long period of time.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a view taken in the direction of arrow B in FIG. 1;

FIG. 3 is an explanatory diagram of a comparison test result of oil separation performance of the product of the present invention and a comparative example.

FIG. 4 is a description of a test result obtained by examining a correlation between a diameter of a discharge pipe and an oil separation performance, and a correlation between a distance from the other end of the discharge pipe to an inner wall of a compressor case and an oil separation performance. FIG.

FIG. 5 (a) is a test result obtained by examining the correlation between the diameter of the discharge pipe and the power of the gas compressor in the product of the present invention;
(B) is a test result obtained by examining the correlation between the diameter of the discharge pipe and the discharge flow rate of the high-pressure refrigerant gas in the product of the present invention;
(C) is an explanatory diagram of the actually measured values of both test results.

FIG. 6 is an explanatory view of a main part of another embodiment of the present invention.

FIG. 7 is an explanatory view of a main part of another embodiment of the present invention.

FIG. 8 is a sectional view of another embodiment of the present invention.

FIG. 9 is a sectional view taken along line BB of FIG. 8;

FIG. 10 is a view taken in the direction of the arrow C in FIG. 9;

FIG. 11 is a cross-sectional view of a conventional gas compressor.

FIG. 12 is an enlarged sectional view taken along the line AA of FIG. 11;

FIG. 13 is a sectional view taken along line BB of FIG. 11;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor case 1-1 Housing 1-2 Front head 1a External discharge port 1b Compressor case inner wall 2 Cylinder 3, 4 Side block 5 Discharge chamber 6 Suction chamber 7 Rotor 8 Rotor shaft 9 Bearing 11 Vane groove 12 Vane 13 Compression chamber 14 Suction passage 15 Suction port 16 Cylinder discharge hole 17 Reed valve 18 Discharge chamber 19 Gas passage 20 Oil separator 21 Oil separation filter 22 Oil reservoir 23 Oil hole 24 Sarai groove 25 Back pressure chamber 26 Oil separator fastening bolt 30 Discharge pipe 30- DESCRIPTION OF SYMBOLS 1 Straight pipe 30a Discharge pipe one end 30b Discharge pipe other end 31 Pipe press-fit hole 32 Screw hole 33 Screw part

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification code FI theme coat ゛ (reference) F04C 29/00 F04C 29/00 B 29/02 351 29/02 351D F-term (reference) 3H003 AA05 AB07 AC03 BH05 CD05 3H029 AA05 AA17 AB03 BB31 BB32 BB35 CC25 CC38 CC42 CC44 3H040 AA09 BB05 BB11 CC15 CC16 CC19 DD01 DD23 DD33 DD35 DD36 DD37 DD38 DD40

Claims (9)

[Claims] 1. A cylinder disposed in a compressor case, a side block attached to both end surfaces of the cylinder, a discharge chamber provided between an inside sealed end of the compressor case and one side block, A cylinder discharge hole for discharging a high-pressure refrigerant gas containing lubricating oil compressed in a compression chamber in the cylinder to a discharge chamber in an outer space of the cylinder; and a lubricating oil in the high-pressure refrigerant gas guided from the discharge chamber to a discharge chamber. An oil separator for separating the components, wherein the oil separator is formed integrally with the one side block, and has one end open to the discharge chamber side and the other end facing the compressor case inner wall. A gas compressor comprising a discharge pipe having an open end. 2. The gas compressor according to claim 1, wherein the discharge pipe forms a discharge route of the high-pressure refrigerant gas which does not detour from the discharge chamber to immediately before the inner wall of the compressor case. 3. The gas compressor according to claim 1, wherein the discharge pipe is a straight pipe extending linearly from the discharge chamber toward the inner wall of the compressor case. 4. The discharge pipe is characterized in that one end thereof opens to the discharge chamber side, and the other end opens to the inner wall portion of the compressor case which is closest to the outlet pipe immediately after exiting the discharge chamber. The gas compressor according to claim 1, wherein 5. The gas compressor according to claim 1, wherein the one side block and the discharge pipe are formed as a single piece of a casting. 6. A means for integrally forming said one side block with a discharge pipe, wherein said one side block is provided with a pipe press-fitting hole communicating with said discharge chamber,
2. The gas compressor according to claim 1, wherein one end of said discharge pipe is press-fitted into said pipe press-fit hole. 7. A means for integrally forming a discharge pipe in said one side block, wherein said one side block is provided with a screw hole communicating with said discharge chamber.
The gas compressor according to claim 1, wherein a screw portion is formed on an outer peripheral surface of one end of the discharge pipe, and the screw portion and the screw hole are engaged and fastened and fixed. 8. The distance from the compressor inner wall side opening end of the discharge pipe to the compressor inner wall is represented by the following formula, where L is the distance, and D is the inner diameter of the compressor case inner wall side opening end of the discharge pipe. The gas compressor according to claim 1, wherein (1) is satisfied. ^{(ΠD 2/4) ≦ πDL} ... Equation (1) 9. When the opening area of the opening end of the discharge pipe on the inner wall side of the compressor case is S ₁ , and the opening area of the opening end of the discharge pipe on the discharge chamber side is S ₂ , the ratio of the opening areas is expressed by the following equation. The gas compressor according to claim 1, wherein (2) is satisfied. S ₁ / S ₂ ≧ 0.7 Equation (2)