JPS59176490A - Screw compressor - Google Patents

Abstract

PURPOSE:To prevent a reversed flow of gas to the suction side due to the engagement of rotors during the suction, decrease the suction pulsation, suppress unpleasant noises, and improve the volume efficiency by inserting a baffle plate between a suction port and rotors. CONSTITUTION:When a male rotor 7 and a female rotor 8 are rotated, the inflow gas is introduced into a space formed by a tooth profile gap between the male rotor 7 and female rotor 8 and the inner peripheral surface of housing spaces 5, 6 and is shifted while being joined and compressed at the boundary portion between the housing spaces 5, 6. The gas entering a suction chamber 17 during the compression action is guided by a baffle plate 19 and is shifted to the tip portion 17a of the suction chamber, thus being made easy to enter into a compression chamber 25, and the volume efficiency is improved. In addition, the gas periodically blown up toward a suction port 18 when a tooth profile passes due to the rotation of both rotors 7, 8 is bent to the compression chamber side 25 by a baffle plate 19, thus inflicting no effect on the inflow gas.

Description

DETAILED DESCRIPTION OF THE INVENTION Technical Field The present invention is directed to a housing in which a male rotor having convex helically cut teeth and a female rotor having concave helically cut teeth are meshed with each other in a housing. This invention relates to a screw compressor that performs compression while avoiding active rotation.

PRIOR ART In the conventional slurry 1-compressor, as shown in FIG. 8, when the male rotor 7 and the female rotor 8 are rotated in the direction of the arrow in the same figure, gas flowing into the suction chamber 17 from the suction port 18 is transferred to the male rotor 7. The female rotor 8 is taken into the space formed by the tooth-shaped gap and the inner peripheral surface of the housing space 5.
is taken into the space formed by the recess of the housing space 6 and the inner peripheral surface of the housing space 6, and then meets at the boundary between the housing spaces 5 and 6. Since Ai L is not compressed, it is moved to the A7 side. However, in this screw compressor, since there is no obstacle between the suction port 18 and the rotor 7.8,
11i1 As the rotors 7.8 rotate, each time their teeth pass, a J gas flow is generated as indicated by the 0 arrow, which is opposite to the intake gas flow indicated by the P arrow, so the intake gas flow is obstructed. There was a problem in that the suction pulsation became large, and as a result, the pulsation was transmitted to the evaporator side, producing an unpleasant sound.

Purpose of Defense The present invention has been made in order to eliminate the above-mentioned conventional defects, and its purpose is to improve the gas flow when passing through the teeth of the rotor by interposing a baffle plate between the suction port and the rotor. To provide a screw compressor that can eliminate the obstruction of the suction gas flow, reduce suction pulsation, suppress unpleasant sounds on the vaporizer side, and improve volumetric efficiency. be.

Structure of the Invention The present invention has been made to achieve the above object, and its gist is that a baffle play 1 is provided between the suction port and the rotor.

Embodiment 1 Hereinafter, Embodiment 1 embodying the present invention will be explained with reference to FIGS. 1 to 4. Freon 1 to housing 2 are bonded and fixed to the front end surface of center housing 1, and a beam A is attached to the rear end surface.
7. A rear housing 4 is joined and fixed via a lead plate 3. Inside the center housing 1, a pair of left and right cylindrical housing spaces 5 and 6 are formed parallel to each other in the front-rear direction and slightly overlapped in the left-right direction.

One housing space 5 accommodates a male rotor 7 having convex helically cut teeth, and the other housing space 6 houses a female rotor 8 having concave helically cut teeth. . As shown in FIG. 4, one male rotor 7 is fitted and fixed onto a drive shaft 11 that is rotatably supported in shaft holes 2a and 3a of the front housing 2 and rear sight plate 3 via a radial needle bearing 9. , the other female rotor 8 is fitted and fixed onto a driven shaft 12 rotatably supported by a radial needle bearing 10 in the shaft holes 2b, 3b of the front housing 2 and rear sight plate 3.

A shaft seal mechanism 13 is interposed in the shaft hole 2a, and a seal chamber S to a seal chamber S is formed.

In addition, a blind cover 13' is installed inside the shaft hole 2b) []
In addition, a 67i bearing chamber is formed.
Thrust bearings 14 are fastened and fixed to the rear side end surfaces of the drive shaft 11 and driven shaft 12 by bolts 15, respectively, and a cover 16 that covers the thrust bearings 14 is bonded and fixed to the surfaces 11i of the rear side plays i to 3. So, rear bearing? R is formed.

On the other hand, as shown in FIGS. 1 and 2, a suction chamber 17 is formed in the upper part of the center housing 1 on the side facing the front 1, and corresponds to the housing space 5.6. A suction port 18 communicating with an external circuit is formed opposite to the meshing portion of the male rotor 7 and female rotor 8. The inner wall surface of the suction chamber 17 has a suction [] 18 and a rotor 7.8.
A baffle plate 19, which is an important part of the present invention, is supported in a cantilever manner so as to be located between the two. The front housing 2 is provided with a first oil supply hole 20h'' which communicates the suction chamber 17 with the shaft seal chamber S as shown in FIG.
A second oil supply hole 21 is provided which communicates the shirt 1 to the seal chamber S and the tip 17a of the suction chamber 17, and a third oil supply hole which communicates the suction chamber 17 and the freon 1 to the bearing chamber F. 22 are set up.

A discharge chamber 23 formed by the rear sight plates 1 to 3 and the rear housing 4 is formed by the accommodation space 5.6 and both rotors 7.8 through the 11 outlet holes 24 provided in the rear side plate 3. The compression chamber 25 is in communication with the compression chamber 25, specifically, the compression chamber 25 in the latter half of the compression stroke. A discharge valve 26 and a retainer 27 are fixed to the cover 16 in correspondence with the discharge hole 24 and the like. A filter 28 for oil separation is provided in the discharge chamber 23, and a discharge port 29 is provided in the rear housing 4.Next, the function of the screw compressor constructed as described above will be explained. Explain.

Now, when the A-throw tough and the female rotor 8 are completely rotated in the direction shown by the arrow in FIG. 2 by the drive mechanism (not shown), the suction 1]f flowing into the suction chamber 17 from the suction 1]18 is accommodated in the tooth-shaped gap of the A-throw tough. It is taken into the space formed by the inner peripheral surface of the space 5, and taken into the space formed by the recess of the female rotor 8 and the inner peripheral surface of the housing space 6, and then the housing They merge at the boundary between the spaces 5 and 6 and are moved toward the rear side in FIG. 1 while being compressed. Then, at the end stage of the compression stroke, the discharge hole 24 is opened to the discharge chamber 2.
3.

During the compression operation, the gas entering the suction chamber 17 from the suction port 18 passes through the baffle plates 1 to 1 as shown in FIG.
9 and is moved to the tip 17a of the suction chamber 17, making it easier to enter the compression chamber 25 during the suction stroke, improving volumetric efficiency. Further, the gas periodically blown toward the suction port 18 when passing the tooth pattern by the rotation of the two-eye tough 8 is bent by the baffle plays 1 to 19 and flows into the compression chamber 25 during the suction stroke. It does not have a negative effect on the gas generated. As a result, the suction pulsation is reduced and unpleasant vibrations and vibrations are prevented from being transmitted to the evaporator side (inside the room), and the flow of waste becomes smooth, improving volumetric efficiency.

On the other hand, the gas flowing in from the suction hole 18 is moved to the first oil supply hole 20 by the baffle plates 1 to 19 as shown in FIG.
The pressure near the tip 17a of the suction chamber 17 is lower due to the suction action of the rotor 7.8.
First oil supply hole 20 → shaft seal chamber S → second oil supply hole 21
→The gas flow at the tip 17a of the suction chamber 17 becomes more active, and the lubrication and cold N1 effect of the seat 71 to the seal mechanism 13 increases. Also, a part of the oil containing dregs in the shaft seal chamber S passes through the front side radial groove leg 9 and flows into the compression chamber 25 during the suction stroke (
(see arrow in Figure 4), radial needle bearing 9
lubrication is performed. Further, a part of the gas in the suction chamber 17 passes through the third oil supply hole 22 to the Noron L-Peno 7 ring chamber F.
radial needle bearing 1 on the front side.
0 to the compression chamber 25 during the suction stroke (see arrow in FIG. 4), the radial needle bearing 1o is lubricated.

The lubrication of the full needle bearing 9゜10 and the thrust bearing 14 is achieved by a portion of the blow-by gas flowing from the compression chamber 25 in the latter half of the compression stroke to the compression chamber 25 in the first half of the compression stroke. This is done by passing .10.1=1.

Embodiment 2 In Embodiment 2 shown in FIG. 5, the baffle plate 19 is curved so as to be convex toward the suction port 18, but other than that, the structure is the same as in Embodiment 1. Therefore, this second embodiment is characterized in that the gas inhaled from the suction port 18 enters the suction chamber 17 and then flows more easily toward the tip 17a of the suction chamber 17, thereby further improving the volumetric efficiency. However, other functions and effects are the same as those of the first embodiment.

Embodiment 3 Embodiment 3 shown in FIGS. 6 and 7 is a baffle plate 1.
A baffle plate 9 is formed separately from the center housing 1 and fixed to the housing 1 with bolts 30, and a large number of small holes 19a are formed through the baffle plate 19.

Therefore, in this third embodiment, when a large amount of oil or liquid refrigerant flows in from the suction hole 18, most of the oil or liquid refrigerant is sprayed onto the rotor 7.8 through the small hole 19a.
Due to the rotation of the rotor 7.8, these oils and the like are scattered and become powder mist before being sucked into the compression chamber 25. At this time, the oil is distributed throughout the rotor 7.8, making it difficult for liquid compression to occur. (The wind pressure caused by the rotation of the rotor 7.8 can be sufficiently reduced even with the baffle plate 1 with the small holes 19a, so the reduction in suction pulsation and the improvement in suction efficiency described in Examples 1 and 2 can be achieved. We can expect it.

Effects of the Invention As detailed above, the present invention provides a screw compressor in which a suction chamber and a suction hole are provided corresponding to the circumferential surface of the rotor.
A baffle brake 1 is provided between the suction hole and the rotor, so that when the rotor passes through the rotor's teeth, the blowing gas prevents the suction gas from diffusing and smoothly transfers the suction scum into the compression chamber during the suction stroke. This reduces the suction pulse VJ, eliminates unpleasant noise on the evaporator side, improves the suction efficiency, and increases the compression capacity J.
It has the effect of increasing the lubricity of the seal, and roughly improving the lubricity of the seal.

[Brief explanation of the drawing]

1 to 4 show Embodiment 1 of the present invention, FIG. 1 is a longitudinal sectional view of the central part, FIG. 2 is a sectional view taken along the line A-A of FIG.
The figure is a sectional view taken along line B-B in Figure 1, and Figure 4 is a cross-sectional view taken along line C-C in Figure 2.
A line sectional view, FIG. 5 is a cross sectional view showing Embodiment 2 of the present invention,
6 and 7 show Example 3 of the present invention, FIG. 6 is a longitudinal sectional view of the central part, FIG. 7 is a sectional view taken along line I)-D in FIG. 6,
FIG. 8 is a cross-sectional view, not showing a conventional example. Rental housing 1, front housing 2, rear side plate 3, rear housing 4, male rotor 7, female rotor 8, suction chamber 17, suction hole 18, baffle plate 19, shirt 1 to seal chamber S.

Claims (1)

[Scope of Claims] 1. A male rotor having a convex helically cut tooth profile, a female rotor having a concave helical cut tooth profile [21- The rotor has a concave helical cut tooth profile] By meshing, a suction chamber is provided on the front side of the housing, a suction port is provided opposite the outer peripheral surfaces of the two rotors, and a discharge hole is provided roughly on the rear side to actively rotate the two rotors. A screw compressor configured to perform a compression action, characterized in that a baffle plate 1- is interposed between the suction port and both rotors. 2. The screw compressor according to claim 1, wherein the baffle plate has a plurality of small holes. 3. The screw compressor according to claim 1, wherein the baffle plate is curved so that the suction port side is convex. 4. The screw compressor according to claim 1, wherein the area of the baffle plate is larger than the passage area of the suction port.