JPS60212685A - Oil non-feed type rotary comressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an io1 rotary compressor, and more particularly to an oil-free compressor having interlocking impellers, each of which has a protruding structure on one side.

The prior art includes rotary oilless compressors of various designs. However, in such compressor operation, a compressor that achieves high compression efficiency and at the same time controls or reduces leakage rates has not yet been shown.

(3) This is 100 or 200 cubic feet/11 minutes (('f
='M) or 2.8 to 5.7 nI'/min
This is especially true in the 100 lb. industrial monthly air supply market.

In general, rotary compressors (↑) can be classified as screw or non-screw type.Screw type compressors have good internal compression efficiency, but are highly leaky devices due to the nature of their two-dimensional structure.200CI・A good screw type compressor has not yet appeared in "M".

A number of two-dimensional compressor configurations have been proposed to reduce leakage losses and improve the structural Qi net.

These installations are described in detail below. However, some have a combination of compression efficiency and leakage control that is sufficient to meet the generally unacceptable standards of 25 horsepower per 100 CI per million. It is enough to say that there is nothing.

100 maybe 200 (100 for FM size
To achieve the output of 441 lbs., J old take (1
) Must be. The compression ratio for each stage should be approximately 6. This compression ratio requires the compression efficiency of all stages to meet the performance level accepted as 64%. When a classic Roots compressor without internal precompression is used in each stage, the resulting compression efficiency is 6
It becomes 4.51%. Since the ideal performance level of the Roots compressor provides a measure of acceptance, it is useful and convenient to use this simple mechanism as a performance comparison. Some previous designs that used internal precompression schemes to improve efficiency actually resulted in efficiencies lower than those obtained using classical Roots compressors due to excessive leakage and excessive pressure losses. It is had. However, to achieve the acceptable performance and bells noted above, it is essential to use a high degree of built-in or internal precompression. In the ideal case,
The gain in compressor efficiency provided by precompression is on the order of 355%. The importance of precompression is therefore very clear. However, the objective is to achieve precompression in a device that can maintain good leakage control and that does not create excessive H-forces when discharging (5) the co-pressure gas.

U.S. Patent No. 2.097.037, 24', 3,5
No. 35.060, No. 3.894.822, No. 3.72
No. 3.031, No. 3.790.315 and No. 4.2
In the press compressor where θn is described in each specification of No. 24.016.

Since a pressure generation phase (precompression) and a separation phase are generated, gas is discharged about half of the time, and no gas is discharged the rest of the time. If the impeller speed is high, such unsteady discharge pulsations will cause an extreme excess pressure loss, so it is necessary to limit the impeller opening speed to a low speed of 100 feet/second or less. On the other hand, the ratio of leakage rate to impeller discharge capacity needs to be low. However, achieving such low ratios requires high pitch line speeds. Therefore, desired efficiency levels cannot be achieved with these low speed unsteady compressors.

Other prior known two-dimensional compressor designs are U.S. Pat.
No. 66.820 and No. 4.076.469. These devices significantly reduce overpressure (6) losses and therefore can use much higher impeller speeds than could be monthly in the unsteady devices described above. However, these prior skins use vanes 11 with at least six protrusions, making them expensive to manufacture, arrange, and assemble. Leakage losses are high due to the large number of displacement surfaces balanced by each cooperating contour.

ψ, a problem with the structure of the patent is when the pressure assembly and transmission process requires more than two profiles.

There is an expensive axial leakage path between the protruding tip of the intermediate profile (profiles) and the compressor housing, so that the high pressure gas in the third or last profile leaks directly into the suction pressure gas in the first profile. There's a lot of pressure. In the two profile configuration, this expensive leakage path does not exist.

- The problem of the related prior art, as well as other problems not specifically mentioned, is that it is extremely simple, highly efficient, low cost, and practical to use H'J and to produce 100 to 200 air or other gases.
The teachings of the present invention provide a rotary compressor capable of achieving generally accepted performance standards for compression in the CFM range (7).

The rotary compressor of the present invention defines two working chambers.

Wings 41.1 rotatably arranged for each task
Combine +lL, each feather is 41+! The car has at least two cross-sectional contours, each contour having only one protrusion and one
one quadrant of the profile has a housing in fluid communication with the volume to the recess 111 in the adjacent profile, and an inlet device in fluid communication with all of the profiles. , and an exhaust [-1 device that interacts periodically with each of the working chambers to continuously discharge gas,
The arcuate range of each contour and the angular displacement between adjacent contours are: - When the main recess on one side of the matching contour starts to engage with the convex part of the matching contour, on one contour of A'l mw. The secondary volume in the adjacent profile is still in communication with the inlet device, and the gas in the main recess is under pressure even though the secondary volume is still curved with the suction 1-I. increases, and this pressure increase (4r impeller pitch line speed is maintained sufficiently early) will be completely maintained (8).

By virtue of the invention, the compressor of the present invention achieves internal compression, constant gas discharge without excess pressure loss, and 10,000 displacement, while leakage losses serve to maintain a minimum pressure.

Indeed, since the profiles are all of substantially similar construction (with the exception of the transition surfaces), manufacturing is simplified and associated costs are reduced.

Next, the drawings will be explained. The central housing 10 has 1
A pair of working chambers 12 and 14 are provided which house a pair of rotatably associated impellers 16 and 18, respectively. The central housing 10 includes suitable end plates 20 and 22 at the axial ends of the working chambers 12 and 14, which plates define a closed casing for the impellers 16 and 18.

Impeller 16 is suitably arranged for rotation in the direction of arrow A and has a pair of adjacent two-dimensional or constant cross-sectional profiles 24 and 26. Similarly, the impeller 18 (9) is preferably arranged for rotation in the direction of the arrow 1 and is arranged for rotation in the direction of the arrow 1, with a pair of adjacent two-dimensional or constant transverse one-way contours 28 and 60.
what to do Wheel wheels 1s24 and 28 are defined by contours 26 and 3.
0 and are identically configured for interlocking engagement. The vanes 16 and 18 can be driven and conditioned in the usual manner by a pair of south-east filters 2 and 34.

An inlet or passageway arrangement is disposed at 5 in simultaneous communication with each pair of profiles in each vane. The device may take the form of a slot 36 extending between the end plates 20 and 220 along the axial depth of the working chambers 12 and 14 and extending equally into each working chamber. The outlet or passage device ft38 is located directly adjacent contours 26 and 3.
I' is provided on the end plate 20 so as to communicate equally with 0. As can be seen in FIG. 3, the four-foot outlet 38 is generally triangular in shape (though other suitable shapes may be used) and is located at the bottom of the joining tip 40 of the working chambers 12 and 14. and extends equally to 14.J
The end 71 (42) of the ν joint end 40 is the adjacent υ1 exit (10
) is removed in the contour 26 and 300 planes adjacent to 38, which makes υr
It should be noted that it provides the first flow path to the outlet.

The contour 24 consists of a single convex portion 44 and a semi-concave portion 46.
8 consists of a single convex portion 48 and a semi-concave portion 50 formed in the same manner. The convex portion 44 and the concave portion 46 are connected by a V-shaped transition surface 52. Similarly.

The convex portion 48 and the concave portion 50 are connected by a Y-concave transition surface 54 . The contour 26 consists of a single convex portion 56 and a semi-concave portion 58, and the contour 30 consists of a single convex portion 60 and a semi-concave portion 6 of the same shape.
It consists of 2. The convex portions 56 and the four portions 5B are connected by a flat tapered transition surface 64. Similarly, the protrusion 60 and the recess 62 are connected by a tapered flat transition surface 66. The protrusions 44, 48, 56 and 60 engage the inner wall of each working chamber in a substantially snug and sealing engagement.

Contours 24 and 26 angularly converge with each other (11) such that the rear end of recess 46 overlaps and communicates with the distal end of recess 58. A similar angular relationship exists between contours 28, 1 and 30, respectively, and concavities 111 to 50:t, 5 and 60.
l(l lt.

Finally, pass through the joint end 40 - (77R minute or concave 111
The "tip" means the part or recess that first passes through the joining end 40.

- Before explaining the operation of the above-mentioned JE compressor, it is important to note that the IIT compressor of the present invention has a relatively high Achieve L ij
Since it is outside the realm 1 to process the method W1, the structure between the convex part to the concave 4/1 and the concave FXIX;
I will trace back the person in charge. The convex part and the concave part of each contour have an angle 1: range of 1fV1B[]o.The centers of the four parts of contour 26 and contour 30 are respectively By moving the concavity f<1' of the contour 28 to the center (as shown in Fig. 71) by about 165°,
Ichikawa - 15° between the tip of each convex portion 44.48 and the rear end of each convex portion 56.600! Provide JJ with an open fan shape.

In this open fan shape, the four parts of each contour in each working chamber are connected. The rear end of each convex portion 11A, 11B and each 1'
! The tip of IKl- is rli, which prevents communication from quadrilateral to quadrilateral in these regions (12).

If the compression ratio is only about 2, then the center of the four parts of profile 26.30 may lag the center of the recess of profile 24.28 by about 11Cr.However, if the compression ratio is 3, The lag of the recess centers is required to be at least 160°, and this requirement is met by the 165° shown.This angular relationship or offset between the recess centers allows the recess 56 to be delayed after 0. The end is the outlet part 3
The degree of internal precompression that can occur before the first appearance of the quadrature corresponding to 8 is determined. Indeed, for compression ratios greater than 2, contours 24 and 28 should be wider than contours 26 and 30, as shown.

Figures 4 through 9 are similar to Figure 2 and should be referred to as an aid to understanding the operation of the compressor according to the present invention.

In the position of the impeller shown in FIG. 4, the convex portion 48 (13) is connected to the discharge port 38 in the closed state, which communicates with the concave portions 46 and 58 by the action of the four portions 46 and the side surfaces of the convex portions 56. IIs where the tip advances? , 111d culm is about to start in the working room. In this position, the recess 58 communicates with the intake port 36 and encloses the gas of the intake FE.

11 between the tip of the convex part 44 and the rear end of the convex part. be.

After about 1〆t, the convex part 48 absorbs four parts of gas 7+
It is clear that the convex portion 60 eventually advances to the concave portion 58, thereby discharging the gas in the concave jτl 558 to the exhaust 1138.

As mentioned above, it is an objective of the compressor of the present invention to provide a madder pitch linear velocity that achieves a low percentage of +JF air leakage. The trap and pinch speed was set to 250 ft/sec and the single suction pressure was set to 1 for the n snake (No. 4 - Figure 9). Therefore, the gas in the recess 46 is placed at the junction provided by the protrusion 48 (so that the gas in the recess 46 is moved counterclockwise through the fourth part 58 toward the inlet 36 by 1.13 mm).
A shock wave is generated in the four parts 46 that travels at a Matsuha number of .

The pressure behind this shock wave, or front, increases at a rate of about 1.33", and this front is indicated by X in FIG.

The pressure in the recess 46 after the shock front X is approximately 1.3 of the inlet pressure.
3, but the pressure in the recesses 46 and 58 in front of the front line is between the inlet pressure and the inlet 36;
nl L, and gas continues to be taken into it -(
It is important to note that there are

If the pitch linear velocity of the impeller is low, e.g. 100 ft/
In this case, the pressure after front X would be low enough to flow back into the suction and significantly reduce compressor performance. The shock wave at is sufficiently large that the gas after the shock S wave is not discharged back out of the inlet.

FIG. 6 shows the relationship between the impellers to prevent the high pressure gas after #JX before impingement from being discharged back to the suction port 36. 6th
As shown in the figure, the active end of the protrusion 56 begins to block the communication between the suction port 6 and the recess 58 when the impact front arrives.

Therefore, the pressure after this front is yl of the inlet pressure, 33
It has been maintained twice as much. In fact, in the case of air, the first compression impulse (15).If the zero-wave nose gear is involved or [-captured], the pitch net velocity in the blade is at least 'j 200 feet 1-/ It became clear that it had to be ↑11 seconds.

This velocity will vary depending on the working fluid ('f). It is clearly within the scope of the present invention to include fluids other than air.
It should be noted that fi remains in communication with the suction port 66 until it is rotated by y45°. At point 16 shown in FIG. 7, when the first shock wave front is reflected at the active end of the convex portion 56, a second shock wave front is generated at X2, and the pressure of the gas after this front is The oral pressure is approximately 1.731f'i. As shown in the figure, the front #1 This third 1ffi front is indicated by X3 in FIG. 8 and increases the gas pressure in the trowel to about 226 times the inhalation [1 pressure]. When the front X3 is reflected from the active part of the convex portion 56, a final shock wave front is generated as indicated by X in FIG.
138 (16) 1ii7 and advance counterclockwise.The gas pressure after this front X4 is increased to the final internal precompression level K, which is approximately three times the inlet pressure. Immediately after the position where is
Front line X4 reaches the engaged position and the total volume of recess 58 is at final pressure. At this point, the tip of the protrusion 56 exposes the recess 58 to the outlet 58, and as a result of the engagement of the protrusion 60 with the recess 58, the gas is evacuated to the point of use. Repeat the above operations for the left impeller for the second half of the next trap compression cycle. Therefore, no further explanation seems necessary on this point.

Although the above description has referred to an impeller with two profiles, in practice, for mechanical balancing, on impeller 16 the same profile 26 and on impeller 18 the same profile 30. It is desirable to use a third profile on each impeller that is . This arrangement is shown in FIG. 10, where all reference numbers are the same as used above except that the number for the third profile is primed.

In the apparatus of FIG. 10, flows from contours 26' and 30' (
17) Another one same as the outlet 38 for receiving the coming gas
-1 is provided on the end plate 22, and it is necessary to merge these streams 1 on the outside of the housing 10.
It is clear that

Although the preferred embodiment of the present invention has been described with the body side open, it will be clear to those skilled in the art that the same can occur during the meal.

It is the intention, therefore, to be limited only by the scope of the claims appended hereto.

[Brief explanation of the drawing]

To better understand the invention and its features. Reference should be made to the detailed description in conjunction with the accompanying drawings below. Figure 1 is Jl: Working Feather 411! A plan view of the pressure lrA machine with a portion of the housing removed to illustrate the east side, FIG. 2 is a cross section taken approximately along line 2-2 in FIG. 3, FIGS. 4 to 9 are sectional views similar to FIG. 3, and FIG. 10 is a sectional view similar to FIG. 1. FIG. 4 is a plan view of an embodiment in which each working chamber is provided with a third impeller profile to provide a symmetrical and balanced structure (18); 12, 14: Working chamber 16.18: Impeller 24.26, 28, 30: Contour 44.48, 56, 60: Convex portion d6.50, 58.62: Recessed portion '56 = Inlet port 68: Outlet port patent Applicant Roger C. Weatherston (19)

Claims (1)

[Scope of Claims] (1) a casing defining two working chambers; an impeller rotatably disposed in each working chamber and having at least two constant cross-sectional contours; directly connected to all of said contours; An oil-free rotary compressor comprising: an inlet device in fluid communication; and an outlet device cyclically and alternately cooperating with each of the working chambers to continuously discharge gas, comprising: Each cross-sectional profile has one convexity and one concavity, and the recessed volume of any profile is in fluid communication with the recessed volume of any other profile of each impeller; What is the arcuate range of a contour and the angular displacement between adjacent contours? When the tip recess volume of the first contour starts to engage with the protrusion of the mating contour to compress and round the gas, the contour adjacent to the first contour ((1) in which the rear end recess volume is 11il) Inhalation [1 In communication with device a (
- An oil-free rotary compressor 3 configured to The compressor according to claim 1(4) completely retains Ichikawa's gas in the volume of the concave portion at the tip end even if it is in communication. Front M+'3 inhalation [1 裟I
2. A compressor according to claim 1, wherein said communication with said suction port device 1 lasts for at least approximately 4 to 5 degrees of rotation of the impeller before communication with the suction port device 1 is interrupted. (4) The compressor according to claim 1, wherein each of the arcs of the convex portion and the four Aft portions has an extent of approximately 180°, and each of the first arcs has a substantially constant radius. (5) Adjacent contours at each blade + lj are
The compressor according to claim 4, which is angularly displaced by approximately 130°. (6) Each of the east vanes has six contours, and the outer two have the same shape. and aligned (2) on the same axis. (2) The compressor of claim 5, wherein said impeller has a linear pitch velocity of substantially at least 200 feet per second. The compressor according to claim 6. (8) The compressor according to claim 1, wherein each of the impellers has three profiles, the outer two having the same shape and aligned on the same axis. Compressor. (9) The compressor of claim 1, wherein said impeller has a pitch linear velocity of substantially less than 200 feet per second.