US3061180A

US3061180A - Compressor

Info

Publication number: US3061180A
Application number: US66317A
Authority: US
Inventors: Harry E Durgin
Original assignee: Individual
Current assignee: Individual
Priority date: 1960-10-31
Filing date: 1960-10-31
Publication date: 1962-10-30
Anticipated expiration: 1979-10-30

Description

H. E. DURGIN Oct. 30, 1962 COMPRESSOR 5 Sheets-Sheet 1 Filed Oct. 51. 1960 INVENTOR. HARRY E. DONG/IV WWW V- PW.

ATTORNEY Oct. 30, 19 62 H. E. DURGIN 3,061,180

COMPRESSOR Filed Oct. 31, 1960 5 Sheets-Sheet 2 INVENTOR. HARM D 'Y I/V ff; WM

ATTORNEY H. E. DURGIN 3,061,180

Oct. 30, 1962 COMPRESSOR 5 Sheets-Sheet 3 Filed Oct. 51. 1960 INVENTOR. HARRY 5. D0 R IIV BY fim/fl PW ATTORNEY Oct. 30, 1962 Filed Oct. 31, 1960 H. E. DURGIN COMPRESSOR 5 Sheets-Sheet 4 HARM 5- D WW 7W IN VEN TOR.

URG/A/ ATTORNEY 5 Sheets-Sheet 5 INVENTOR.

ATTORNEY H. E. DURGIN COMPRESSOR Oct. 30, 1962 Filed Oct. 51, 1960 HARRY E. DURG/n/ BY MM Patented Oct. 30, 1962 3,061,180 COMPRESSGR Harry E. Durgin, East Hanover, NJ. (PMR Station Manager, P.0. Box 31, Naalehu, Hawaii) Filed Oct. 31, 1960, Ser. No. 66,317

Claims. (Cl. 230-444) My invention relates generally to compressors and specifically to rotary compressors.

It is among the objects of my invention to provide a rotary compressor which minimizes the frictional contact of rotating vanes and the grave lubrication problems which arise therefrom.

It is yet a further object of my invention to provide a compressor which operates efficiently with only approximate engagement of the rotating vanes, rather than exceedingly critical engagement of the rotating vanes.

It is yet a further object of my invention to provide a rotary compressor which is simple in form, easy to construct, durable, and highly efiicient.

These objects and advantages, 'as well as other objects and advantages may be achieved by the device shown by way of illustration in the drawings in which-- 7 FIGURE 1 is a view in perspective of the compressor with portions of the housing exploded away;

FIGURE 2 is a side elevational view of the eliptical drive gears;

FIGURE 3, diagrams 1 to 16 show the complete compression cycle;

FIGURE 4 is a perspective view showing the compressor housing with the walls partly exploded away;

FIGURE 5 is an end view of the housing showing the compressor valves and valve drives;

FTGURE 6 is a side view of the housing showing the compressor-valve drives;

FIGURE 7 is a top plan view of a valve passage;

FIGURE 8 is a top plan view of the valve ports in the housing;

FIGURE 9 is a side view of the valve plug;

FIGURE 10 is a front view of the valve plug;

FIGURE 11 is a horizontal sectional view of the valve plug in the valve passage;

FIGURE 12 is a vertical sectional View of the valve plug in the valve passage; and

FIGURE 13 is an end sectional view of the housing, valve passage and impeller.

Referring now to the drawings in detail, my compressor has a housing 21, which is generally tubular in shape. It defines a chamber having a uniform cross sectional area from end to end and having end walls 22 to enclose the ends of the chamber. The end walls each support a bearing 23 and the bearings carry a shaft 24 which extends at both ends outside the chamber. The shaft is tubular and contains solid second shaft 25. This second shaft is supported at its outer ends by second bearings 26. The first tubular shaft 24 is provided with diametrically opposed radial slots 27. The solid second shaft is provided with a radial impeller 28. The impeller 28 is a generally rectangular member extending through the radial slots 27 in the tubular first shaft 24. The impeller extends an equal distance out from the slot on both sides of the second shaft 25. The first shaft 24 is also provided with unitary radial impellers 29 which extend from the shaft in opposition to each other. The outer edges of the four ends of the

impellers

23, 28, 29, 29 all define the same circle upon rotation. The slots 27 in the first shaft 24 diverge outwardly so that the impellers 28 on the second shaft may approach or retreat from the impellers 29 on the first shaft 24. That is to say, the radial slots 27 in the first tubular shaft 24 are flared outwardly and are wider than the impeller 28 mounted on the second shaft 25 so that when the slot is stationary, the second shaft may nevertheless be moved around forward and backward. As a result, the space between the impeller 28 on the second shaft 25 and the impellers 29 on the first shaft 24 will define a space that will vary as to cubic content, dependent upon the position of the

impellers

28, 2 9 with respect to each other. The outer edges of the

impeilers

28, 29 are close to (.l") the inside of the chamher 2 1 so as to substantially seal the space on one side of the

impellers

23, 29 from the other. Also the side edges 30 of the

impellers

28, 29 likewise come close to (.1) the corresponding interior end walls of the housing 21 to complete the seal.

The housing 21 is provided with alternate intake 31 and discharge 32 ports disposed radially with respect to the axis of rotation of the shafts. These alternate discharge 32 ports and intake 31 ports are disposed at an angle of from each other. The admission of gaseous material into the housing through the intake 31 ports is governed by the valves which operate in timed relation to the

impellers

23, 29. The discharge of gaseous material from the housing 21 through the exhaust ports 32 is governed by the

valves

33, 34 which operate in timed relation to the

impellers

28, 29. Thus when the impellers 28,

29 subtend the intake port 31, the

intake valves

33, 33 are open. The increase in cubic capacity of the chamber defined between the

impellers

28, 29 opposite the intake port 31 reduces the pressure in the said chamber and the intake valve 33 being open, admits gaseous material. As soon as the

impellers

28, 29 which subtend the

intake ports

31, 31 have reached their maximum degree of volumetric expansion, the intake valves 33 close and the rotating

impellers

28, 29 begin to move so as to decrease the space between them. Any gas in the chamber defined by the

impellers

28, 29 is compressed. When the

impellers

28, 29 reach the discharge ports, the

discharge valves

34, 34 which have remained closed in timed relation to the impellers, are opened as the

impellers

28, 29 approach the point of maximum compression. That is to say, when the chamber defined between the impellers has attained its smallest cubic capacity, the

exhaust valves

34, 34 open, and the gaseous material, now compressed, escapes through the discharge ports 32. It will be seen that the compression cycles and the intake cycles proceed in pairs, in chambers from each other.

The first drive shaft 24 is supported at both ends by the bearings 23 mounted on the housing. A large gear 45 is mounted on the first drive shaft 24 and another large gear 44 is mounted on the inner drive shaft 25. Immediately adjacent to the inner and

outer drive shafts

25, 24 is a pair of coaxial

auxiliary drive shafts

35, 36. Each of these

drive shafts

35, 36 is supported bycentral bearings 37 and by a bearing 38 at their outer ends.

An elliptical gear 39 is mounted on the outer auxiliary drive shaft 35 and engaged with a corresponding elliptical gear 46] on a motor shaft 41. Each of the

auxiliary drive'shafts

35, 36 has a

regular gear

42, 43 mounted thereon and these gears engage the gears 44, 45 mounted on the inner or second shaft 25 and on the tubular shaft 24. The diameter of the

gears

42, 43 is one-half the diameter of the gears 44, 45, in order that each chamber shall twice expand and twice contract during each 360 rotation whereby there shall be two exhaust phases for each chamber during each 360 cycle. A regular gear 46 is mounted on the motor shaft 41 and this gear 46 engages the gear 43 on the shaft 36. The shaft 25 is caused to rotate at alternately faster and slower rates of speed by reason of the

elliptical gears

39, 40. Thus, the

impellers

28, 29 are driven at alternately slower and faster rates of speed with respect to each other and vary the cubic capacity of the chambers defined between them 3 in timed relation to the opening and closing of the

intake

33, 33 and

exhaust valves

34, 34. The motor shaft 41 is driven by a motor (not shown) and is supported by the bearings 44, 44.

The operation of my compressor is illustrated in FIG- URE 3. In diagram 1,

chambers

1 and 3 are in exhaust phase and

chambers

2 and 4 are in intake phase. Impellers A and B will be observed to define the

chambers

1 and 3, having small cubic capacity, and discharging the gaseous matter to be compressed. In diagram 2, impeller A has moved, but impeller B has moved considerably more, so that the

chambers

2 and 4 are decreasing in cubic capacity; simultaneously, the exhaust valves (not shown in these views) at the entrance to the exhaust ports xx have closed and the gaseous material is being compressed in the

chambers

2, 4. In diagram 3, impeller A has moved toward the intake ports yy and the

chambers

2 and 4 have nearly reached their minimum cubic capacity. In diagram 4,

chambers

2 and 4 have nearly reached the exhaust ports x-x, the exhaust valves have opened, the impeller B has reached its point of maximum deceleration with respect to A, and is just beginning to increase its speed. The maximum degree of compression has been attained and the compressed gaseous material is being vented through the exhaust ports x-x. In FIGURES 5, 6, 7 and 8, the chambers '1 and 3 are in compression phase as described above for

chambers

2 and 4. It is noted that with each pair of chambers taking in gaseous material, a corresponding pair of chambers is exhausting material. Views 9 to 16 need not be explained in detail for they merely show the

chambers

1 and 3 completing the remainder of the 360 cycle, going once more through intake to exhaust phase.

An illustration of volume and pressure capacity for a set of probable vane characteristics assuming elliptic gears for two compression phases for each cycle or shaft revolution:

Assume:

Vane dwell=l2 Vane lead=12 Vane length=L=8" Vane width=R=4 radius of compressor cylinder (4 compression cycles) (qrR L) 462 in. Pressure out- 905 p.s.1.) -20 p.s.1.

The major features of the compressor have been described. The secondary features of the compressor will now be described.

The housing is provided with 4 elongated shells 47 defining triple intake and exhaust passages. Each of the triple intake and exhaust passages 47 is divided into three sections by a pair of central fins 48 terminating at the segment of an arc which is a portion of the circle defining the external surface of the housing 21 as shown in FIGURE 13. The housing is provided with triple ports 31 as shown in FIGURE 8, coincident with the triple intake and exhaust passages 47. It is preferred that the impellers be sufiiciently thick as to cover completely each of the ports or slots 31. A rotatable plug or valve 33 closes the end of each passage. The end of each triple passage 47 is provided with a semi-circular valve slot 49 (see FIGURE 12). The valve 33 (see FIGURES 9 and 10) is pivotally mounted on an axle 50 and has a pair of semicircular discs 51 mounted on a closure plate 52. The plate 52 has the axle 50 for rotation. The semicircular 51 discs intimately engage the semicircular valve seats 49 in the passages 47. A spiral spring 53 is connected with each of the valve axles to normally urge the valves closed.

The other end of each valve axle has a finger 54 engaged with the end of a push-rod 55. The push-rod passes through a sleeve 56 and is provided with a camrider 57 or head on the opposite end. A spring 58 is carried by the push rod and inwardly urges the head into engagement with a rotary cam 59. The rotary cam is mounted for rotation with the impeller shaft 25. The cam is provided with four cam surfaces 60. Each cam surface 60 has a gradual slope terminating in an abrupt fall ofi or drop so that each valve is gradually moved, and abruptly restored to its original position as the riders 57 ride up and off the cam surfaces 60 when the rotary cam 59 turns with the shaft 25. Thus the intake and exhaust valves are operated in timed relation to the compression and decompression phases of the impellers.

The foregoing description is merely intended to illustrate an embodiment of the invention. The component parts have been shown and described. They each may have substitutes which may perform a substantially similar function; such substitutes may be known as proper substitutes for the said components and may have actually been known or invented before the present invention; these substitutes are contemplated as being within the scope of the appended claims, although they are not specifically catalogued herein.

What is claimed is:

1. A compressor comprising,

(a) a generally cylindrical housing closed at each end defining an operating chamber, the housing having intake and exhaust ports communicating with the chamber,

(b) a tubular outer shaft rotatably mounted in the housing extending coaxially through the chamber, the outer shaft having diametrically opposed, out wardly flaring radical slots,

(c) a pair of impellers mounted on the outer shaft within the chamber,

(d) an inner shaft mounted within the outer shaft and rotatable independently on the outer shaft, a portion of the inner shaft extending beyond the end of the outer shaft externally to the chamber,

(e) a pair of impellers mounted on the inner shaft within the chamber extending through the slots in the outer shaft, the slots being wider than the impellers extending therethrough,

(f) valves in each of the intake and exhaust ports,

(g) means engaged to the inner and outer shafts adapted to drive one shaft alternately faster and slower than the other shaft, whereby the impellers on one shaft periodically converge and diverge with respect to the impellers on the other shaft thereby periodically increasing and decreasing the volume of the space between the impellers and the housing, and

(h) means engaged to one shaft and operatively connected to each of the valves in the intake and exhaust ports adapted to periodically open and close said valves in timed relation to the volumetric expansion and contraction of the space between the impellers and the housing.

2. A compressor comprising,

(a) the structure in accordance with claim 1 in which the impellers extend toward close contact with the inside of the housing.

3. A compressor comprising,

(a) the structure in accordance with claim 1, and

(b) a cylindrical gear mounted on the end of the outer shaft externally to the chamber,

(0) a cylindrical gear mounted on the end of the inner shaft externally to the chamber,

(d) a first and second independently rotatable idler shaft,

(e) a cylindrical gear and an eliptical gear mounted on the first idler shaft, the cylindrical gear being engaged to the cylindrical gear on the inner shaft,

(1'') a cylindrical gear mounted on the second idler shaft engaged to the cylindrical gear on the outer shaft,

(g) a third rotatable shaft,

(h) an eliptical gear on the third shaft engaged to the eliptical gear on the first idler shaft, and

(i) a cylindrical gear on the third shaft engaged to the cylindrical gear on the second idler shaft.

4. A compressor comprising,

(a) the structure in accordance with claim 1 in which (b) the housing has a plurality of longitudinal slots communicating with the operating chamber, each slot being parallel to the end of the respective impellers, and defining intake and exhaust ports, and

(0) each impeller is wider than each of said slots in the housing.

5. A compressor comprising,

(a) the structure in accordance with claim 1 in which (b) the housing has a plurality of longitudinal slots communicating with the operating chamber, each slot being parallel to the end of the respective impellers, and defining intake and exhaust ports,

(c) each intake and exhaust port having a plurality of slots in the housing, each slot being narrower than the ends of the respective impellers,

(d) a conduit mounted on the housing over and communicating with each intake and exhaust port,

(e) a plurality of internal longitudinal dividing walls in each conduit defining passages parallel to and communicating with the respective slots, and

(f) said valves comprising a valve in the end of each conduit operatively connected to said means engaged to one of the rotating shafts for periodically opening and closing the valves in timed relation to the volumetric expansion and contraction of the space between the impellers and the housing.

References Cited in the file of this patent UNITED STATES PATENTS 88,215 Ruggles Mar. 23, 1869 719,969 Wood Feb. 3, 1903 726,353 Sainsevain Apr. 28, 1903 967,097 Woodward Aug. 9, 1910 1,370,548 Neebe Mar. 8, 1921 2,108,385 Murakami Feb. 15, 1938