SCREW ROTOR ASSEMBLY FOR SCREW COMPRESSOR OR THE LIKE

Abstract: A screw rotor assembly for a screw compressor or the like comprises a male screw rotor (1) and a female screw rotor (2) having rotor teeth each having a profile consisting of a plurality of special curves designed to reduce both the length of sealing line and the area of blow hole. The configurations of the male and female screw rotors (1,2) reduces the abrasion of the screw rotor assembly as well as the length of sealing line and the area of blow hole, so that the performance of the screw rotor assembly is improved. The length of sealing length and the area of blow hole in the screw rotor assembly of the present invention are about 10% and about 50%, respectively, of those of the conventional screw rotor assembly.

Description: The present invention relates to a screw rotor assembly for a screw compressor or a similar apparatus such as a vacuum pump or an expander. Description of the Prior Art Various profiles for screw rotors for screw compressors or the like have been proposed, for example, in Japanese Patent Laid-open Nos. 59-196988 and 61-190184, and Japanese Patent Publication No. 60-41238. A profile proposed in Japanese Patent Publication No. 60-41238 is shown in Fig. 12 by way of example. The profile is formed of a plurality of sectional curves. Fig. 12 shows the intermeshing portions of a male rotor 11 and a female rotor 12. A male rotor tooth 11a consists of sectional curves a-b, b-c, c-d, d-e, e-f and f-g successively arranged in that order from the leading side to the trailing side, and the female rotor tooth 12a consists of sectional curves A-B, B-C, C-D, D-E, E-F, F-G and G-H successively arranged in that order from the leading side to the trailing side. In Fig. 12, indicated at P M and P F are the respective pitch circles of the male rotor 11 and the female rotor 12, at A M and A F are the respective tip circles of the male rotor 11 and the female rotor 12, and at D M and D F are the respective root circles of the male rotor 11 and the female rotor 12. Generally, the performance of the profile of the screw rotor is dependent mostly on the length of sealing line and the area of blow hole, and the performance is improved as both the length of sealing line and the area of blow hole are reduced. However, since a portion of a conventional profile corresponding to the curve e-f of the male rotor tooth 11 a of the male rotor 11 is an arc of a circle, when either the length of the sealing or the area of blow hole is decreased, the other increases as indicated by a curve I in Figure 13, and hence it has been impossible to reduce both the length of sealing line and the area of blow hole. Furthermore, since a portion of the conventional profile corresponding to the curve C-E of the female rotor tooth 12 a of the female rotor 12 is formed of two curves respectively defined by two functions, the length of sealing line is increased inevitably. That is, the respective quadratic derivatives of those functions at the junction of the curves do not coincide with each other. Therefore, a line indicating the variation of the projected length ℓ of sealing line in the xy plane with the rotating angle ψ is bent at the junction, and thereby the length of sealing line is increased as indicated by a broken line I in Figure 7. According to the invention there is provided a screw rotor assembly comprising a male rotor having male rotor teeth each formed in a profile consisting of curves a-b, b-c, c-d, d-e, e-f and f-g, and a female rotor having female rotor teeth each formed in a profile consisting of curves A-B, B-C, C-D, D-E, E-F and F-G, wherein (a) the curve a-b is an arc of the root circle of the male rotor teeth with its center on the center O of the male rotor, (b) the curve b-c is a generated curve corresponding to the curve B-C of the female rotor tooth, (c) the curve c-d is a generated curve corresponding to the curve C-D of the female rotor tooth, (d) the curve A-B is an arc of the tip circle of the female rotor, (e) the curve B-C is an arc of a circle, (f) the curve D-E is a generated curve corresponding to the curve d-e of the male rotor, characterised in that (g) the curve d-e is a curve with its origin at a point O" on a straight line connecting the center O of the male rotor and the center O' of the female rotor and with a function at polar coordinate (r1,ϑ₁) r1 = R1 + R2 (ϑ₁/ϑ₃) n , osculating with the tip circle of the male rotor, where ϑ₁ is a variable, R2 < 0, |R2| > |R1|/2, 0 < ϑ₃ < 90, and 1 < n < 1.5, (h) the curve e-f is a generated curve corresponding to the curve E-F of the female rotor, (i) the curve f-g is an arc of a circle with its center on the pitch circle of the male rotor, osculating with the root circle of the male rotor, (j) the curve C-D is a curve with its origin at a pitch point O''' and with a function at polar coordinate (r2,ϑ₂) r2 = R + R3a(ϑ₂/ϑ₀) n /{b + (ϑ₂/ϑ₀) n }, osculating with the root circle of the female rotor, where ϑ₂ is a variable, a = ß(1 - α n ), b = α n (1 - ß)/(ß - α n ), and, when ß = 0.5, 0.7 ≦ α ≦ 0.85 and 2.5 ≦ n ≦ 3.5, (k) the curve E-F is a part of a hyperbola having the pole on a normal to the male rotor tooth at a point E, and (l) the curve F-G is an arc of a circle with its center on the pitch circle of the female rotor and osculating with the tip circle of the female rotor. The invention will now be described with reference to the accompanying drawings in which: FIGURE 1 is a diagram showing the respective profiles of the male and female rotors of a screw rotor assembly in a preferred embodiment according to the present invention; FIGURES 2 and 3 are graphs showing the relation between the length L of the sealing line in a portion formed of the curve d-e of the male rotor, and the area S of the blow hole; FIGURE 4 is a diagram of assistance in explaining the method of deciding the curve C-D of the female rotor of Figure 1; FIGURES 5 ad 6 are graphs showing the variations of a function f( ϑ ), and radius of curvature R for α; FIGURE 7 is a graph which represents a real sealing line length when the parameter α of a function f( ϑ ) is varied; FIGURES 8 and 9 are graphs showing the variation of the function f( ϑ ) and the radius of R with the angle ratio ϑ for n; FIGURE 10 is a graph showing the variation of the length L of sealing line in a portion formed of the curve C-D of the female rotor tooth with a for n; FIGURE 11 is a graph showing the variation of the length L of sealing line in a portion formed of the curve C-D of the female rotor tooth with n; FIGURE 12 is a diagram showing the respective profiles of the male and female rotors of a conventional screw rotor assembly; and FIGURE 13 is a graph showing the variation of the length L of sealing line with the area S of blow hole. Figure 1, similarly to Figure 12, shows only an intermeshing portion of a screw rotor assembly embodying the present invention. The screw rotor assembly comprises a male rotor 1 having male rotor teeth 1 a , and a female rotor 2 having female rotor teeth 2 a . The male rotor tooth 1 a consists of curves a-b, b-c, c-d, d-e, e-f and f-g successively arranged in that order from the leading side to the trailing side. The female rotor tooth 2 a consists of curves A-B, B-C, C-D, D-E, E-F and F-G successively arranged in that order from the leading side to the trailing side. The respective forms of the curves are as follows. (1) The curve a-b: An arc of the root circle D M of the male rotor teeth 1 a having its center on the center O of the male rotor 1. (2) The curve b-c: A generated curve corresponding to the curve BC of the female rotor tooth 2 a . (3) The curve c-d: A generated curve corresponding to the curve C-D of the female rotor tooth 2 a . (4) The curve d-e: A curve with its origin at a point O" on a straight line connecting the center O of the male rotor 1 and the center O' of the female rotor 2 and with a function at polar coordinate (r1,ϑ₁) r1 = R1 + R2(ϑ₁/ϑ₃) n , osculating with the tip circle A M of the male rotor, where ϑ₁ is a variable, R2 < 0, |R2| > |R1|/2, 0 < ϑ₃ < 90°, and 1 < n < 1.5. (5) The curve e-f: A generated curve corresponding to the curve E-F of the female rotor tooth 2 a . (6) The curve f-g: An arc of a circle with its center on the pitch circle P M of the male rotor 1, osculating the root circle D M of the male rotor 1. (7) The curve A-B: An arc of the tip circle A F of the female rotor 2. (8) The curve B-C: An arc of a circle. (9) The curve C-D: A curve with its origin at a pitch point O‴ and with a function at polar coordinate (r2,ϑ₂) r2 = R + R3a(ϑ₂/ϑ₀) n /{b + (ϑ₂/ϑ₀) n } osculating with the root circle D F of the female rotor 2, where ϑ₂ is a variable, a = ß(1 - α n )/(ß - α n ), b = α n (1 - ß)/(ß - α n ), and when ß = 0.5, 0.7 < a < 0.85, and 2.5 < n < 3.5. (10) The curve D-E: A generated curved corresponding to the curve d-e of the male rotor tooth 1 a . (11) The curve E-F: A part of a hyperbola having the pole on a normal to the tangent line to the male rotor tooth 1 a at a point E. (12) The curve F-G: An arc of a circle with its center on the pitch circle P F of the female rotor 2 and osculating with the tip circle A F of the female rotor 2. The curve d-e (equivalent to e-f in Figure 12) is expressed by a function other than that of a circle so that the length L of sealing line and the area S of blow hole are located within the shaded area demarcated by the curve I in Figure 13. Thus, the performance of the screw rotor assembly of the present invention is higher than that of the conventional screw rotor assembly. The dependence of the relation between the length L of sealing line and the area S of blow hole for R1, R2 and n are constants, and broken lines represent the relation between the length L of sealing line and the area S of blow hole in the conventional screw rotor assembly shown in Figure 12, in which the curve corresponding to the curve d-e is circular. As is obvious from Figures 2 and 3, the area S of blow hole of the screw rotor assembly of the present invention is reduced to approximately one-third of that of the conventional screw rotor assembly at the maximum for the same length L of sealing line. Such reduction in the areas S of blow hole is possible because the area S of blow hole decreases as the radius of curvature of the tip of the rotor teeth decreases, while the length L of sealing line decreases, since the radius of curvature increases when the sealing point is shifted away from the tip of the rotor teeth. Referring to Figure 4, the first position of a hypothetical point K on the pitch circle P F is decided taking the tooth thickness of the female rotor tooth 2 a into consideration. The form of the curve C-D is dependent on the selection of a curve connecting the point D and hypothetical point K. The R3 and ϑ₀ are parameters for deciding the hypothetical point K. ϑ₀ = ∠DO‴K R3 = O‴K - R The function of the curve C-D is represented as r₂ = R + R₃f( ϑ ). Since the function r₂ = R + R₃f( ϑ ) includes the point D and hypothetical point K, the function f( ϑ ) = a( ϑ ) n /(b + ( ϑ ) n ) must include points (0, 0) and (1, 1), when ϑ₂/ϑ₀ = ϑ . Suppose that a = ß(1-α n )/(ß - α n ) and b = α n (1 - ß)/(ß - α n ) to facilitate the decision of the form of the function f( ϑ ). Then, the function f( ϑ ) includes points (0, 0), (1, 1) and (α, ß). When ß is a fixed value, and α is varied between α1, α2 and α3 (α1 > α2 > α3) as shown in Figure 5, the variation of the radius of curvature R of the curve D-K with the angle ratio ϑ for α in the configuration shown in Figure 4 is indicated by curves shown in Figure 6. Consequently, as shown in Figure 7, the projected length ℓ of sealing line in the xy plane varies with the rotating angle ψ along a substantially linear curve when α = α2, and along respective arcs of circles when α = α1 and α = α3. Since ℓ is substantially fixed regardless of α, the length of sealing line decreases as the curve approaches a straight line. Since a shorter sealing line is desirable, it is undesirable that a is excessively large or excessively small when f( ϑ ) - ß, because excessively large α and excessively small a increases the length of sealing line. As is obvious from Figures 8 and 9, the effect of on the variation of f( ϑ ) and the radius of curvature R with ϑ is similar to that of α. When O'D / O"O ‴ = 0.6 and ξ = 30° in Figure 4, the variation of the length L of sealing line with a for n is indicated by curves shown in Figure 10, and the variation of the length L with n is indicated by a curve shown in Figure 11. When ß = 0.5, α in the range of 0.7 to 0.85 gives a minimum length of L of sealing line, and hence it is preferably to define a and b by such values of α and ß. Preferably values for n are in the range of 2.5 to 3.5. In Figures 10 and 11, LB on the vertical axes indicates the length of sealing line in the conventional screw rotor assembly. The length L of sealing line of the screw rotor assembly of the present invention is shorter than that of the conventional screw rotor assembly by approximately 15%. As apparent from the foregoing description, since the male rotor teeth and female rotor teeth of the screw rotor assembly according to the present invention are formed respectively in the above-mentioned curvilinear forms a-b-c-d-e-f-g and A-B-C-D--F-G, the curve d-e reduces the length of sealing line and the area of blow hole, and the curves B-C-D-E reduce the length of sealing line. For example, the length of sealing line and the area of blow hole in the screw rotor assembly of the present invention are about 10% and 50% of those in the conventional screw rotor assembly shown in Figure 12, respectively. Thus, the present invention provides improved profiles for the male and female rotor teeth of the screw rotor assembly.

Claims: A screw rotor assembly for a screw compressor or the like, comprising: a male rotor having male rotor teeth each formed in a profile consisting of curves a-b, b-c, c-d, d-e, e-f and f-g; and a female rotor having female rotor teeth each formed in a profile consisting of curves A-B, B-C, C-D, D-E, E-F and F-G; wherein (a) the curve a-b is an arc of the root circle of the male rotor teeth with its center on the center O of the male rotor, (b) the curve b-c is a generated curve corresponding to the curve B-C of the female rotor tooth, (c) the curve c-d is a generated curve corresponding to the curve C-D of the female rotor tooth, (d) the curve A-B is an arc of the tip circle of the female rotor, (e) the curve B-C is an arc of a circle, (f) the curve D-E is a generated curve corresponding to the curve d-e of the male rotor, characterised in that (g) the curve d-e is a curve with its origin at a point O" on a straight line connecting the center O of the male rotor and the center O' of the female rotor and with a function at polar coordinate (r1,ϑ₁) r1 = R1 + R2 (ϑ₁/ϑ₃) n , osculating with the tip circle of the male rotor, where ϑ₁ is a variable, R2 < 0, |R2| > |R1|/2, 0 < ϑ₃ < 90°, and 1 < n < 1.5, (h) the curve e-f is a generated curve corresponding to the curve E-F of the female rotor, (i) the curve f-g is an arc of a circle with its center on the pitch circle of the male rotor, osculating with the root circle of the male rotor, (j) the curve C-D is a curve with its origin at a pitch point O‴ and with a function at polar coordinate (r2,ϑ₂) r2 = R + R3a(ϑ₂/ϑ₀)n/{b + (ϑ₂/ϑ₀) n }, osculating with the root circle of the female rotor, where ϑ₂ is a variable, a = ß(1 - α n ), b = α n (1 - ß)/(ß - α n ), and, when ß = 0.5, 0.7 ≦ α ≦ 0.85 and 2.5 ≦ n ≦ 3.5, (k) the curve E-F is a part of a hyperbola having the pole on a normal to the male rotor tooth at a point E, and (l) the curve F-G is an arc of a circle with its center on the pitch circle of the female rotor and osculating with the tip circle of the female rotor.

Inventors: YOSHIMURA, SHOJI
Applicants: KABUSHIKI KAISHA KOBE SEIKO SHO
Application year: 1988
Main classification: F04C18
IPC codes: F04C18