JPS58174102A - Rotary hydraulic machinery - Google Patents

Abstract

PURPOSE:To permit the smooth operation of the captioned hydraulic machinery in sliding vane type by forming a cylinder to which a vane is slidably attached, into the form obtained from a specific equation, thus reducing the variation rate of the amount of projection of each vane into a back-pressure chamber. CONSTITUTION:A rotor case 4, namely the inner peripheral surface A of a cylinder is formed into the shape obtained from a specific equation. As a result, the amount of projection of each vane 71-74 into a cylinder 4, namely the variation rate of the sum of the amount of projection into a back-pressure chamber 62 always becomes zero. Therefore, the pressure variation in the back-pressure chamber 62 becomes zero, and each frictional force generated between vanes 71-74 and the cylinder 4 is reduced. Further, the acceleration which is generated on each of vanes 71-74 is also smoothly varied.

Description

[Detailed description of the invention]

The present invention relates to sliding vane type one-turn fluid machines such as refrigerant compressors and hydraulic pumps. An example of a conventional sliding compressor for vehicle air conditioning and refrigeration is the iWA iWA. As shown in the second IllK 5, the compressed structure is such that one end is
:: It consists of a compressor assembly (2) inside the housing (1), a front casing (3) that fixes the opening of the housing (1), and the compressor assembly (the , a rotor case (4) whose inner circumference is approximately elliptical and whose outer circumference is approximately cylindrical; a front guide block (6) and a rear guide block (5) attached to both front and rear ends of the rotor case; Two independent crescent-shaped cylinder chambers (50-1) (<5O-2) are formed by the rotor (8)K. ) K advance/retreat possible Kk-/
(7-1). (7-4), (7-3), and (7-4) are interposed, and the rotor (8) is rotatably supported by the front guide block (6) and the rear guide block (57. cylinder chambers (50-1), (50-2)
is the vane (7-1). (7-2), (7-3), (7-4) K J
') And then Komuro (151-1). (51-4), (51-3), (51-4) K divided, small rooms (51-1>, (51-4), (51-3)
, (51-4) gradually increases and decreases as the W-taper (8) rotates, sucking and compressing the refrigerant gas. Evaporator etc. not shown! ') Suction fitting (52) It is divided into two intermittent large passageways (Sito1) and (54-2) provided, and two cylinders III (so-t) and (50- 2)
VC suction ports (55-1) and (55
-2), two cylinder chambers (50-1), (5
0-2) K is supplied. Cylinder chamber (50-1), (
50-2) to Vane (7-1), (7-2), (7-3
)-(7-4)KJ') A small chamber (51-1) formed by being divided. (51-2), (51-3), and (51-4) are suction bows when the volume increases due to one rotation of the rotor (8).
(55-1). (55-2) Inhales refrigerant gas, and its volume decreases. Compresses refrigerant gas from K, and discharges it) (1
0-1), (10-2) from the discharge valve (11-1),
(11-2) is pushed up to open the cylinder chamber (50-1),
(5G-4) 6 cylinders m (5G-
1), (So-2)! The re-discharged high-pressure refrigerant gas passes through an oil separator (13) provided on the rear guide block (5), where the refrigerant gas and oil are separated, and the high-pressure refrigerant gas passes through the discharge fitting (12). ) is sent to a condenser, etc. (not shown) outside the compressor. Also, the bottom part of the housing (1) is SRSG. The pressure is reduced through the oil hole (@l) of the tour guide V printer 5) and the vane back pressure m1 (62)K is led to -1 (7-1).
). Press K to apply hydraulic pressure to the back of (7-2), (7-3), and (7-4).

[There is. In the J5 rotary compressor mentioned above, when the rotor (8) is rotated, the vanes (7-1), <7-2), (
7-3). <7-4) is pressed against the inner surface of the rotor case (4) by the centrifugal force and the hydraulic pressure of the vane back pressure chamber (62), and frictional power is consumed between the tip of the inner rotor case and the rotor case. As stated in eIcK, this changes depending on the -turn angle of 1-ta (8). Here, each vane (7-1) is inserted into the vane back pressure chamber (62).
). The pop-up children (7-2), (7-3), and (7-4) are
It is determined by the inner circumferential shape of the rotor case (4 (hereinafter referred to as Schilling's white horse W shape), the vane tip shape, the amount of vane offset, etc.), and each vane (7-1). (7-2), (7-3) ), (7-4) protrusion amount is
The rotor changes as it rotates. Furthermore, the change in pressure within the back pressure column corresponds to the change in volume, which is equal to one in each case (7-1), (7-2). Corresponds to the change in the sum of the protrusion amounts into the vane back pressure chamber (62) of (7-3) and (7-4). In other words, for example, when a certain vane tries to protrude into the vane back pressure chamber, k- The volume of the back pressure chamber decreases and the pressure increases, which acts to press against the inner peripheral surface of the rotor case, thus generating a large frictional force. Vane back pressure amount (62) Each vane (7-1), (7
-2). (7-3), (7-4) change in protrusion amount,
As illustrated in FIG. 6, each vane (7-1),
The amount of protrusion of (7-3) and horns (7-2) and (7-4) into the back pressure chamber (62) is shown in Figure 6 -IaA
, B, which is twice the sum of -lines A and B, that is, the total sum of the protrusion amounts of each vane, as shown by line C. The change in this - line C (with respect to one rotor rotation angle) corresponds to the pressure change in the vane back pressure chamber (62), and in the part A, the pressure in the vane back pressure chamber (62) increases and a large frictional force Conversely, if the pressure in the vane back pressure chamber decreases at the mouth, and the force due to this pressure change is greater than the centrifugal force of the vane, the vane may separate from the inside of the rotor case. 15) This movement of the vanes is clearly explained by the above explanation.
It is greatly influenced by the shape of the cylinder or vane. Here, in order to compare the magnitude of the change in the sum of the amount of protrusion of each vane into the R-back pressure chamber, the rate of change 4k of the vane protrusion shelf is defined as follows. However, Aha-< - Rate of change of the vane pop-out shelf s: Number of vanes □ #24-tar rotation angle Therefore, if the change rate of the vane pop-out shelf is large, (1) When the vane pop-out shelf IAI is large; Since there is incompressible oil in the vane back pressure chamber, each vane is strongly pressed against the inner periphery of the rotor case, generating a large amount of frictional power, which in turn leads to an increase in the power required for the compressor. Furthermore, since an abnormally large force is applied to the vanes, a certain amount of wear occurs. (2) On the other hand, the spring pop-out shelf Σ and #) is small.
In the vicinity of -1, the -n may separate from the inner surface of the rotor case, and proper suction and compression may not be possible. (3) Furthermore, since the large and small positions of ΣA* (#) are determined by the rotor rotation angle -1, only certain parts of the rotor case wear out, and the cylinder, which had a smooth shape, eventually becomes wavy. As a result, the wind becomes chattering, and when chattering occurs, proper compression and compression cannot be performed. (4) Since the frictional power of the rotor case varies greatly with the amplitude of the rotor, the movement of the compressor can be increased. This results in major drawbacks such as: In addition, the shape of the inner circumferential surface of a conventional rotor case, that is, the shape of the inner circumferential surface of a sill, is, for example, as shown in No. 4-.
It is OK to connect the arcs of four needles, but in this case, the rate of change of the protruding shelf of each vane can be made as small as 5 to 6411 degrees. Although it can be seen, it is actually much larger than that, at Kt$
The current situation is that it is as high as 15-16%, and the above (
It has the following drawbacks as shown in (1) to (4), and the frictional power increases by 1%, and the above-mentioned drawbacks are common to i-transformer compressors. j! In the rotary compression Il&C as described above. Rotor (if you turn the light one time, vane (7-1), (7-2
). (7-3) and (7-4) are centrifugal force and vane back pressure chamber (
62) is pressed against the inner surface of the rotor case (4) and moves along the inner surface of the rotor case (4). In the conventional cylinder shape formed by
As shown in Figure 5, the acceleration acting on each vane suddenly changes from + to - or from - to 10 at a certain rotor rotation angle position, causing a so-called skip phenomenon. (Figure 5 shows 71 pieces of E.) Due to the movement of the vane, if a 5μ skip occurs as described above, the direction and magnitude of the force acting on the vane will similarly change suddenly and skip, so the following will occur. disadvantages may occur. (a) The vanes move so that they touch the inner surface of the rotor case, and the tracking performance of the vanes is poor, causing the vanes to separate from the rotor case and make it impossible to perform good suction and compression.
Because the vane is pressed against the inner surface of the rotor case with a sudden force, the frictional force between the vane and the rotor case becomes abnormally large. As a result, a large amount of power consumption is required. (b) In addition, since the acceleration skip position is determined by the rotor rotation angle, wear progresses at a specific position on the inner surface of the rotor case, and the cylinder, which had a smooth shape, eventually becomes wavy. As a means to solve the above-mentioned drawbacks such as the vane causing chatter cylinder, the inventors previously proposed a cylinder shape shown in detail in Application No. 100437/1983. However, in % Application No. 100457/1983. lQk! It has the characteristic that the displacement, volume-line, and compression curve of the compressor are determined by determining the value of FIG. Figure 6 of this application shows examples of volume curves and compression curves,
FIG. 6 corresponds to the conventional structure shown in FIGS. 1 and 2, and shows curves a, 4. c, d are small ijL (5
1-1) Volume fk indication such as *ai, 13. a, I)
shows pressure changes corresponding to volume lines m, h, e, and d. Here, one factor governing the performance of the compressor is the small 1i1 ((51-1) and (51-2) in Figure 2).
etc.), and this depends on the threshold pressure 1ji and the size of the minute gap between the members forming the small chamber, and the compression-summary in Figure 116 ,
From B and O, leakage occurs to the adjacent room as indicated by the arrow 5 in the figure. (Please note that the small chambers ((5-1) etc.) are back pressure chambers (62).
However, leakage may occur between the compressor and compressor performance.
The explanation thereof will be omitted here. ) Therefore, reduce such leakage pressure! In order to improve Li machine performance, it is necessary to obtain a good compression curve and thus a good volume curve. In the above explanation, an example was shown in which the number of vanes was 4, but if the number of vanes was 3.4°...
..., the pitch of the compression curved edge, that is, the volume curve changes depending on the number of vanes, so superposition is used to obtain a volume curve adapted to each number of vanes. Furthermore, it is superposition to obtain a volume #A line adapted to each operating condition or application of the fluid machine. On the other hand, the size of the compressor rotor case (cylinder) is
This determines the size of the compressor, but Patent Application No. 185
In No. 6-100437, the shape of the cylinder 4 is determined by determining the radius of the 4-metal radius and the machining distance 5 in the same diagram. It was something that would end up happening. As mentioned above, the cylinder shape of Japanese Patent Application No. 100437/1987 provides a much better fluid machine than the conventional one, but it has the following problems. (1) From the point of view of leakage, which controls compressor performance, the compression curve and hence the volume l! l1ii is 1, which means that when changing the number of vanes, it is desirable to obtain a curve corresponding to the number of vanes, and it is also desirable to obtain a curve corresponding to the operating conditions of the machine or each application. However, this modification cannot be made in Japanese Patent Application No. 56-10041. (2) If the size of the compressor is the same, it is desirable that the displacement be larger (if the displacement is the same, the magnitude of compression is smaller). ), but in Japanese Patent Application No. 56-100437, the amount of displacement (per unit length of the rotor) is determined by the rotor radii a and h. For example, if you want to slightly increase the displacement, it is necessary to slightly increase the length of the rotor case or change the rotor radius or k. This results in a slightly larger value. On the other hand, if the compressor is to be displaced by a slightly smaller compressor, the size of the compressor itself becomes slightly smaller, contrary to the above. In other words, when manufacturing a compressor, if a series is developed, the size of the parts (rotor case) will differ slightly depending on the slight change in electric displacement, and as a result, the size of the compressor will differ slightly. There is a certain inconvenience. The present invention is based on the following objectives (II is tall, and the following (2+(3)
1 (Aimed at Section 41.) (1) A rotary fluid machine that eliminates the above-mentioned drawbacks of conventional machines, which is housed in a rotor groove so that it can move forward and backward, and whose proximal end surface is connected to a common A sliding vane type rotary fluid machine is constructed in which a plurality of vanes facing the back pressure chamber and having their tips in contact with the inner circumferential surface of the cylinder are moved forward and backward within the groove by the rotation of the rotor. O-°
The vane is characterized in that it is configured in the shape of an inner circumferential surface of a cylinder such that the rate of change in the sum of protruding amounts of the proximal end surface portions of the vanes protruding into the back pressure chamber is equal to or less than - cent. The purpose of the circle is to reduce the rate of change in the sum of the protrusion amounts of each vane protruding into the back pressure chamber, reduce power consumption, wear of the vanes and the inside of the cylinder, etc.
(2) When the vane moves along the inner surface of the rotor case, the acceleration acting on the vane changes continuously and smoothly.
The sliding vane type single-turning fluid system improves followability of vane motion, prevents chattering, and reduces wear on the inner circumferential surfaces of the vanes and rotor case (cylinder), allowing smooth and good operation. Kagome 9 provides machines (3) Any number of vanes or machine operating conditions;
Depending on the application, etc., we set a cylinder shape that is suitable for each,
The purpose of this K is to bring out good performance of rotary fluid machines. The purpose is to be able to change the displacement of 5KL, and to obtain a displacement that matches the conditions and applications in which the machine is used. Embodiments of the present invention will be described below with reference to the drawings. The present invention relates to a sliding vane type rotary fluid machine, specifically a rotor (8
) is transparently housed in #I (code omitted) of the rotor case (4), with the proximal end facing the common back pressure chamber (62) K, and the tip facing the inner circumferential surface of the rotor case (4) (Figure A-82) K. A plurality of pins (7-1), (7-2) formed by sliding contact. In a sliding vane compressor configured to advance and retreat into the groove by the rotation of the rotor (8), each peg 7 protruding into the back wealth (62)
(7-1), (7-2),... groups 111N1ms(
B-2 Figure) f) Rate of change of the sum of protrusion amounts 4k (Refer to formula 13 above) is intended to be made as small as possible @9. It is intended to change K smoothly and continuously without sudden changes.It is also intended to provide performance that is adapted to the number of vanes of the fluid machine, the operating conditions under which the machine is operated, and the purpose of the machine. It is intended that the displacement of the machine can be changed without changing the size of the machine.
It is intended that The embodiment of the present invention focuses on the rotor that is most related to the occurrence of the rate of change h, performance in terms of vane acceleration, number of vanes, machine operating conditions, application, etc., and machine displacement. The shape of the case (4) (that is, the inner peripheral body of the cylinder) is configured as follows. That is, as shown in 1M78, when expressed in g-y coordinates of the shape of the inner circumference (color) of the cylinder, the shape (z (#), y (#)) of the inner circumference (ml) of the cylinder is formed by the following formula. There is. Note that here, the Een thickness was set to 0. However, (see FIG. 7), the protrusion amount l(#) of the vane into the cylinder is determined by the following equation (4) or (4)1. X[(C1strL(me) publication)(C,cOy(2mθ
)+1)X (cap (me)+1)C engineering]
・・・・・・・・・(4)x [(011is(-
)+1) (C3cap (2”#)+1)X
(cat (lll#)+cap (IILλ))
”] −−−−−−1−(4)′Furthermore, α in the above formula is based on the following formula, α=11g−1d/a ・・・・・・・・・・・・・・・
・・・・・・−・(5) However, -2 rotor rotation angle (2 rammeters representing the position of the vane); rotor radius (radius of the circle inscribed in the cylinder) d: vane offset amount and cylinder inner circumference Difference between major axis of surface and rotor radius a,, a
,, a3: Constant m Number of contact points between cylinder and rotor (number of cylinder chambers) λ:
The angle of the G land portion The cylinder shape is determined by the equations (3), (4), and (5), or as will be explained in detail later, the (CeI (expletive) +
1)C! b b i+1111 E (4Y formula l) (
cap (mill) +coz (m2))c
” [, High 11 & ((2-θn, 1isllI number of (31su, -) based on (Otori-), caz yHBt
The above-mentioned protrusion amount formed by multiplying c by a certain constant and adding 1 to it by at least one coefficient! (
The cylinder shape is determined by the negative number of θ), and the rate of change in the amount of protrusion of the vane into the back pressure chamber is approximately zero. To elaborate further. In the assembled formula (4), the constants a, , a, , a, C1; Q,
=xQ. Assuming C, tsu1, 1(-) becomes the following equation, which means equation (4) of the previous invention (Japanese Patent Application No. 56-100457). ! (θ) 2 pieces (cot (me) + 1t...
...(6)-Here, to simplify the explanation, the (4th
) For each constant a, , C2, G3 in the formula, the following 3
We will show two cases. 1) When G2=1 and c3=o, Equation (4) Eli C2:1, and when G3=0, l(
#)+1 O! (θl=, (Q1zt path (isthmus +1) (COjC-)
+11... (7) Here, since it is necessary that the vanes protrude from the rotor, l(θ) ≧0 is a necessary condition, and therefore, tc, t≦1 are required. There is. Furthermore, when the fringe equation (7) is expanded, the equation (7) becomes the following equation. According to the cylinder shape formed by the above-mentioned formula II (3), formula (7), and formula (5), any rotor rotation angle #
In this fluid machine, the amount of protrusion of each vane into the cylinder is 14m>, lCe+-8!, since the vanes are installed at equal pitches in this fluid machine. ! -), Bg+>,...s
s, that is, l(#+(i-1)P-). However, i=x, 2. ...Island S: Depending on the number of vanes, the shelf that protrudes from each vane into the cylinder is determined by the formula (
7) From 'Σ j (#+(1-1)L-) 小-1蕗+C11锵-+(i-1) 小) + cap (me + (i-1) ''-!!-)
Le + 13 = 11 ・・・・・・・−・ Constant ・・・
・・・・・・・・・(8) ml However, ■=T-, l,, ・・・・excluding”,
°J product (2πmm) = O from = 0 just 6, -1 □, 2,3010. Le H + □ excluding - From JP product (2 lectures) = 0, Σcoz (ㅝ θ 0 (i-1) - 7Kwh. No. -1 Le; 0, but - = 1.2.3...) Excluding Le 1.11 Product (πm) = 0, that is, *(7) 5 fC, csI (m#),
pin(wlj) and their harmonics (2i1θ':
3m#, 4ml,...), the sum of the vane protrusion amounts is constant. As mentioned in 5 above, since the protruding shelf of each vane to the ring is constant, conversely, the back pressure of each vane ii (62
) is also constant. Therefore, by adopting the cylinder inner peripheral surface shape of the present invention, the rate of change in the amount of protrusion of the vane into the back pressure chamber (62) A (Equation (1)) is 4 times KO. An example of the cylinder shape formed by the above equations (3), (7)', and (5) is #! 8 shows the volume curve and the compression curved edge in FIG. 9, and the broken lines in FIGS. Example 17 is based on the present invention. In the same figure, the CI of formula (7) 1 shows the case where Q1=α4. As shown in the figure, the cylinder shape of the JIIaWJ Yen line of the present invention is on the suction side (C) compared to the previous invention indicated by the broken line in Figure 1118.
At this point, the cylinder goes thin, and conversely, at the discharge side (d), it goes down, leading to lead 9 (note that if the value of C□ is negative, this will be reversed), and this difference differs depending on the value of C1. It is clear that it is something. Therefore, in the cylinder shape as described above, its volume curve and compression line as shown in FIG. II! It is clear that the slope of 1 m becomes steep (on the contrary, it becomes gentle when Yt and C1 are negative), and this differs depending on the value of C1. Furthermore, the acceleration of the vane when the cylinder shape of the present invention shown in FIG. 8 is used is shown in FIG. 10, corresponding to FIG. 5, and from this, the vane acceleration according to the present invention is It can be seen that it changes continuously and clearly without skipping. As is well known, under such conditions, the radius of the curve (that is, the shape of the cylinder) changes continuously. That is,
That lil & 1m contraction! 1 (evolute) is continuous, and the cylinder shape of the present invention satisfies this and C
- This is for the purpose of I) When c1=o, c,=o From equation 14), when OH"= Oe 03 = 0, K becomes as follows, 1 (#I=k ・"-(cap (凰り◆") )”
・−4・−(9) C2 Expanding the above formula, the following formula becomes O C, (C, −1)−・(C, −r〇, ・・+
co/(ia#)+...)r! ......(9)' However, r=L2sa... Cocote, coo" (wna) +! (*#) woj
li book J knee”t b (111#) harmonic ca
t(cat(wrsu, cap(2311, cap
It is expressed as the sum of (3wh,...). Therefore, as mentioned above, the sum of the protrusion amounts of the vanes is I
N (7) is always constant like the formula 7. Figure 11 shows an example of the cylinder shape formed by the above formula (3), the iris (both formula), and the K (51 formula). and pressure-tight are shown in FIG. 12, and the dashed lines in FIGS. 11 and 12 indicate formulas (3), (6), and (5) according to the previous invention, The solid line is from the main departure @.The same figure shows the case where C3=2.
Compared to K, in the present invention, the suction side (C) and application II
(=) makes me look thinner. As can be seen from the volume curve shown in FIG. 11, the cylinder shape (solid line) of the present invention reduces the maximum volume, and as a result, the displacement of the machine becomes smaller. Although not shown here, it is clear from the above explanation that the acceleration generated in the vane smoothly changes continuously without skipping as the 10-tar rotates, as in the case 1) shown in FIG. 10. (It is clear that the evolution route is continuous.) ■) When a1=O, C221 From equation (4), when Q1=Q, Q, and =i, l(#) becomes -, Here, since l(θ1≧00, IC1l≦1-wheel type with respect to 17 is as follows. +(,C,+1) coJP(m#) +1)
``i(1', !(#) is c based on (m)
The harmonics of the ap function (can(m, cap(2wne)
) , -) f) Sum J:, Since it is expressed as ``C'', the sum of K and the amount of protrusion of the vane is exactly constant as shown in equation (7). FIG. 16 shows an example of the cylinder shape formed by Equation I, Equation I, and Equation (5), and FIG. 14 shows the volume curve and compression line, and the broken lines in FIGS. 13 and 14 are , formula (3), formula (6), and formula (5) according to the previous invention, and the solid line is according to the present invention. 1g131iiKyyfX 5 K, 1jllEl broken 1
i11) Compared to the previous FJAIIC, the one of the present invention has a sudden stop on the suction lI (c) and discharge side (d).
Note that if the value of C1 is set to a negative value -f, the weight can be reduced), but this changes depending on the value of C1. As can be seen from the cylinder shape shown in Fig. 16 and the volume line in Fig. 14, when the cylinder shape K of the present invention is adopted, the maximum volume increases (C, >0), and as a result, the displacement of the machine increases. Furthermore, the acceleration that occurs all at once (not shown) does not skip (changes continuously and smoothly) with the rotor rotation angle, as in the case 1) shown in FIG. 10. are the constants c, , c, , c, K in equation (4)
So, 1). Three cases are shown: 1) and 1il). These results are also b off! The function of (θ) is (WXa
) based harmonics ((2111#), (311#)
It is expressed as the addition of the 1?1j7 function and the ztn function of 1#), -), and as a result, the sum of the protrusion amounts of R-n is always (constant).Here, the (4th ) is characterized by cases l), i),
K, (co
JP(III +11) Multiply the coefficient that changes with the function Kt or as a power (Ca#(m#)+
The purpose is to correct and incorporate 1). Therefore, given as equation (4), t<or,)r-sI),1),
1) If G1゜021CB has each value in j9 size rule j5, the multiplication of Kzgn and cH can be expressed as the sum of these harmonics as shown below.
As a result, harmonics (2 proverbs) based on (m), (3
1111) - Its @ number and addition of Cal function 0 Ca car)X cmQ = -cap (α-β) +
T cap (α + β) JPt happy) XJF lecture = -c
ap (α−β) −7F cy (α+β)tsp
)Xcozip = upper pin (α+βn12Ejs(
α−β) Therefore, as a result, Equation (3), Equation (4),
The sum of the vane protrusions il, ,') for the cylinder shape shown in equation (5) is constant as the value increases. It should be noted that the acceleration of the cylinder shape according to the above changes continuously and smoothly without skipping, as in cases I), l), and l). Therefore, according to the embodiment of the present invention, the above! 51'
, l'-n into the cylinder is always constant, and conversely, the amount of protrusion of each vane into the back pressure 1i1 (62) is also constant. Therefore, by adopting the cylinder inner peripheral surface shape of the present invention, the change rate of the protrusion amount to the vane back pressure 1i1 (62) k (Equation (1)) % Expression % aW! In the embodiment A, the shape within the inner circumferential surface of the cylinder is formed by the above equation as shown in FIG. 7, so
C), and the problem when the change *jh is large can be solved. That is, the inner circumferential surface of the cylinder (which is made of Al)
Therefore, the pressure fluctuation (hydraulic fluctuation) within the back pressure 1il (62) of the vane becomes O.
0437), (Al cylinder circumference yC-<-n is no longer pressed strongly, and the abnormal increase in frictional power that occurs between -1 and the cylinder is eliminated.Also, with the conventional one, almost - An abnormally large force was applied to the vane, causing wear on the vane, but in this example, such abnormal force does not cause vane wear. This phenomenon no longer occurs, and proper suction and compression can be obtained. (Since the pressure inside the back pressure chamber is constant at all rotation angles of the C1 rotor, only a certain part of the cylinder will not wear out.) Regular K Proper 7a: It is possible to obtain a straight movement. During rotor rotation, the frictional force generated by the back pressure inside the cylinder 1 and cylinder 1 does not fluctuate, so the torque fluctuation of the compressor is greatly reduced. In the case of the cylinder shape according to equation (41, (5)), the acceleration acting on the vane does not fluctuate (it changes continuously and smoothly). ...), for this reason.@ The followability of the blade becomes very good, and the problem of the blade being separated from the inner circumferential direction of the rotor case and not being able to perform good suction and compression is eliminated.Also. On the other hand, by being pressed against the inner circumferential direction of the rotor case with a sudden force, the frictional force between the rotor case and the vane becomes abnormally large, eliminating the need for large power consumption. (g) Acceleration is skipped. Since the vane movement changes continuously without any deviation, good vane motion occurs over the entire inner circumferential surface of the rotor case, eliminating chattering of the vanes and achieving good suction and compression. By using the cylinder shape according to equation (41, 15), the compression line can be changed as described in case 1). Compression suitable for each machine depending on operating conditions, usage, etc.
It has the very great feature that the line can be determined while maintaining the above-mentioned advantages (A, 1 to V). In addition, according to the present invention, while having the very excellent characteristics of the above-mentioned cases i) and c) K, as shown in the example, the rotor radii a and 5 are not changed, i.e. , the machine's volume curve and maximum volume can be changed without changing the size of the machine, and the displacement can be changed without changing the size of the machine. Furthermore, to explain specific examples of the present invention, (1)
In the above embodiment, the shape of the inner circumferential surface (A) of the cylinder was given using the theoretical formula aIPi, but this would result in machining errors when actually manufacturing the product. The machining error is ±Q, 06~± in the normal direction with respect to the theoretical value of the above example, taking into account the current machining method based on mass production (for example, NO@, cam polisher, etc.) Q.05
■Below the level. This addition difference is a value sufficient to sufficiently reduce the rate of change k intended in this embodiment. In practice, the theoretical value of the example ±[1,08 ~ ±α11111
This is within a sufficiently tolerable range. Expressing this using the short diameter of the cylinder (rotor diameter) = 2a, the machining error is less than 1 ± (500 to 700) In the above embodiment, an example was shown in which the thickness of the blade = 0, but in reality, the blade has a thickness, and when considering the thickness t of the blade, 11c is expressed as the following equation. In other words, the inner circumferential surface of the cylinder (the shape of Al is expressed in ty coordinates as shown in Fig. 1115), and the equation K (5)' is used instead of the equation (5). ( ! = pin-' (snoring μm, song...
...(5) HatakeInstead of equation (5), K Since the point of contact P between the inner surface of the cylinder and the inside surface of the cylinder changes by degrees Celsius depending on the rotation angle of the rotor, the rate of change of the heavy phase when the engine jumps into the actual back pressure chamber is 4 m (Equation 1)
is not O, but has some value, but in practice Δ
The problem has been reduced to the point where it is no longer a problem. (3) Furthermore, in the above embodiments and conventional examples, the shape within the inner peripheral surface of the cylinder was expressed by equation (3) or by connecting a total of four circular arcs, but in the processing of the cylinder, the following It may take a certain shape. That is, as shown in FIG. 16, in order to improve the machining accuracy (only the vicinity of the minor axis of the shape of the inner circumferential surface of the cylinder is sometimes made into a circular arc. This circular arc portion is called the G land.
Since the accuracy in the 271 part does not greatly affect the performance of the compressor, it is made into a circular arc to increase the machining angle of this part. "One of the 16th Evil" indicates the angle of the arc. λ in Fig. 16 indicates the angle of the circular arc portion, and in the case of a refrigerant compressor, λ is usually 10 to 156 or less, and the proportion of the total cylinder is generally 1 to 1 or less9. . In such a case, the shape of the inner circumferential surface of the cylinder in this embodiment may be handled in the following two ways. ■ It is formed according to the shape of the cylinder inner circumferential surface (Equation (3)) shown in the specific example, and only the necessary 0271 part is formed by a predetermined arc KF.
jll rounded shape. That is. shall be. (2) The G runt 0 portion having a predetermined angle is formed by a circular arc, and the portion other than the G runt 71 portion has the shape of the cylinder inner circumferential surface of this embodiment. That is. However, instead of formula (4), the formula (4) x[(C11IS(+1 of ml) (Q, Car
(2111#) +1)X (cat(vme)
+C*z (expletive λ) )01〕 ・・・・・・(4
)′. In both cases (1) and (2) above, the rate of change j is slightly larger than in the case where there is no G land, but there is no practical problem and good results can be obtained. Further, in the above case, the G land is made into a circular arc, but it is not limited to a circular arc, but may be made into a shape that smoothly connects the shape of the cylinder inner circumferential surface of the embodiment with the circular arc at this portion. (4) Furthermore, 1 In the above examples, in both cases, equation (4)
Although the value of the word ``in'' corresponds to a cylinder in which two so-called substantially elliptical cylinder chambers are formed with the door=2, the value is not limited to ``2'' and may be any positive integer. For example, the J:5rm=H machining shown in FIG. 17 corresponds to the conventional circular cylinder shape, and rx=3 means that three cylinder chambers are formed. Further, although not shown in the drawings, the number 4 indicates that four cylinder chambers are formed, the number 5 indicates that five cylinder chambers are formed, and so on. (5) It should be noted that with respect to the shape of the inner circumferential surface of the cylinder in this embodiment, the number of paths of the wheels movably interposed in the rotor is arbitrary, and it is clear from the above explanation that it may be an even number or an odd number. . (6) In the above explanation, II (formula 41 or formula (4)1) was proposed as determining the cylinder shape. However, the present invention is limited to formula (4) and formula 14r. Rather, the purpose of the present invention is that the sum of the vane protrusion amounts is theoretically always constant, and as a result, the (4th)
) equation Ah-Q (when vane thickness = 00) Under the intention of the previous invention (Japanese Patent Application No. 56-100437), the cylinder shape is such that the acceleration of the vane is continuously smooth K, and furthermore, ( -7 It is possible to suppress the number of sheets with an appropriate cylinder shape adapted to each machine application and operating condition, and it is also possible to change the size of the machine (without changing the rotor radii α and k), and to displace them. The purpose is to provide a function that gives a cylinder shape that can change the amount.Equation (4), which satisfies this purpose, is !
(In addition to Equation 41', the following can be mentioned: Term 1 of Equation (4) (coJP(m#)+1)0!,
-(41"M (41'jC's XJ -(eat(w
+cap(mλ))"-...+41" of a, the (4th
) equation and equation (4) and 7th equation (in addition to each coefficient shown, multiply the Jis function and cap function of harmonics ((2, (311θ)...) based on the , it may be multiplied by a coefficient (further K) that adds 1 to this. This coefficient is, for example, as follows. Example: (Q, #product (2mθ) + 1), ...
G4Ca#(4-)Today,...However, C4,
C, is a constant.As mentioned above, these functions result in (++a#)
Since it is the sum of the harmonic 71% function based on , and the caj function, the sum of the vane protrusion amounts is always constant and %J
ll (jA=o in Equation 11. Also, according to these, the vane acceleration becomes continuous and smooth. (73) The present invention is applicable not only to refrigerant compressors but also to various rotary fluid machines. (8) Although the present invention has been described above with reference to embodiments, the present invention is of course applicable to such embodiments. However, the present invention is not limited to the above, and the design may be significantly modified without departing from the spirit of the present invention.

[Brief explanation of the drawing]

Figure +81 is a vertical cross-sectional view of a conventional sliding vane type rotary fluid machine, Figure 2 is a 1-1m cross-sectional view of Figure 1, Figure 6 is a performance diagram of the machine, and Figure 4 is the rotor of the machine. Figure 5 shows the shape of the inner circumferential surface of the case, and Figure 6 shows the vane acceleration diagram of the sympathizer.
The figure shows a compression curve and a volumetric curve in the small chamber of the same machine, FIGS. 8 shows the compression curve and volumetric curve of the small chamber, FIG. 10 shows the vane acceleration diagram in FIG. 8, FIG. 13 is a diagram of another implementation example of the inner peripheral surface shape in FIG. 8; FIG. 14 is a diagram of the compression curve and volume curve in the small 1tK shown in FIG. 13; FIG. The figure is an explanatory diagram of the shape of the inner circumferential surface of the cylinder when E7 thickness is taken into account. Figure 16 is an explanatory diagram of the cylinder G run
FIG. 7 is a cylinder shape diagram when the number of cylinder chambers is 2 and 6. A: Inner peripheral surface of Niji cylinder B: Vane base end 1fIs4
Niji Linda (rotor case) 7-1.7-2.7-3.7-4: Vane 8:
Rotor 62: Back pressure chamber. Sub-Agent Patent Attorney Shige Okamoto 2 other persons Figure 3 Rotary rotation angle 0 Figure 7 1'' Figure 8 Figure 9 Figure 12 Figure 15 Figure 16 Decoy Figure 17 (A) (B) Procedural amendments September 7, 1981 Kazuo Wakasugi, Commissioner of the Japan Patent Office 1. List of cases “1982 Patent Application No. 56660 2. Title of invention: Rotating fluid machine 3. Relationship with the amended person case. Patent applicant name (620
) Mitsubishi Heavy Industries, Ltd. 4, Sub-Agent (6208) 2 others 7, In the statement of contents of the amendment (The first line of page 11815, "compressor and one body" is amended to read "compressor itself.") +21# Correct the "configuration that results in 0" in line 6 of page I20 j111m to "configuration that results in 0." (3) Correct the formula in line 9 of page 22 as shown below. (4) No. 40 Correct the formula on page ts line 3 as shown below.

Claims (1)

[Scope of Claims] It is housed in a groove of the rotor so as to be able to move forward and backward, and the base end side faces a common back pressure chamber, and the tip end faces the inner peripheral surface v of the cylinder.
In a rotating fluid machine of a sliding vane disk, which has a structure in which a plurality of two-vanes in contact with each other move forward and backward in the groove by rotation of a rotor, the shape of the inner circumferential surface of the cylinder is determined by ignoring the thickness of the vanes. At the g-7 locus lI, the following (is shown in equation 31, and the amount of protrusion of the vane into the cylinder ttS is the following (
4) Expression or (4r expression), ×((01fj
l&(-)+1)(G, C##(211riten
(cab(-) +1)") ・・・・・・・・・
・・・・・・・・・・・・(4)X [(01JPis(m
#)+1)toe ##(!-)+1)X (ea
t(m$)+ey(mlλ))') ・・・・・・
・・・・・・(4 dots, 0:11 rotation angle (A meter indicating vane position) a: W-radius IL: vane offset amount α: #lB 4/a A Niji cylinder inner circumferential direction Difference between semimajor axis and 11ta radius C1ρ2
．． C1: Constant 11 Contact point 1k between Nijilinda and Shi-Yu (cylinder condition)
λ: Angle of the G-tuned part The cylinder shape determined by the formula (4) and the formula (e), or the (cap (110s in wno) of the formula (4) in the cylinder shape determined by the formula (e) or the formula ( 4-bit type (esJP(m#)+eoy(mλ)
)) csK, harmonics based on (m#) ((2 θ)
, (3 tremors 8...) I-Koh function, tel function multiplied by a certain constant and 1 added to it by a function of the protrusion amount l (#) formed by multiplying it by at least one coefficient. A sliding van type rotary fluid machine having a determined cylinder shape and having a structure in which the rate of change in the amount of projection of the van into a back pressure chamber is w&0.