GB2154666A

GB2154666A - Rotary scroll-type fluid machine

Info

Publication number: GB2154666A
Application number: GB08504477A
Authority: GB
Inventors: Takahisa Hirano
Original assignee: Mitsubishi Heavy Industries Ltd
Current assignee: Mitsubishi Heavy Industries Ltd
Priority date: 1984-02-21
Filing date: 1985-02-21
Publication date: 1985-09-11
Also published as: FR2559846A1; DE3506376A1; GB8504477D0; AU3892485A; SG39089G; FR2559846B1; GB2154666B

Abstract

The machine has a stationary spiral element 600 nested with a movable spiral element 601 and, in use, the central portion of element 601 moves around a circle defined about the center of the element 600, and the portion distant from said central portion moves in reciprocating motion in either a rectilinear or an arcuate locus. In view of such complex movement of the element 601 it is necessary to maintain the desired cooperating relationship between the two nested elements 600,601. This is achieved by providing a limit element or elements, e.g. a link 651, balls (751, Fig. 16) or keys (Figs. 20 to 27) between the nested elements. <IMAGE>

Description

SPECIFICATION Rotary type fluid machine The present invention relates generally to a rotary machine, and more specifically to a rotary type fluid machine such as a compressor, a pump, an expander, etc.

(ii) Description of the Prior Art The typical construction of a scroll-type compressor, for example, generally known in art of the fluid compressor machine as shown in FIG. 1, a schematic view showing generally the principle of operation, is such that there are provided two spiral elements having the same sectional shape, one spiral element 2 being fixed in position onto the surface of a sealing end plate shown having a central delivery opening 4, the other element 1 fixed in position upon the surface of the opposite end plate.Stating further to this construction, these two elements are rotated relatively 1 80 degrees with each other and are shifted in relative location by a distance 2p ( = the pitch of a spiral pattern - 2 X thickness of a spiral element plate) so as to be nested with each other in such a manner as typically shown in the drawing figure that they may be located in their relative position to come mutually in contact at four points 51, 52 and 51', 52'.In this construction, it is further noted such that one spiral element 2 is disposed stationary in position, and the other element 1 is arranged to move in revolution or in solar orbital motion with a radius of p = 00' about the center 0 of the spiral element 2, without moving in rotation or in planetary motion on its own axis, by using a crank mechanism having a radius p.

With such construction, there are defined small chamber or spaces 3, 3 being tightly closed between the abutting points 51, 52 and 51', 52' of the spiral elements 1, 2, respectively, the volumes of which chambers 3, 3 vary gradually with the revolving or solar motion of the spiral element 1.

Reviewing more specifically, it is notable that when the spiral element 1 is firstly caused to be revolved 90 degrees starting with the state shown in FIG. 1 (A), it turns now over to the position as shown in FIG. 1 (B), when it is revolved 1 80 degrees, then it turns to be the state as shown in FIG. 1 (C), and when it is further revolved 270 degrees, it turns then to be the state as shown in FIG.

1 (D). As the spiral element 1 moves in revolution, the volume of the small chambers 3, 3 decrease gradually, and eventually, these chambers come to intercommunicate with each other and merge into one tightly closed small chamber 53. Now, when it moves further in revolution 90 degrees from the state shown in FIG. 1 (D), it turns back to the state of position shown in FIG. 1 (A), and the small chamber 53 would then be reduced in its volume as it turns from the state shown in FIG. 1(B) to that shown in FIG. 1 (C), and eventually, it would exhibit to be a smallest volume intermediate the states shown in FIGS.1(C) and (D).During this stage of motion, outer spaces beginning to be opened as seen in FIG. 1 (B) get grown to be greater as the element 1 turns from the state of FIG. 1 (C) through the state of FIG. 1 (D) to the state of FIG. 1 (A), thus taking another volume of a gas into the tightly closed small chamber to be eventually defined together from these outer spaces, and then repeating this cycle of revolution so that the gas taken into the outer spaces of the spiral elements may accordingly be compressed, thus being delivered out of the delivery opening 4.

The foregoing description is directed to the principle of operation of the scroll-type compressor, and now, referring more in practice to the construction of this scroll-type compressor by way of FIG. 2 showing in longitudinal cross-section the general construction of the compressor, it is seen that a housing 10 is comprised of a front end plate 11, a rear end plate 1 2 and a cylinder plate 1 3. The rear end plate 1 2 is provided with an intake port 14 and a delivery port 1 5 extending outwardly therefrom, and further mounted securely with a stationary scroll member 25, comprised of a spiral or helical fin 252 and a disc 251. The front end plate 11 is adapted to pivotally mount a spindle 1 7 having a crank pin 23.As typically shown in FIG. 3 which is a transversal cross-sectional view taken along the plate defined by the line Ill-Ill in FIG. 2, in corporative relationship with the crank pin 23 there is provided a movable scroll member 24 including a spiral element 242 and a disc 241, through a non-rotary or stationary mechanism, which comprises a radial needle bearing 26, a boss 243 of the movable scroll member 24, a square sleeve member 271, a slider element 291, a ring member 292 and a stopper lug 293.

On the other hand, there are provided such members as a radial needle bearing 1 6 for the shaft 1 7, a movable thrust plate 27 formed integrally with a square sleeve member 271, a backing plate 21, and thrust bearings 20 and 22, which are adapted all together to receive and stop a thrust to be rendered thereupon during the operation.

According to the general construction of this type compressor, however, there is adopted the non-rotary mechanism of the socalled Scotch yoke type, and this mechanism would inevitably bring such drawbacks noted as follows.

They are: (1) There are relatively many components incorporated.

(2) There is the essential requirement that the gaps existing between the sliding engage ment elements be worked to a high precision, which would bring a greater cost burden in the manufacture of the fluid machine.

(3) When the gaps fail in meeting the high precision requirement, there would possibly occur tapping noises in the engagement between the sliding elements, thereby producing abnormal noises of the entire machine, under which condition there would very possibly bring the risks of abnormal wears of the sliding elements, thus eventually cutting the service life of the machine substantially shorter.

In coping with these drawbacks particular to the conventional rotary fluid machines incorporating the non-rotary mechanism as raised above, the present inventors have previously proposed the provision of the rotary type fluid machine construction which omitted the nonrotary type mechanims by way of the Japanese Patent Applications Nos.

205,413/1982; 149,092/1982 (publication Nos. 96493/1984 and 39987/1984); and the Japanese Utility Model Application No.

130,551/1982.

Referring firstly to the Japanese Patent Application No. 205,413/1982, the general construction is of such as shown schematically in FIG. 4 that one spiral element (stationary spiral element) 500 is located securely to a sealing end plate having a generally central delivery port (not shown), and the other spiral element (movable spiral element) 501 is placed fixedly against an opposite end plate in such a relationship that they may come mutually in contact with each other abutting at points 502, 503 and 502', 503', respectively, when installed together.

Reviewing further in detail, these spiral elements are operatively arranged in such a manner that while maintaining constant a distance "I" between the center p' of the driving pin (not shown) adapted to generate the revolutionary motion of the movable spiral element 501 with the radius of motion of p and a point p of reciprocating motion along an arc qq' having a radius r, the movable spiral element 501 is caused to be moved in revolutionary motion about the center 0' of the drive shaft with a radius of revolution p (the distance across the drive shaft center 0' and the driving pin center p').

More specifically, the revolutionary motion of these spiral elements is defined in such a relationship that the point p' may move in rotating motion along the circle having the radius p, and the point p moves in reciprocating motion along the arc qq' having the radius r around the point 0", while maintaining the relationship of pp' = I.

With such structural arrangement, there are defined small tightly closed spaces or chambers 504, 504' between the points of contact 502, 503 and 502', 503' where these two spiral elements 500, 501 meet in contact with each other, and it is seen that these small closed chambers 504, 504' reduce gradually in continuation in their volumes, as the movable spiral element 501 moves in revolution during the operation of the rotary machine.

Now, when the movable spiral element 501 is started in revolutionary motion 45 degrees apart from the position shown in FIG. 4 (A), it will turn to the position as shown in FIG. 4 (B); when it is moved in revolution 90 degrees further, it will then turn to the position as shown in FIG. 4 (C) and so on, then with its eventual revolutionary motion by 31 5 degrees reaching the position shown in FIG. 4 (H).

During this cycle of revolutionary motion of the movable spiral element 501, it is noted that the small chambers 504, 504' will gradually grow smaller, and with a further revolutionary motion of the element 501 by 45 degrees from the position shown in FIG. 4 (H), it will again turn back to the position shown in FIG. 4 (A), and the small chambers 504, 504' will turn to be similar small chambers 505, 505', whereupon these two small chambers 505, 505' will now come to be in communication with each other.

With a further cycle of revolutionary motion of the element 501, it will follow the same patterns of positioning from FIG. 4 (A) through FIG. 4 (B) and so on, and at the moment that the element 501 reaches the position shown in FIG. 4 (H), the small chambers reduces in their volumes to a minimum.

Along with such a cycle of positional shift of the element 501, the outer spaces defined between the outer extensions of the two elements 500, 501 will grow greater from the point to start opening at the position shown in FIG. 4 (A), passing through the positions of FIG. 4 (B) through FIG. 4 (C) and so on to the end of cycle shown in FIG. 4 (H), and at the beginning of a subsequent cycle of revolutionary motion shown in FIG. 4 (A), there is captured another body of gas by a pair of small chambers defined over again. With the subsequent cycles of revolutionary motion of the element 501, a body of gas taken from the outer openings defined between the outer extensions of the two elements is to be compressed by the continuously reducing volumes of the small chambers, finally being delivered outwardly from a delivery opening (not shown) disposed generally at the center of the stationary spirral element 500.

Reviewing more practically, as shown in FIG. 5, which is a fragmentary longitudinal cross-sectional view and FIG. 6, a cross-sectional view taken along the plane defined by the line VI-VI in FIG. 5, there is mounted securely a stationary spiral element 600 in position to the housing 10, and the front end plate 11 mounts pivotally the drive shaft (shaft) 1 7 having the crank pin 23, the boss 243 of a movable spiral element 601 being held rotatably by the crank pin 23 through the radial needle bearing 26.

Also, it is seen that the boss 243 of the element 601 has an arm 607 formed integrally therewith, the leading end of the arm being connected pivotally to one end of a link 609 by way of a pin 608, the other end of the link 609 being connected likewise pivotally to a stopper element 610 mounted fixedly to the cylinder plate 1 3 of the housing 10 through a pin 611. With such construction, when the shaft 1 7 is moved in rotation, the central portion of the movable spiral element 601 is caused to be revolved in the solar motion with the distance between the shaft 1 7 and the crank pin 23 (the radius p of revolution), thus producing the reciprocating motion of the central point of the pin 608 at the arm 607 mounted to the movable spiral element 601 along the arc having the center of the pin 611.

As stated hereinbefore in connection with the principle of operation of the present rotary compressor, it is seen that the spiral elements for this type compressor may take any configuration that has a plurality of abutting points to be defined in the engagement of the two spiral elements, and in consequence, it is possible in practice to dispense with all the drawbacks particular to the conventional nonrotary mechanism incorporated therein that has essentially been required in the conventional construction, accordingly.In this connection, however, there may be adopted an alternative construction in an attempt to bring to practice the compactness, the reduction in production cost and the simplified construction of the thrust resisting mechanism of the compressor as typically shown in FIG. 7, a fragmentary longitudinal cross-sectional view, and FIGS. 8 (A) and 8 (B), the former being a cross-sectional view taken along the line A-A in FIG. 7, the latter a similar cross-sectional view taken along the line B-B in FIG. 7.

Referring more specifically to the above noted drawing figures, it is seen that there are provided a plurality of semi-spherical recesses 700 and 703 in the front end side surface of a disc portion 605 of the movable spiral element 601, and an arc-shaped recess 701 in the rear end side surface 705 of the front end plate 11, the recess 701 being defined having a center 0" and an arc of a radius r.

There is fitted a ball 704 between the semispherical recess 700 and the arc-shaped recess 701, when located together in the opposed relationship. Also, there is likewise fitted balls 71 5 in the number corresponding to the numbers of the semi-spherical recesses 703 between the recesses 703 and the rear end side surface 705 of the front end plate 11, when installed together in the opposed position in the assembly of the front end plate 11 and the movable spiral element 601.

Now, it is designed that the total depth of the semispherical recess 700 and the arcshaped recess 701 is equal to or smaller than the diameter of the ball 704, and that the extension of the arc-shaped recess 701 is equal to or greater than the value that allows a due reciprocating motion along the arc defined around the movable spiral element with the ball 704 mounted in engagement position. Also, it is designed that the width of the arc-shaped recess 701 is determined to be such a value that the ball 704 can hardly move in play widthwise of the recess, when the ball is installed in due position, and that the diameter across the semi-spherical recess 700 is generally equal with the diameter of the ball 704, respectively.

With such dimensional relationship as noted above, it is noted that the ball 704 fitted in position to the semi-spherical recess 700 of the movable spiral element 601 corresponds in function to the very point p as stated in connection with the principle of operation by way of FIG. 4, and that as the motion of the ball 704 is duly restricted by the configuration of the arc-shaped recess 701 provided in the rear end side surface 705 of the front end plate 11, only the rolling motion of the ball along the course of arc having the radius of r around the center 0" is permitted in operation, thus making it possible to have the due reciprocating motion of the point p along the arc as noted in connection with the principle of operation, and thus letting the ball 704 work in proper function to receive and stop the thrust as rendered during the operation, accordingly.Now, with the balls 715 disposed properly in the spaces defined between the semi-spherical recesses 703 and the rear end side surface 705 of the front end plate 11, when installed together in opposed relationship as stated herein before, there is provided a due function of the balls for receiving and stopping the thrust generated during the operation, thus affording the advantageous accomplishment of the compactness, the light weight, the high reliability, and the relatively low production cost, accordingly.

According to the constructions of the compressors of this type, there may be many variations in practice, as follows.

They are: (1) As shown typically in FIG. 9, the member 801 defined with the arc-shaped recess 701 may also be formed integrally with the end surface 705.

(2) In place of the semi-spherical recesses 700 and 703, there may be provided an alternative recess 802 of rectangular shape in its cross-sectional shape as shown in FIG. 10, if the balls 704 and 715 can be held properly in position.

(3) The arc-shaped recess 701 may otherwise be formed in its cross-sectional shape with a due curvature as typically shown by the reference numeral 803 in FIG. 10.

(4) In place of the semi-spherical recess 700, there may be provided such alternative constructions as shown in FIGS. 11 (A) and (B), wherein there are shown a positioning element 804 having a spherical recess 805, and a ring member 806 for the determination of a due position of the ball, which may alternatively be formed integrally with the disc portion 605 of the movable spiral element 601. This shall commonly apply to the semispherical recess 703.

(5) There may alternatively be provided a semi-spherical recess in the rear end side surface of the front end plate 11, instead of the provision of the semi-spherical recess 703 in the disc portion 605 of the movable spiral element 601. Also, the recess 703 may not be the semi-spherical shape, but a guide member 808 may be formed integrally with the end surface 705 as typically shown in FIG. 12.

(6) Instead of the provision of the ball 704 immediately between the opposed semi-spherical recess 700 and the arc-shaped recess 701, there may alternatively be provided a slipper 809 therebetween as shown in FIG.

1 3. This shall commonly apply to the semispherical recess 703 and the ball 715, accordingly.

(7) There may be adopted a pin 810 in place of the ball 704 as shown in FIG. 14(A), and also, there may be formed a projection in the disc portion 605 as shown in FIG. 14 (B).

While the pin 810 or the projection 811 cannot receive and stop the thrust as rendered, they may function to bring a due rectilinear motion of reciprocation required.

Also, the leading end of the pin 81 2 may be formed to be spherical so as to receive the thrust forces encountered.

(8) In the modifications as noted above, while there is shown such a typical construction that the thrust may be received directly by the disc portion 605 of the movable spiral element 601 and the rear end side surface 705 of the front end plate 11, it is of course possible in practice that there may also be provided an appropriate thrust plate upon these members in the opposed relationship for attaining an increased durability.

(9) There may naturally be adopted an appropriate construction of lubrication in the positions of engagement between each of the semi-spherical recesses, the arc-shaped recess and the balls.

In addition to the commonly known constructions as noted above, the present inventors proposed for the same objects the improvement in the construction by filing the Japanese Patent Applications Nos.

149,092/1982 and the Japanese Utility Model Application No. 130,551/1982, in which the central portion of the movable spiral element may move in solar revolutionary motion, while the portion placed away from the central portion may move in rectilinear motion.

However, in the constructions of the rotary type fluid machine as noted, it is very important to have the proper relative relationship in the spiral or helical configurations of the spiral elements incorporated therein. Without this proper relative relationship of these elements, there may possibly be formed an undesired gap between the spiral elements when installed in mutually nesting relationship, from which gap the fluid may very possibly escape, thus reducing the performance of the machine to a substantial extent.

Now, referring again to the constructions as typically shown in FIGS. 5 and 6, it is noted that the stationary spiral element 600 is fixed securely to the housing 10, while the movable spiral element 601 is connected pivotally by the pin 611 to the stopping element 610 of the housing 10 by way of the linkage connection including the arm 607, the pin 608 and the link 609. With such construction, it is notable that the relative relationship of the spiral configuration of the both spiral elements is established with respect to the housing 10.

In consequence, therefore, while it is essential to ensure the due circumferential positions between the stationary spiral element 600 and the housing 10, and between the stopping element 610 and the housing 10, it is generally difficult to attain a proper arrangement in the practice of positioning such elements involved.

Next, referring to the constructions as shown in FIGS. 7 and 8, it is noted that the stationary spiral element 600 is fixed securely to the housing 10, while the movable spiral element 601 is installed in due position by the aid of the ball 704 and the arc-shaped recess 701 of the front end plate 11, when assembled in the opposed relationship with each other, and with this construction, the relative relationship of the spiral configurations of the both spiral elements may be set accordingly by way of the housing 10 and the front end plate 11.

Reviewing more specifically such construction, while it is essential to ensure the proper circumferential positioning between the stationary spiral element 600 and the housing 10, and between the front end plate 11 and the housing 10, it is usually difficult to satisfactorily accord with such requrement in positioning in practice.

Now, according to these constructions as noted above, it is difficult in practice to have the due relative relationship of the spiral configurations of the both scroll members ensured with certainty, thereby resulting in an inevitable reduction in the performance of the machine, and thus resulting in the relatively high production cost of the machine from the necessity of having the proper relative positioning of the involved members mentioned above, accordingly.

Referring further to the other standard arts generally known, there is shown another example of the conventional scroll type fluid machine in FIG. 18. A movable scroll member designated at 101 is shown having a disc portion 101b and a spiral element 101a. Also shown is a stationary scroll member at 102, having a disc portion 102b and a spiral element 1 02a. It is seen that these spiral elements of the scroll member 101 and of the stationary scroll member 102 are nested in an opposed relationship with each other, thus forming a fluid pocket 103 therebetween. The stationary scroll member 102 is fixed securely against a frame 106, and the movable scroll member 101 is interlocked with a crank portion 1 07a of a crank shaft 107 through a bearing 106b, and also with the frame 106 by way of a self-rotation preventing mechanism 108 comprising the Oldham's coupling.

The crank shaft 107 is actuated rotatably by a motor 109, then the movable scroll member 101 is caused to move in solar revolutionary motion with a radius of crank p while being held from the planetary rotating motion by way of the self-rotation preventing mechanism 108, and concurrently, taking the fluid with suction effect into the fluid pocket 103 so as to have it compressed and then directed to a delivery opening 104 provided in the disc portion 1 02b of the stationary scroll member 102 during its revolutionary motion.

According to this construction of the scroll type fluid machine, if the origin or center of the movable scroll member 101 does not move in constant revolutionary motion with the radius of crank p around the origin or center 0 of the stationary scroll member 102, while maintaining the proper relative relationship of the spiral configuration with respect to the stationary scroll member 102, it would occasionally happen that the spiral elements 102a, 101a of the stationary scroll member 102 and the movable scroll member 101 respectively come to even an improper engagement or biting with each other, or resulting in a possible growth of the gap between the two elements, and thus bringing an escape of the fluid in the fluid pocket 103 therefrom, with the eventual reduction in the performance of the scroll type fluid machine, after all.

Under such circumstances, however, in the conventional arrangement as noted above there is employed the Oldham's coupling as the self-rotation preventing mechanism 108, and with such construction, this Oldham's coupling is, as typically shown in FIG. 19, fitted in slidable fashion by way of one key 1 08b of the Oldham's ring 1 08a into the key way of the movable scroll member 101, and also by way of the other key 1 08c fitted freely slidably into the key way of the frame 1 06, respectively. In addition, according to the such construction that the stationary scroll member 102 is fixed in position to the frame 106, it is noted that the relative relationship of sprial configurations of the movable scroll member 101 and the stationary scroll member 102 may duly be determined with respect to the frame 106.

In consequence, in order to attain a proper relative relationship of spiral configuration between the movable scroll member 101 and the stationary scroll member 102, it is then essential to have the relative relationship in the spiral configurations between the frame 106 and the stationary scroll member 102 established prior accordingly. For this purpose, while there was conventionally provided a positioning pin, for example, between these two in such common construction, this would bring a relatively high cost, and it is generally difficult to have a due setting in precision of the two scroll members 101, 102, and therefore, resulting accordingly in such a defect as an undesirable struggling in the performance of the fluid machine in practice.

4. SUMMARY OF THE INVENTION: The present invention is therefore materialized to practice in view of such circumstances and inconveniences as noted above and is essentially directed to the provision of an improved rotary type fluid machine, which can afford an efficient solution to these problems, accordingly. It is therefore a primary object of the present invention to provide an improvement that there is attained a ready setting of the relative relationship in the spiral configurations between the stationary spiral element and the movable spiral element of the fluid machine, as well as the stability and efficiency in such setting, thereby ensuring a high performance of the machine, and also with a substantial reduction of the production cost.

According to the entity of the present invention, there is provided, as briefly summarized, an improved construction of the rotary type fluid machine having two spiral element means disposed in mutually nested relationship with each other, one spiral element means being to be stationary and the other spiral element means being to be movable with respect to the one element means with its central portion shifting in revolutionary motion along the circumference defined around the center of the one stationary spiral element means, and with its portion distant away from the central portion shifting in reciprocating motion either in a rectilinear or in an arcuate locus, thereby having the fluid introduced and delivered under pressure, which further comprises limit means adapted to control the relative relationship in the spiral configurations between the both spiral element means in the mutual nested engagement.

By virtue of such an advantageous construction as noted above, there is assured the following effect and function, as follows.

(1) There is no longer any need for the strict setting of the relative positioning of the both scroll members with respect to the front end plate, the housing, etc. of the fluid machine that has hitherto been required in the conventional construction, and which will certainly bring a substantial reduction of the machine cost.

(2) Since the relative relationship between the both spiral elements is, as noted above, determined essentially from the construction of the both spiral elements per se or of the self-rotation preventing mechanism of the movable spiral element incorporated between the both elements, and with the precision of work duly ensured, there will be no risk of leakage from the gap to be defined between the both elements, thus making a substantial improvement in the performance of the machine, accordingly. In addition, the struggling in the machine performances is reduced to a substantial extent, and thus making it feasible in practice to provide the stable supply of the excellent performances of the machine, after all.

The other objects, principle, property and details of the present invention will, as well as advantages thereof, become more apparent from the following detailed description by way of a preferred embodiment of the invention, when read in conjunction with the accompanying drawings.

5. BRIEF DESCRIPTION OF THE DRAWING: FIG. 1 is a series of schematic views showing the principle of operation of the known scroll-type compressor; FIG. 2 is a longitudinal cross-sectional view showing the general construction of the known scroll-type compressor; FIG. 3 is a transversal cross-sectional view taken along the line Ill-Ill in FIG. 2; FIG. 4 is a series of schematic views showing the principle of operation of the rotarytype fluid machine disclosed by way of the Japanese Patent Application No.

205,41 3/1 982 filed by the present inventors; FIG. 5 is a longitudinal cross-sectional view showing the construction of the prior art rotary-type fluid machine according to the principle shown by way of FIG. 4; FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG. 5; FIG. 7 is a cross-sectional view showing the modification in the construction shown in FIG.

5; FIG. 8 (A) and (B) are transversal crosssectional views taken along the line A-A and B-B in FIG. 7, respectively: FIGS. 9 through 14 are fragmentary longitudinal cross-sectional views showing the modifications in the construction of the prior art ball engagement mechanisms shown in FIG.

7, respectively; FIG. 1 5 is a fragmentary longitudinal crosssectional view showing a preferred embodiment of the present invention; FIG. 16 is a similar longitudinal cross-sectional view showing the modification in the construction shown in FIG. 15; FIGS. 1 7 (A) and (B) are fragmentary longitudinal cross-sectional views showing the modifications in the construction of the ball engagement sections shown in FIG. 16, respectively.

FIG. 1 8 is a longitudinal cross-sectional view showing the general construction of a further known scroll-type compressor; FIG. 1 9 is an enlarged top plan view showing in detail the self-rotation preventing mechanism of the scroll-type compressor shown in FIG. 18; FIGS.20 through 22 are schematic views showing the construction of another embodiment of the present invention; in which FIG.

20 is a fragmentary longitudinal cross-sectional view, FIG. 21 is a fragmentary perspective view showing a cross-type key according to the present invention FIGS. 22 (A) and (B) are plan views showing the configuration of key ways formed in the movable and stationary scroll members; FIGS. 23 and 24 are perspective views showing the cross-type key according to a further embodiment of the present invention, respectively; FIG. 25 is a fragmentary longitudinal crosssectional views showing still another embodiment of the present invention; FIG. 26 (A), (B) and (C) show a still further embodiment of the present invention, in which FIGS. 26 (A) and (B) are plan views showing the key ways provided in the movable and stationary scroll members, respectively, and FIG. 26 (C) is a perspective view showing the general construction of the crosstype key; and FIG. 27 is a perspective view showing the general shape of the cross-type key according to a further embodiment of the present invention.

6. DETAILED DESCRIPTION OF THE INVEN TION: The present invention will now be explained by way of a preferred embodiment thereof as adapted in practice to the rotary type fluid machine in reference to the drawings attached herewith. Now, the reference is made to FIG.

1 5 showing the fragmentary longitudinal cross-sectional view of the present embodiment, FIG. 16 similar longitudinal cross-sectional view showing the modification in the construction shown in FIG. 15, and FIGS. 1 7 (A) and (B) also similar longitudinal crosssectional view showing the modification in the arrangement of the ball engagement section of FIG. 16, respectively.

Firstly, FIG. 1 5 is shown in correspondence with FIG. 5, in which the like parts shown are designated by the like reference numerals.

According to this construction, there is shown the stationary spiral element 600 fixed securely in position to the housing 10, while the movable spiral element 601 has the link 651 mounted pivotally at its one end by way of the pin 650 on the disc portion 605, and having the opposite end of the link 651 connected pivotally by way of the pin 652 to the disc portion 603 of the stationary spiral element 600, respectively.

In this construction, there is also a recess for relieving designated at the reference numeral 653 formed in the disc portion 603 of the stationary spiral element 600 for allowing the pin 650, with the link 651 connected pivotally in position, to move in reciprocating motion with an arcuate pattern.

With such construction, like the one shown in FIGS. 5 and 6, it is arranged that the pin 650 of the movable spiral element 601 can move in an arcuate reciprocating motion by the aid of the link 651, accordingly.

It is to be noted that the relative relationship between the stationary spiral element 600 and the movable spiral element 601 may be determined by the general construction of the both elements per se, or in other words, that the relative positioning of these elements can therefore be determined exclusively from the definite location of the pins existing on these elements and from the precision of work of the link member, after all. As there is no factor in relation with any other members involved such as the housing, the front end plate, etc., it is advantageous that there will consequently be no need for a strict positioning of these members, at all.

Now, referring to FIG. 16, which shows the general construction of the invention corresponding to the conventional construction shown in FIGS. 7 and 8, the construction for receiving the thrust loads as rendered upon the movable spiral element 601 during the operation is such that there are shown provided the plurality of semi-spherical recesses 703 in the disc portion 605 similarly to the conventional arrangement, into which recesses there are the balls 704 inserted, respectively.In addition, there is also provided the semi-spherical recess 750 in part of the end surface of the disc portion 605 of the movable spiral element 601 facing the stationary spiral element 600, and there is provided an arc-shaped recess 752 (with the similar shape to that shown in FIG. 8 (A)) in part of the end surface of the disc portion 603 of the stationary spiral element 600 on the side of the movable spiral element 601, respectively, and there is snugly inserted the ball 751 therebetween.

According to such construction as noted above, as in the case shown in FIGS. 7 and 8, it is notable that a part of the movable spiral element 601 may be caused to be moved in reciprocating motion in an arcuate fashion, and further that thus-established relative relationship between the both spiral elements may be determined exclusively with the both spiral elements and the balls operatively engaged therebetween, accordingly.

In place of the ball engagement noted above, there may be adopted an alternative arrangement as shown in FIGS. 1 7 (A) and (B).

According to the construction shown in FIG.

1 7 (A), there is formed a pin dwell hole 900 in the disc portion 605 of the movable spiral element 601, and on the other hand, there is provided an arc-shaped recess 902 in the stationary spiral element 600, respectively.

Now, referring to FIG. 1 7 (B), there is a pin-like projection 903 formed integrally in the disc portion 605 of the movable spiral element 601.

Unlike the conventional constructions shown in FIGS. 9 through 13, it is notable that there may be provided a disc portion of the movable spiral element in place of the front end plate 11, and that there may also be provided the components of such linkage mechanism as noted above on the part of the disc portion of the stationary spiral element in place of the disc portion of the movable spiral element, respectively. In such constructions, however, it is not necessarily essential that the ball element will receive the thrust loads rendered thereupon during the operation.

By the way, it is naturally possible in practice that these components such as pins and links, or such as balls, pins and semi-spherical recesses as noted above may be lubricated in any appropriate manner.

For the provision of such lubrication of these components, it is needless to mention that there may be provided an appropriate clearance between these components so that no thrust loads may be rendered thereupon.

Also, it is practicable that these balls or pins may be provided on the part of the disc portion of the stationary spiral element in place of the disc portion of the movable spiral element, and that the arc-shaped recess may be provided on the part of the disc portion of the movable spiral element in place of the disc portion of the stationary spiral element, as well.

In addition, the description will now be given in the concrete by way of still other embodiments of the invention by referring to FIGS. 20 through 22. As typically shown in FIG. 20, there are provided a plurality of key ways 301 extending in the same direction in the surface of the disc portion 1 02b of the stationary scroll member 102 facing opposedly the movable scroll member 101. yet only two key ways seeable in the figure. On the other hand, there are provided a corresponding number of key ways 302 in the surface of the disc portion 101 b of the movable scroll member 101 facing opposedly the stationary scroll member 102 in such a relationship that these key ways may extend generally at the right angles with respect to the key ways 301, respectively.And there is provided a cross-shaped key 300 as schematically shown in FIG. 21, with its key element 303 being engaged in slidable fashion with the key way 301 formed in the stationary scroll member 102, and with the other key element 304 engaged in like slidable fashion with the key way 302 in the movable scroll member 101, respectively. As the other details are similar in its construction to that shown in FIG. 18, the like parts are designated at the like reference numerals.

Now, as shown typically in FIG. 22, there are formed key ways 301 and 302 in the disc portions 102b and 101b of the stationary scroll member 102 and the movable scroll member 101, respectively, with the cross key 300 being operatively engaged with the key ways 301, 302 respectively in such manner that the key element 303 may move in slidable reciprocating motion along the key way 301 of the stationary scroll member 102 in the longitudinal direction thereof shown by the double-headed arrow, and that the key element 304 of the cross key 300 may also move in slidable reciprocating motion along the key way 302 of the movable scroll member 101 in the longitudinal direction thereof.

By virtue of this operative engagement of the key 300 allowing such two reciprocating motions in combination with each other, the movable scroll member 101 may move in solar revolutionary motion while being prevented from its selfrotating motion, accordingly.

With the provision of the cross-type key 300 of such a unique yet very simple construction as noted above, it is now possible in practice to effectively hold the movable spiral element from its self-rotating motion, and thus making it feasible to provide a substantial reduction of the production cost of the fluid machine, accordingly.

At the same time, by virtue of the fact that the relative relationship in the spiral configurations between the both scroll members 101, 102 may duly be predetermined exclusively from the precision of machining work of the key ways 301, 302 and the cross-type key 300, it is to be noted that the step of strict positioning of the stationary spiral element with respect to the machine frame that has hitherto been essential in the installation work is not necessary any longer. In addition, with the elimination of this specific mechanism required thus far for such positioning work, it is now possible to have the period of time required for the assembly of such mechanism cut short, accordingly.

While the relative relationship in the spiral configurations between the both scroll members is predetermined accordingly by the precision of machining work of the self-rotation preventing mechanism and also by the precision of installation work for the stationary scroll member with respect to the frame of the machine, this relative relationship will now depend upon the precision of machining work of the self-rotation preventing mechanism exclusively of the precision in installation of these members.From this advantageous feature, it is now possible in practice that the relative relationship in the spiral configurations between the both scroll members may well be set with a sufficient stability, thus bringing a substantial reduction in the struggling of the machine performances when assembled, and then making it possible to ensure the accordingly stable provision of the proper machine performances, after all.

Now, as shown in FIG. 23, it is also possible in practice to employ a modified crosstype key 400 having key elements 402 and 403 extending generally at the right angles with each other on the opposite head and tail surfaces of a disc portion 401 thereof. It is noted that this cross-type key 400 may be made with an increased constructional strength of the key elements 402, 403, but a modification will be required in the addition of a recess in the disc portion 101b or 102b of the movable scroll member 101 or the stationary scroll member 102 for allowing the shifting motion of the disc portion 401, accordingly.

Besides, as shown in FIG. 24, there is made available a modification with the employment of a cross-type key 450 having a plurality of pins 452, instead of the key elements, formed integrally with or implanted by way of screw-in or press-fitting into a disc portion 451 thereof.

In addition, as typically shown in FIG. 25, there may also be provided an oil groove 361 in the movable scroll member 101 so that the key way 302 may properly be supplied with the lubricating oil, and the engagement of the crosstype key 300 and the key ways 301, 302 are lubricated accordingly.

The material and the surface treatment for the cross-type key may be specified appropriately. It may be made of an iron casting or of any other metal material such as alminium, or else of a further material like a plastic resin, and its surface may be treated accordingly with such as the phosphoric acid film treatment, the general metal platings, the Teflon coating, etc. as desired accordingly.

As shown further in FIG. 26 (C), there may be provided an annulus 472 as a further modification of the cross-type key having key elements 474, 475 extending at the right angles with each other on the opposite sides thereof. This modified key 472 may as well be adapted with its key element 474 being engaged in a slidable relationship with the key way 471 as formed in the surface of the movable scroll member 101 facing the stationary scroll member 102 and with its key element 475 engaged in the like manner with the key way 473 formed in the surface of the stationary scroll member 102 facing opposedly the movable scroll member 101, respectively, as shown in FIGS. 26 (A) and (B).

Also, as shown in FIG. 27, there may be implanted pins 476 into the annulus 472, instead of the key elements shown in FIG. 26, as an alternative construction.

While the typical preferred embodiments of the present invention has been described fully hereinbefore, it is to be understood that the present invention is not intended to be restricted to the details of the specific constructions shown in the preferred embodiments, but to the contrary many changes and modifications may be made in the foregoing teaching without any restriction thereto and without departing from the spirit and scope of the invention.

It is also to be understood that the appended claims are intended to cover all of such generic and specific features particular to the invention as disclosed herein and all statements relating to the scope of the invention, which as a matter of language might be said to fall thereunder.

Claims

1. A rotary type fluid machine having two spiral element means disposed in mutually nested relationship with each other, one spiral element means being to be stationary and the other spiral element means being to be movable with respect to said one element means with its central portion shifting in revolutionary motion along the circumference defined around the center of said one stationary spiral element means, and with its portion distant away from said central portion shifting in reciprocating motion either in a rectilinear or in an arcuate locus, thereby having the fluid introduced and delivered under pressure, which further comprises limit means disposed in an operative relationship immediately between said both spiral element means and adapted to operatively restrict the relative relationship in the spiral configurations between said both spiral element means in a mutually nested state of engagement.

2. The rotary type fluid machine as claimed in Claim 1, wherein said limit means are linkage means connected pivotally between said stationary spiral element means and said movable spiral element means.

3. The rotary type fluid machine as claimed in Claim 1, wherein said limit means are ball means inserted in operative engagement between the semi-spherical recess means defined in the end surface of the disc portion of said movable spiral element means facing said stationary spiral element means and the arcshaped recess means defined in the end surface of said stationary spiral element means facing said movable spiral element means.

4. The rotary type fluid machine as claimed in Claim 1, wherein said limit means are pin means implanted into said disc portion of said movable spiral element means in opposed relationship with said arc-shaped recess means defined in the end surface of said stationary spiral element means facing said movable spiral element means.

5. The rotary type fluid machine as claimed in Claim 1, wherein said limit means are projection means formed integrally with said disc portion of said movable spiral element means in opposed relationship with said arcshaped recess means defined in the end surface of said stationary spiral element means facing said movable spiral element means.

6. The rotary type fluid machine as claimed in Claim 1, wherein said limit means are selfrotation checking means disposed in operative relationship between said both spiral element means in such a manner that said checking means permit the solar revolutionary motion, yet prevent the self-rotating motion of said movable spiral element means.

7. The rotary type fluid machine as claimed of Claims 1 and 6, wherein said self-rotation checking means for preventing the self-rotating motion of said movable spiral element means are cross-shaped key means which are adapted to engage slidably with a plurality of key way means defined extending in same one direction in the surface of said stationary spiral element means facing said movable spiral element means and with key way means defined extending in a direction generally at the right angle with said plurality of key way means in the surface of said disc portion of said movable spiral element means facing said stationary spiral element means.

8. The rotary type fluid machine as claimed in Claims 1, 6 and 7, wherein said crossshaped key means have key elements formed projecting from the opposite sides of disc means and extending generally at the right angle with each other.

9. The rotary type fluid machine as claimed in Claims 1, 6 and 7, wherein said crossshaped key means have key elements in the form of pin formed integrally with or implanted into the opposite sides of said disc means.

10. The rotary type fluid machine as claimed in Claims 1 and 6, wherein said selfrotation checking means are key means which are adapted to engage slidably with key way means defined in the surface of said disc portion of said movable spiral element means facing said stationary spiral element means and with key way means defined in the surface of said stationary spiral element means facing said movable spiral element means, and which are formed extending in the opposite sides of annulus means generally at the right angle with each other.

11. The rotary type fluid machine as claimed in Claims 1, 6 and 10, wherein said key means are in the form of pin formed integrally with or implanted into the opposite sides of said annulus means.

12. The rotary type fluid machine as claimed in Claims 1, 6 and 7, wherein said movable spiral element means are defined with oil groove means adapted to provide said key way means with the lubrication oil for due lubrication in the engagement between said key means and said key way means.