JPS6114359B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to scroll-type liquid pumps and includes embodiments of such liquid pumps that can be submerged in the liquid being pumped.

There are pumps, compressors, and engines commonly referred to as "scroll type" in which two interdigitated spiroid or involute curved helical elements having the same pitch are mounted on separate end plates. This is known to those skilled in the art. These helical elements are offset both angularly and radially and are in line contact with each other, for example along only at least one pair of contact lines between the two helical surfaces. A pair of line contacts occur approximately on a radius drawn outwardly from the central region of the scroll to form at least one fluid region or pocket. The positions of these pockets change with the relative rotation of the helical centers, and all pockets maintain the same relative angular position. As the contact line moves along the scroll surface, the volume of the pocket thus formed changes. Compressors and expansion engines thus have lowest and highest pressure regions connected to the fluid ports. In a liquid pump, the volume ratio remains 1 throughout. The outermost pocket and the innermost pocket are connected to liquid ports such that liquid flow may be directed outwardly from the innermost pocket or inwardly from the outermost pocket.

Compared to expanders and compressors, scroll-type liquid pumps have many advantages, including fewer leakage problems and lower operating temperatures.
However, despite these advantages, scroll-type liquid pumps offer significantly higher speeds (e.g. at least
1800 rpm) and virtually without pulsation, it will not be possible to realize a device that is acceptable on the market. The scroll-type liquid pump of the present invention incorporates means for eliminating pressure pulsations or reducing pressure pulsations below a level at which the pulsations adversely affect pump performance and efficiency. . As will be seen from the description below in connection with the embodiment of the scroll pump shown in Figures 62-84, the scroll liquid pump is suitable for immersion in the liquid being pumped, particularly in the fuel tank of a self-propelled vehicle, such as an automobile. It is possible to create a structure that allows

It is therefore a first object of the present invention, when incorporated into a scroll-type liquid pump, to provide a pulsation-free liquid flow of the pump in a quiet manner at a considerably high velocity.
Moreover, it is an object of the present invention to provide a unique stationary and orbiting scroll member that allows operation to discharge with maximum efficiency. Another object in this connection is to provide a scroll-type liquid pump which is simple and economical in construction and whose parts are made of plastic, for example by molding.

Another main object of the invention is to provide a scroll-type liquid pump having the above-mentioned characteristics, which in one embodiment is suitable for being immersed in the liquid being pumped. Another object of the invention is that it can be used as a fuel pump for self-propelled vehicles using light fuel oil and can be placed in the fuel tank and for this purpose be used as a fuel pump for self-propelled vehicles using light fuel oil. It is an object of the present invention to provide a scroll-type liquid pump that can be isolated from excessively high temperatures that may occur.

Yet another object of the present invention is to be capable of generating high fuel discharge pressures, being self-starting, capable of operation substantially free of noise, vibration and output flow vibration, and capable of withstanding long periods of dry operation. An object of the present invention is to provide an immersion type liquid pump which is characterized in that it can be operated, does not require a valve, and is not permanently damaged even if dust enters the pump. Yet another purpose is
Automatic scroll sealing, minimal friction losses, long-term reliable operation,
It is an object of the present invention to provide a scroll-type liquid pump having the above-mentioned characteristics and having a low cost. Other objects of the invention are in part obvious and in part will become apparent later.

According to one feature of the invention, a stationary scroll member is provided having a central liquid port, a stationary end plate, and a stationary end plate, the stationary scroll member being suitable for incorporation into a scroll-type liquid pump. It consists of a stationary involute trap fixed to one side of the plate and having the shape of a one-and-a-half turn involute curve, and a stationary concave liquid transfer passage provided on the one side of the stationary end plate. a stationary scroll member, the orbiting scroll member being arranged to be rotated relative to the stationary scroll member by a driving means, the orbiting scroll member being fixed to one side of the orbiting end plate; , an orbiting scroll member comprising an orbiting involute trap having the shape of a one-and-a-half turn involute curve, and an orbiting concave liquid transfer passage provided on the one side of the orbiting end plate. and the position and shape of the stationary and swirling concave liquid transfer passages reach a point where the swirling involute trap forms three essentially blocked liquid pockets of the swirling cycle. A pair of scroll members is provided that is positioned and shaped such that both passages are substantially immediately open for liquid flow.

According to another feature of the invention, a positive displacement liquid pump is provided with an axial force forcing the scroll members into axial contact with the paired scroll members of the invention as described above. an application means, a coupling for maintaining a fixed angular relationship of the scroll member, a liquid inlet and a liquid outlet, and a liquid inlet and a liquid outlet for pivoting the orbiting scroll member, thereby causing the involute trap to characterized in that the side flanks and the end plate are provided with a combination of a displacement liquid pocket of varying volume and a drive means for forming a peripheral region around the pocket and a discharge region. A positive displacement liquid pump is provided.

According to a further feature of the invention it is suitable for immersion in the liquid being pumped;
The housing further includes a housing having a chamber containing the scroll member formed therein, and having the liquid suction port at one end and the liquid discharge port at the other end. includes a motor disposed within the chamber between the scroll member and the liquid outlet end of the housing to cause liquid to be pumped by the scroll member and passed through the pump. A positive displacement liquid pump as described above is provided in which a radially outwardly flowing liquid flows around the drive means to maintain a predetermined liquid pressure within the chamber to provide the axial force applying means.

Accordingly, the present invention consists of features in the configuration, combination of elements, and arrangement of parts that will become apparent in the configurations described below.

For a more complete understanding of the nature and objects of the invention, reference should be made to the following description in connection with the accompanying drawings.

The sealed pockets of fluid within the scroll device are defined by two parallel planes formed by the end plates and two cylindrical surfaces formed in the shape of circular involutes or other suitable curved shapes. Turn around and be surrounded. The axes of the scroll members are parallel to each other. Only by doing so will continuous sealing contact between the flat surfaces of the scroll members be maintained. As the two line contacts between the cylindrical surfaces move, the sealed pocket moves between these parallel planes. The line contact is moved by the rotation of one columnar element, such as a scroll member, within the other columnar element. This is accomplished, for example, by keeping one scroll member stationary and rotating the other scroll member. In the pump of the present invention, the pumping action is achieved by such a mechanism, so
This pump is called a scroll liquid pump.

In the following description, the term "scroll element" refers to the basic component consisting of the end plate with the unique porting mechanism of the present invention and the involute curved component forming the contact surface creating line of travel contact. It is used. The term "lap" is used to refer to an involute-like component that creates moving line contact. These laps have the shape of, for example, an involute vortex or an arc, and have height and thickness. The term "scroll member" is used to refer to the entire stationary or orbiting component of which the stationary or orbiting scroll element forms a part.

In scroll systems used as compressors and expanders, the wraps of the scroll member can be involuted with any number of turns as desired. However, in scroll-type liquid pumps, each scroll member wrap must be an involute of one and a half turns. This constraint arises from the constraint that the compression ratio of a scroll device designed as a liquid pump must be exactly 1. If the compression ratio of the scroll device is greater than 1, the scroll device will attempt to compress the trapped liquid. Since liquids are inherently incompressible, scroll pumps operating at compression ratios greater than 1 are subject to failure or reduced performance. Therefore, in order to achieve a compression ratio of 1 in a scroll pump, the wrap of the scroll member must be an involute of only one and a half turns. This length of the wrap achieves the desired continuous seal between the internal region formed between the scroll members and its surrounding region, while ensuring that the trapped liquid is not compressed. do not have.

However, limiting the length of the wrap to one and a half turn involutes does not solve all the problems in making an efficient and practical scroll liquid pump. This is because it still does not solve the important problem of pressure pulsations that occur when discharging liquid from a pump. The cause of these pressure pulsations is that the rate of change in the volume of the scroll pocket (whether in the center or the periphery) leading to the discharge port is faster than the rate of change in the discharge area opened for this pocket. It's a big thing. Thus, by rotating the orbiting scroll member, the liquid in the discharge pocket is compressed and forced through the narrow discharge gap, thereby generating intermittent high pressure pulses. This pressure can be so great as to damage the hardware forming the scroll member.

Some pressure pulsations are acceptable when small, relatively inefficient pumps are operating at relatively low speeds. However, almost all uses of liquid pumps require that they provide relatively pulsation-free discharge flow and be capable of operating at significant speeds, such as 1800 rpm or higher.

By employing a new port mechanism, the scroll pump of the present invention achieves relatively high flow rate, pulsation-free pumping action. This new port mechanism eliminates pulsations within the discharge pocket by opening the discharge port at a greater rate than would be the case if the movement of the orbiting scroll member wrap was used solely to open the discharge port. Release the pressure that occurs.

Since liquid flowing through a scroll pump can flow from the peripheral area into the central pocket or out from the central pocket into the peripheral area, this new porting mechanism will
peripheral areas or combined with both.

Figures 1-4 illustrate stationary and orbiting scroll elements suitable for use in scroll members forming scroll-type pumps in which fluid flows from a peripheral region into a central pocket. The stationary scroll element 10 of FIG. Patent No.
(See No. 3994635). The starting point of the involute trap 12 is the tangent to the involute generation radius (a
The contact point 14 passes through the contact points of both the involutes of the stationary and orbiting scroll members, drawn as tangent to the involute generating radius), and the ending point is at the contact point 15, also drawn as a tangent to the involute generating radius. . The wrap is thus in the form of a one-and-a-half turn involute curve and has an outer flank surface 16, an inner flank surface 17, and an end surface 18.

End plate 11 has a central boss 20 extending from an outer surface 21. The boss 20 has an annular groove 22 arranged to retain the seal ring when the stationary scroll element is incorporated into a stationary scroll member in a liquid pump as shown in FIG. A liquid port 23 extends through the end plate 11 and the boss 20, and a concave transfer passage 24 is formed in the inner surface 13 and communicates with the port 23. Ports 23 and recessed transfer passageways 24 together form a manifold means or discharge area.
As shown in the top view of FIG. 1, one main boundary line 25 of the transfer passage 24 coincides with a straight line drawn through the center 26 of the end plate 11 parallel to the contact points 14 and 15; The two curved main boundaries 27 are formed when the two scroll elements are oriented to produce a maximum of four points of contact between the flanks of their laps, as shown in the lap orientation of FIG. It conforms in shape to the outer flank surface 34 of the involute trap 32 of the orbiting scroll element 30 (FIGS. 3 and 4). This curved main boundary line 27 may therefore be defined as a partial locus of the edge of the involute trap of the scroll elements to be combined. These main boundaries are connected via a fused radius 28. Although the transfer passageway 24 could be semi-circular without the involute border 27, the involute shape shown is preferred to provide accurate port functionality. Since the concave transfer passage 24 is located inside the involute trap, it may be referred to as an "inner passage" for convenience.

In Figures 1 and 2, port 23 is replaced by transfer passage 24.
Although the port 23 is shown intersecting the boundary line 25 of the scroll element, the port 23 may be provided by the wrap of the scroll element as long as the port 23 is in communication with the transfer passageway 24 and does not interfere with the integral construction of the wrap 12. It is within the scope of the present invention to provide it anywhere within the formed inner pocket.

As can be seen in FIGS. 3 and 4, the orbiting scroll element 30 has the same shape as the stationary scroll element 10. The orbiting scroll element 30 is formed by an end plate 31 and an involute curved lap 32 fixed to or integral with the inner surface 33 of the end plate 31. The lap 32 has an outer contact flank surface 34 and an inner flank surface 35.
and a contact end surface 36. The starting point of the involute trap 32 is at a contact line 37 through the contact point of both the involutes of the stationary and orbiting scroll elements, drawn as a tangent to the involute generation radius, and the end point is also drawn as a tangent to the involute generation line. The contact line 38 is located at the contact line 38. Inner surface 38 of the end plate of the orbiting scroll element
is formed with a concave transfer passage 39 whose position and shape with respect to the stationary scroll element is in the same relationship as the position and shape of the stationary scroll element's transfer passage 24 with respect to the orbiting scroll element. That is, one straight main boundary line 40 defining the transfer passage 39 coincides with a straight line drawn through the center 41 of the end plate parallel to the contact lines 37 and 38, and another curved main boundary line 42 of the edge forming the outer flank surface 16 of the lap 12 of the stationary scroll element when the two scroll elements are oriented to produce a maximum of four points of contact as shown in FIG. It is now consistent with the partial trajectory. These main boundaries are again connected via a fused radius 43. These concave transfer passages 24 and 3 in the end plates of the scroll elements
9 in combination constitutes one embodiment of the unique port mechanism of the device of the present invention.

If the scroll element is made of metal such as stainless steel, the concave transfer passageway can be made by machining the element, and if the scroll element is made of a synthetic resin such as polyimide, the concave transfer passageway can be made by machining the element. The channels can be created during molding of the element. It is generally preferred that the depth of these concave transfer passageways be approximately equal to the width of the involute trap.

The manner in which the scroll element porting mechanism shown in FIGS. 1-4 provides substantially pulsation-free liquid pumping is illustrated in detail in FIGS. 5-20. Fifth
~Figure 20 shows the operation of a scroll pump that uses these scroll members to pump up liquid so that it flows radially inward. One cycle of pump action is divided into eight stages, and the scroll pump at each stage is divided into eight stages. Indicates the position of the element. The odd-numbered figures are cross-sectional views of the wrap taken in a plane perpendicular to the centerline of the device, and the even-numbered figures following these figures are corresponding longitudinal cross-sections of the wrap.
5-20, the same components as in FIGS. 1-4 are given the same reference numerals as in FIGS. 1-4. Although it is usually not possible to see the contours of the concave transfer passages 39 of the rotating scroll elements in cross-sectional views taken along a plane perpendicular to the center line (for example, FIGS. 5 and 7), The outline of these passages 39 has been drawn in dotted lines in order to indicate their location in the longitudinal cross-sectional views (e.g., FIGS. 6, 8, etc.). The boss 20 of the stationary scroll element has been omitted from the longitudinal cross-sectional views of FIGS. 6, 8, etc. for simplicity of illustration.

During operation of the scroll pump, the orbiting scroll element 30 attached to the orbiting scroll member orbits the stationary scroll element 10 attached to the stationary scroll member (described in more detail below with reference to FIG. 61). (by means), when the flank surfaces 16 and 17 and 34 and 35 of the stationary and orbiting scroll elements form a line of travel contact. As will be described when explaining FIG.
There is a very small gap of 0.005 inch (0.0025-0.127 mm). The end faces 18 and 36 of the stationary and orbiting scroll elements contacting the inner surfaces 33 and 13 of the orbiting and stationary scroll elements, respectively, form moving pockets 50, 51 and 52, and the volumes of these pockets and the distance between them The liquid moves within the pump by changing the conduction state of the liquid. Since liquids are much more viscous than gases, and the volume ratio in the liquid pump is equal to 1 rather than greater than 1, an effective radial seal between the pockets at the contact end faces 18 and 36 of the wrap is less likely to occur in the compressor. Or you don't need to be as strict as you would with an expander. There is therefore no need to provide radial sealing means as described in US Pat. No. 3,994,686.

In the somewhat simplified longitudinal cross-sectional view shown in FIG.
The end surface 55 is the inner surface 5 of the orbiting scroll member 57 of which the orbiting scroll end plate 31 is a part.
6 , which forms a peripheral area 58 for the liquid to be pumped to enter through the peripheral port 59 . FIG. 61 shows in more detail and detail how both scroll members are assembled into a scroll pump. In the other even-numbered figures, i.e., figures 8, 10, . . . , 20, only the wrap of the scroll element and the portion containing the port mechanism are shown; I want to be understood.

The cycle I am going to explain is the center pocket 52.
It shall begin from the time when the is in a sealed state. At this point, pockets 50 and 51 are also sealed. Liquid is discharged through a discharge manifold means consisting of ports 23 and transfer passages 24. In this mode of operation, the central pocket 52 functions as a dispensing area.As shown in FIGS. 5 and 6, the pockets 50 and 51 are at their maximum volume, and are located between the lap flanks and between the lap end face and the end plate. If the slight gap between the pockets 50 and 51 and the center pocket 52 is ignored, the space between the pockets 50 and 51 and the center pocket 52 is completely sealed. Concave transfer passage 2 on end plate
Let us assume that neither 4 nor 39 is provided. The effect in this case can be seen from FIGS. 7 and 8. FIGS. 7 and 8 show the wrap position at the time when the orbiting scroll member has completed one-eighth of the total amount of revolution, and the direction of revolution is indicated by a dashed arrow. pockets 50, 51, and 5
The volume of 2 begins to decrease. Since the liquid in the pump is substantially incompressible, it passes from pockets 50 and 51 to pocket 52 through the relatively narrow passages 60 and 61 created by the movement of the laps.
through which it is forced under pressure.
Furthermore, the relative dimensions of central pocket 52 and discharge port 23 are sized to accentuate this effect. Therefore, the pressure inside the device increases, which has a very negative effect on the hardware of the scroll device, and creates strong impact pressure, resulting in inefficient and noisy operation.

This undesirable situation is substantially avoided if the inner surfaces of the stationary and orbiting scroll members are provided with concave transfer passageways 24 and 39, respectively. As can be seen in FIG. 8, these transfer passageways are contoured and arranged so that they open substantially immediately after pocket 52 is closed. These transport passages 24 and 39, which were previously blocked by the position of the lap, are therefore opened with continued movement of the pivot lap. Transfer passages 24 and 39
are large enough to increase passageways 60 and 61 to provide sufficient flow capacity to reduce pressure build-up inside the pocket and to avoid pulsation of liquid through port 23. It's getting deeper and deeper. (Liquid flow is indicated by solid arrows in the figure.) As can be seen in Figures 9-14, the transfer passage 24
and 39 from pockets 50 and 51 to pocket 5
2 remains open to create a substantially pulse-free flow of liquid into the 2. The volume of pockets 50, 51 and 52 is then reduced to provide a smooth discharge through discharge port 23 for these passages until they become essentially one central pocket.
As the total volume of pockets 50, 51 and 52 decreases, liquid begins to flow from peripheral region 58 into pockets 65 and 66, called "open" pockets, formed between the scroll wraps. These pockets 65 and 66 are open in the sense that they are in direct communication with the surrounding area 58. As can be seen in FIGS. 9 and 10, after the first quarter of the stroke, the passages 60 and 61 formed by the movement of the wraps become larger and the transfer passages 24 and 39 become larger. is fully open and liquid is free to pass into the central pocket 52 and further through the discharge manifold means. Passages 60 and 61 are the 11th
As shown in Fig.-14, it continues to expand until half of the application is completed. Transfer passages 24 and 39 are connected to pockets 50,
Although conduction continues to occur between 51 and 52, it is no longer necessary to pass a significant amount of liquid and it gradually closes due to the movement of the orbiting scroll member. As can be seen in Figures 15-20, as the turn progresses, the center pocket 52 becomes what can be considered an independent pocket after about 3/4 of the turn, and the "open" pockets 65 and 66 become attached to the periphery. It is now sufficiently insulated from the area 58 that it can be considered that new outer pockets 50 and 51 have been formed, although they open towards the peripheral area 58 from the diminishing passages 67 and 68. .

When passages 67 and 68 are closed, central pocket 52
A new cycle begins with all closed pockets, including , at maximum liquid volume, reproducing the conditions shown in FIGS. 5 and 6. As long as passages 67 and 68 are open to the surrounding area,
Transfer channels 24 and 39 are closed. However, as discussed above, substantially at the same time as these pockets are closed, the port mechanism of the present invention is activated.

Figures 21-24 illustrate stationary and orbiting scroll elements incorporating the porting mechanism of the present invention and suitable for use in scroll-type pumps in which liquid flows radially outwardly from a central pocket to a peripheral region. . The stationary scroll element 70 of FIG. 21 consists of an end plate 71 and an involute curved lap 72 integral with or fixed to the inner surface 73. The wrap 72, like the wrap 12 of FIGS. 1 and 2, begins at a contact line 74 and ends at a contact line 75, forming an involute curve of one and a half turns. Wrap 72 has an outer flank surface 76, an inner flank surface 77, and an end surface 78. A central boss 79 is provided on the outer surface 80 of the end plate 71 . Liquid port 81 connects end plate 71 and boss 7
It extends through 9.

A concave transfer passage 85 is provided on the inner surface 73 of the end plate 71. As shown in the top view of FIG. 21, the main inner boundary 86 of the transfer passageway 85 is such that the stationary scroll element 70 and the orbiting scroll element 90 (FIGS. 23 and 24) have the greatest extent between the flank surfaces of their laps. It conforms in shape to the inner flank surface 95 of the involute trap 92 of the orbiting scroll element 90 when oriented to produce four point contact. This main boundary line 86, like the boundary line 27 of the inner passage 24 in FIG. 1, is thus a partial locus of the edge of the involute trap of the associated scroll elements. Another major boundary of the transfer passageway 85, an outer major boundary 87, is spaced radially outwardly from the inner boundary 86 and is shaped to follow the contour of the boundary 86. Border lines 86 and 87 are connected via a fusion radius 88 . Preferably, the spacing between boundaries 86 and 87 is approximately twice the thickness of the involute trap of the scroll element. The transfer passageway 85 is thus an arcuate recess adjacent to or a short distance from the end of the wrap 72 and approximately 45
It extends along an arc with an angular range of ~90 degrees. Because the transfer passageway 85 is located outside the involute trap, it will be referred to as the "outer" passageway for convenience.

The orbiting scroll element 90, shown in top and cross-sectional views in FIGS. 23 and 24, respectively, consists of an end plate 91 and an involute curved lap 92 integral with or fixed to the inner surface 93. The wrap 92 begins at the contact line 74 and ends at the contact line 75, forming an involute curve of one and a half turns. Wrap 92 has an outer contact flank surface 94, an inner flank surface 95, and a contact end surface 96.
A concave transfer passage 97 corresponding to the stationary scroll element transfer passage 85 is provided on the inner surface 93 of the end plate 91. As shown in the top view of FIG. 23, the main inner boundary 98 of the transfer passageway 97 is defined when both scroll elements are oriented to produce a maximum of four points of contact between the flank surfaces of their laps. , is adapted in shape to match the partial trajectory of the edge of the inner flank surface 77 of the involute trap 72 of the stationary scroll element 70. The main outer border 99 of the transfer passage 97 has the same contour as the main inner border 98 and these borders are connected by a fusion radius 100. The shape and size of the transfer passage 97 corresponds to those of the arcuate concave transfer passage 85 of the stationary scroll member.

The manner in which the scroll element port mechanism shown in Figures 21-24 provides substantially pulsation-free pumping action will now be described in detail with reference to Figures 25-40. In this case the scroll elements move the liquid radially outward. As with Figures 5-20, Figures 25-40 show the various positions of the scroll elements during one cycle of pumping, with the odd numbered figures being in a plane perpendicular to the centerline of the device. Figure 1 is a cross-sectional view of the wrap taken at , and each successive even-numbered figure is a corresponding longitudinal cross-section of the wrap. In FIGS. 25-40, in order to clearly show the open and closed states of the recessed transfer passages 85 and 97, the longitudinal plane cutting through the scroll member is the concave transfer passage 85.
and 97 are rotated around the center line in each figure.

In FIG. 26, scroll elements 70 and 90 are the sixth
It is shown that it is built into a scroll pump in the same manner as shown in the figure. Stationary scroll element 70 is attached to a housing plate 105 having an annular projection member 106. The annular projection member 106 forms a contact surface 107 for the inner surface 93 of the projection 108 of the orbiting scroll member. A peripheral liquid region 110 is formed inside the enclosed region created in this way, and a peripheral region 1
A port 109 (which may be one or more ports) is provided through housing plate 105 to provide a liquid conduit between housing plate 10 and a liquid reservoir (not shown). In the operation described below, the liquid flows radially outward to port 10.
9 functions as a liquid ejection port for the peripheral ejection area thus created. Stationary scroll member port 81 is therefore an inlet manifold. When the wrap is in the position shown in Figures 25 and 26, there are two closed outer pockets 111.
and 112 and a central pocket 113.

The operation of the port mechanism of the present invention is shown in detail in Figures 25-40. Let us take the starting point of the cycle at the time when each pocket 111, 112 and 113 is in its minimum volume state, isolated from each other, just before it begins to increase in volume. As with the port mechanism described with reference to Figures 1-20, the lap flanks should be spaced, for example, approximately 0.001 to 0.005 inches (0.025 to 0.025 inches) to avoid flank wear.
There is always a slight gap of 0.127mm). Again, assuming first that arcuate concave transfer passages are not provided in end plates 71 and 91, when the orbiting scroll is driven in the direction indicated by the dashed arrows in FIGS. It will be seen that the liquid therein will be subjected to increasing pressure. This is because the openings 115 and 116 (FIG. 27) created by the relative movement of the orbiting scroll wrap 92 with respect to the stationary scroll wrap 72 are not large enough to open the pockets 111 and 112. The problem is that the flow rate of the liquid flowing into the peripheral area 110 is not large enough, which causes excessive pressure on the liquid in the pockets 111 and 112. This can result in pressure pulsations and damage to the scroll hardware.

However, if concave transfer passages 85 and 97 are present, a further liquid flow passage occurs almost immediately after pockets 111, 112 and 113 are closed.
That is, the transfer passages 85 and 97 augment the passages 115 and 116 created by the relative movement of the orbiting scroll lap with respect to the stationary scroll lap, thereby increasing the flow of liquid causing pressure pulsations. Unreasonable pressurization can be avoided.

As can be seen in Figures 27-32, transfer passages 85 and 97 are closed by the time the orbiting scroll member has completed three-eighths of its orbital stroke. This is because by this point liquid passages 115 and 116 are at approximately their maximum state, transfer passages 85 and 97
This is because there is no longer a need to reinforce passages 115 and 116. Of course, central pocket 113 gradually came to include what was part of pockets 111 and 112;
The liquid pressure inside the pocket 113 will be well controlled as more liquid is drawn into the pocket 113. As can be seen, as the pivoting stroke progresses, the outline of the numbered pockets in FIGS. Become. However, for purposes of clarity, the reference numerals from FIGS. 25 and 26 are also used in FIGS. 27-40 and in the discussion relating to these figures.

Passages 115 and 116 between laps 72 and 92
is effectively at its maximum when the pumping action is 4/3 of the way through the cycle, as shown in FIGS. 35 and 36. For this purpose, the transfer channels 85 and 97
may be in a substantially closed, ie, inactive state. Pockets 111 and 11 during the last 1/4 stroke of one cycle (Figures 37-40)
A small amount of liquid remaining in the surrounding area 110
and when one cycle is completed, passages 115 and 116 are closed. It is apparent from Figures 33-40 that the port conditions achieved by the relative movement of the swirling lap to the stationary lap are sufficient to obtain pulsation-free liquid flow and discharge. Because of this condition, transfer passages 85 and 97 remain closed. When one cycle is completed, pockets 111, 112 and 113 are isolated from each other as shown in Figure 25 and are in position to begin the next cycle.

As can be seen from the foregoing description of the operation of the liquid port mechanism of the present invention, the location and shape of the concave liquid transfer passages are such that the concave liquid transfer passages can be pivoted into positions to form three substantially completely blocked liquid pockets. Almost immediately after the utrap reaches mid-swivel cycle, the concave liquid transfer passage opens and at least the liquid discharge area (whether central or peripheral) formed by the movement of the swirl wrap is opened. The concave liquid transfer passageway is located and shaped so that it remains open until the liquid passageway for conducting liquid therein is sufficiently large to prevent appreciable pressure pulsations from occurring within the scroll pump. It's summery.

In many scroll-type liquid pump applications, pumps designed to flow radially outward are preferred over pumps designed to flow radially inward. Efficient operation is generally achieved in outward flow pumps because the hydraulic pressure within the pump tends to hold the scroll members engaged. Additionally, larger discharge port means can be obtained if desired by providing multiple ports spaced from each other around the peripheral area. These factors contribute to a more effective reduction or elimination of pulsating flow through use of the port mechanism of the present invention.

It is also within the scope of the present invention to provide both central (inner) and peripheral (outer) concave transfer passages in the end plates of the scroll elements as shown in Figures 41-44. Stationary scroll element 1 of Figures 41 and 42
20 is shown in FIGS. 1 and 2 or 21 and 22.
As in the case of the scroll element shown, the end plate 121
and a wrap 122 in the form of an involute curve of one and a half turns. Scroll element 120 has a central port 123, a centrally located concave transfer passage 124 of the same shape as passage 24 of FIG.
It has a concave transfer passage 125 located at the periphery and having the same shape as the passage 85 in FIG. Similarly, the orbiting scroll element 130 of FIGS. 43 and 44 has an end plate 131 and a wrap 132 in the form of an involute curve of one and a half turns, as in the scroll element of FIGS. 3 and 4 or 23 and 24. and has. Scroll element 130 has a centrally located concave transfer passage 133 and a peripherally located concave transfer passage 134 of the same size and shape as shown in FIGS. 3 and 23, respectively.

Figures 45-60 are cross-sectional views of the same type as Figures 25-40, and the longitudinal cut planes used to create even-numbered cross-sectional views such as Figures 46 and 48 are of the transfer passage. It has been rotated to show how it opens. Scroll-type liquid pumps incorporating the scroll elements of Figures 41-44 may be used to flow liquid radially inwardly from a peripheral region toward a central discharge region or from a central pocket radially outwardly toward a peripheral discharge region. It can also be used to flow towards an area. The sequence shown in Figures 45-60 indicates the former of these modes of operation, ie, the radially inward mode of operation. But the 45th-
Viewing 60 in a different order, these figures can also be viewed as the operation of the port mechanism in the latter, radially outward, mode of operation, as discussed below. Therefore, in order to use Figures 45-60 to indicate both modes of operation, the arrows indicating liquid flow in the first inward mode are marked with the numeral 1 followed by the letters a, b, ..., h. They are distinguished by enclosing them in a circle. Each letter indicates each step in one cycle of pump action in order, and the application stroke progresses in steps of 1/3 in the order of a, b, c, etc., as in the previous diagrams. There is. Arrows indicating flow in the second outward mode are distinguished by the number 2 followed by the letters a, b, . . . , h in a circle. In this case as well, the pumping action progresses in the order of letters a, b, c, . . . , but as will be described later, in this case the figure must be searched in the order of these letters.

FIG. 46 shows the scroll member of FIGS. 41-44 incorporated into a liquid pump in the same manner as in FIG. 26, and like reference numerals have been used for like elements. As can be seen from Figure 45,
Assume that the cycle begins when outer pockets 135 and 136 and center pocket 137 are closed differently.

The following description relates to the first mode of operation, ie, the mode in which the liquid flows radially inward. Look at Figures 45-56 and replace these figures with Figure 5.
- As can be seen by comparing with Figure 16,
central and peripheral concave transfer passages (124, 13
3, 125 and 134) operate similarly to a port mechanism having only a central transfer passageway. i.e. 41st-44th
In the illustrated liquid pump having stationary and orbiting scrolls and operating to move liquid radially inward, central transfer passages 124 and 13
3 is the central passage 14 created by the movement of the lap.
0 and 141, thereby increasing the flow rate through the discharge port 123 and creating a state in which no pulsating flow occurs. During the first 5/8 cycles of pumping, the peripheral transfer passages 142 and 143 created by the lap movement are large enough to admit liquid into the scroll. is unnecessary and remains inactive. However, while the orbiting scroll member moves between 5/8 and 3/4 cycles of its orbiting motion (55th
58), the orbiting scroll wrap is moved to open the peripheral transfer passages 125 and 134;
Pocket 1 opened through the peripheral passage for this purpose.
The flow rate of liquid into 44 and 145 is increased.
The opened pockets 144 and 145 are preliminary pockets that will eventually become pockets 135 and 136. This increased flow rate of liquid into pockets 144 and 145 provides a smoother flow of liquid into the scroll, thereby providing a more uniform flow rate of fluid through the scroll. As can be seen in Figures 57-60, these peripheral transfer passageways 124 and 183 remain open and operative until the cycle is complete. When the cycle is complete, pockets 135 and 13
6 is closed as shown in FIGS. 45 and 46.

To follow the sequence of operation of the port mechanism of the present invention when it functions in the second mode, that is, the mode that displaces liquid radially outward, start with Figures 45 and 46 and then proceed to Figures 45 and 46. The figures must be followed backwards from figures 59 and 60 to figures 47 and 48. Peripheral transfer passages 125 and 134 are in the second
Peripheral wrap passages 142 and 143 are increased as in the case shown in Figures 7-30. During this period, center pocket 137 will be replaced by pockets 135 and 13.
6, and there is no problem in electrical conduction between these pockets. As fluid flows into the central pockets, pockets 135, 136 and 137 become increasingly distinct, and the presence of central transfer passageways 124 and 133 prevents fluid from entering these nascent pockets. The fluid pressure on the lap is increased to flow smoothly and maintain good line contact between the flanks of the lap. This differentiation of pockets 135, 136 and 137 continues from Figures 55 and 56 to Figures 47 and 48, and as central wrap passageways 140 and 141 continue to decrease, the open central transfer passageway continues. 1
24 and 133 are responsible for delivering smooth, non-pulsating liquid to the inlet port 123 and central pocket 137.
This becomes even more important as it leads into pockets 135 and 136 via. When these pockets are closed, as shown in FIGS. 45 and 46, the scroll wrap is ready to begin the next cycle, reopening peripheral transfer passageways 125 and 134 to discharge liquid into peripheral area 138. It is becoming a state.

Although it is possible to operate the scroll member of FIGS. 1-4 or 21-24 in a radially inward or radially outward mode, most applications, especially large scroll-shaped devices, are relatively For high speed operation, it is preferred to use a scroll member having both a central or inner concave transfer passage and a peripheral or outer concave transfer passage, as shown in Figures 41-44.

FIG. 61 is a longitudinal sectional view of a scroll-type liquid pump incorporating the scroll element and port mechanism of the present invention. The illustrated scroll member is the fourth scroll member.
61 is shown incorporating the scroll element shown in FIGS. 2-44 at the point in time shown in FIGS. 51 and 52 during the pumping cycle. In FIG. 61, the same reference numerals have been used to designate the stationary and orbiting scroll components and the pockets formed thereby as were used in FIGS. 41-44 and 51 and 52.

The pump of FIG. 61 has stationary scroll element 12
A stationary scroll member 150 consisting of a stationary plate 151 to which 0 is fixed, and an orbiting scroll element 13
an orbiting scroll member 152 consisting of a pivot plate 153 to which 0 is fixed, a coupling member 154, a drive mechanism indicated generally by reference numeral 155, a crankshaft assembly means indicated generally by reference numeral 156, an oil sump 158, a cooling fan 159 and cover 160
A housing 157 including a housing 157.

The end of the stationary plate 151 of the stationary scroll member has a peripheral annular projection 165 and an outwardly extending flange 1.
66, and these portions of plate 151 form part of the housing of the device. The stationary plate 151 also has a central columnar projection 167 that forms a liquid passageway 168. The liquid passage 168 is directly connected to the central port 123 of the stationary scroll;
Both constitute a liquid conduit means which functions as a liquid inlet or a liquid outlet depending on the selected mode of operation. Stationary scroll element 1
The boss 79 of 20 extends into the protrusion 167,
It is sealed by an O-ring 169. A thread 170 is formed on the inside of the central post 167 for engaging a liquid conduit (not shown). Further, at least one columnar projection 175 is provided at the peripheral portion of the stationary plate 151, and each peripheral columnar projection 157 forms a liquid inlet or a liquid discharge port 176 that communicates with the peripheral region 138. A thread 177 is provided for engaging a conduit (not shown).

The diameter of the orbiting plate 153 of the orbiting scroll member is
The pivot plate 153 is large enough so that it always extends beyond the inner edge of the flange 166 so that, if desired, an oil seal ring 18 can be inserted between the plate 153 and the flange 166.
0 can be placed to isolate the scroll pocket from the rest of the device. By doing so, the drive mechanism and the bearings can be lubricated with oil while the working fluid remains substantially unmixed with other liquids. In applications where the pumped liquid itself can function as a lubricant, oil seal ring 180 may be omitted.

The housing, generally designated by the numeral 157, includes an annular projection 165 of the stationary scroll member and a flange 166.
and a main housing portion 181. The main housing portion 181 has a flange 182 and is integral with a lower sump housing 183.
The housing 157 has a plurality of bolts 184 and 1
It is fixed and sealed to the scroll member via flanges 166 and 182 using two O-ring seals 185.

During operation of the pump, the angular relationship between the two scroll members must be maintained constant, and this is achieved using the coupling member 154. 61st
The coupling member shown in the embodiment of the device shown in the figure is US Pat.
It is substantially the same as the coupling member described in No. 3994638 (see FIG. 14 of that patent and its detailed description). As can be seen in FIG. 61, the coupling member consists of a ring 190. One side of the ring 190 is provided with opposing keys 191 which are slidably engaged in keyways 192 provided on the inner surface of the flange 182 of the housing. A second pair of keys (not shown) are provided oppositely on the other side of the coupling ring 190, and are arranged on the opposite side of the plate 1 of the orbiting scroll member.
It is slidably engaged with a keyway (not shown) provided in 53. Another example of a suitable coupling member is described and claimed in U.S. patent application Ser.

The orbiting scroll member 152 has a columnar shaft 195 fixed to the orbiting plate 153 or integral with the orbiting plate 153. The orbiting scroll member is driven by a motor (not shown) that is external to the housing and engages the compressor shaft 196.
The shaft 196 extends into the housing through an oil seal 197, and its end reaches a crank plate 198. The crank plate 198 is the shaft 1
96 or integral with the shaft 196. Shaft 196 is mounted within the housing by shaft bearing 199 and crank bearing 200.

The drive means for the scrolling device was provided by John E.
It is the same as that described in U.S. Patent Application No. 761,889, filed in the name of McCullough, and is a fixed radius crank mechanism. The orbiting scroll member is fixed to a drive shaft 196 via a bearing mount 201. The mount 201 has a counterweight 202 for the purpose of balancing the centrifugal force of the orbiting scroll member. Bearing mount 201 engages columnar shaft 195 via needle bearing 203 which is held in place by a snap spring (not shown). A thrust bearing 205 is sandwiched between the bearing mounting base 201 and the outer surface of the orbiting scroll plate 153 of the orbiting scroll member. and acts as an axial force applying means to achieve the desired axial seal. Thrust face bearing 205 transmits the load from orbiting scroll member 152 via crank bearing 200 substantially to the housing.

Main shaft 196, crank plate 198, bearing mount 201, and counterweight 202 constitute the adjustable fixed radius drive mechanism of the scroll pump of the present invention. As previously mentioned, the viscosity of the liquid used in a liquid pump is greater than the viscosity of the gas used in a compressor or expander, and the volume ratio is maintained at unity in a liquid pump, so this is why the scroll lap It is possible to operate with a small gap between the flank surfaces of the For this purpose, it is possible to use a fixed radius crank to drive the orbiting scroll member, with a predetermined gap between the flank surfaces. Thus, when securing the orbiting scroll member to the crank plate 198, an adjustment is made in the position of the lap of the orbiting scroll member relative to the lap of the stationary scroll member. This positions the bearing mount 201/counterweight 202 assembly relative to the crank plate 198 using a pivot pin 206 and a locking screw extending through the slot 208 of the bearing mount 201/counterweight 202 assembly to the threaded portion of the crank plate 198. (preferably 4
This is done by making adjustments using the book). This mechanism is shown in detail in FIG. 7 of patent application no. 761,889. In the embodiment shown and described in FIG.
The assembly is shaped so that it can be moved along a small arc before being secured to the assembly.

FIG. 61 shows an adjustable fixed radius crank, but a non-adjustable fixed radius crank, i.e. bearing mounts 201 so as to provide the desired clearance between the wraps of the rotating and stationary scroll members. /Balance weight 202
It is also possible to use a fixed radius crank that is designed and constructed such that the assembly is permanently fixed to the crank plate 198 from the beginning. In such a structure, the bearing mounting base 201/
Place the counterweight 202 assembly on the crank plate 1.
At least two screws such as those shown in FIG. 8 of US Pat.

It has been found that by leaving gaps between the laps of the scroll member, lap wear is greatly reduced or eliminated and special lap mechanisms are not required. In operation, the clearance between the flanks of the scroll members is preferably maintained at about 0.001 to 0.005 inches (0.025 to 0.127 mm).
There are several ways to create gaps between laps. One method is to place a thin metal shim between the laps with a thickness equal to the gap when assembling the device, and remove the shim after tightening the set screw 207. Another method is to measure the swirl radius of the scroll member during a trial assembly and set the drive crank assembly's swing radius to this measurement minus the desired flank clearance. Whatever the design and dimensions of the liquid pump,
What radius of gyration (equal to the distance between the axis 210 of the machine and the axis 211 of the orbiting scroll member)
operate the device to determine what is desirable;
It is then generally advantageous to set the bearing mount 201 for a radius of gyration that is slightly less than the radius of gyration where line contact occurs between the laps.

The actual size of the gap that ultimately remains between the laps will typically depend, at least in part, on the size of the liquid pump and the viscosity of the liquid being pumped. Generally, the larger the device and the more viscous the liquid, the larger the gap can be.

As mentioned in the general description of the device shown in FIG. 61, a sump 158 is provided in the lower portion 183 of the device housing. Oil sump 158
Lubricant oil 212 within the coupling member 154 is supplied to the various shafts and drive bearings within the coupling member 154 and the housing 157 by at least one oil finger 213 fixed to the coupling member 154.
The length of the oil finger is such that the oil finger periodically dips into the oil 212 and is then lifted to blow the oil upwardly into the housing. It circulates through the housing and returns to the oil sump. Housing cavity 2 surrounding the crank plate and bearing mount
An oil passage 214 is provided for guiding a portion of the oil blown directly into the shaft bearing 199 . The liquid being pumped can itself act as a lubricant, so that oil-sealing 1
If 80 is not provided, there is no need to provide an oil finger as the entire interior of the housing will normally be filled with liquid.

Under operating conditions, such as pumping hot liquids, it is preferable to air cool the pump housing and provide means for cooling the pump elements and circulating lubricating oil through the housing. Such means are shown in FIG. An air duct 216 leading to a duct cover 217 is mounted around the housing of the device and is supported on the drive end of a plurality of housing fin members 218. Cooling air is circulated through the air duct by fan 159. Juan 15
Reference numeral 9 denotes a plurality of fan blades 219 attached between the rim 220 that contacts the belt on the outer periphery of the pulley 222 and the ring 221 that engages with the shaft on the inner periphery.
Consists of. The pulley 222 is connected to the keyway 22 of the shaft 196.
4 is attached to the main shaft 196 via a key 223 that engages with the key 223. The duct cover 217 is fixed to the scroll member side end of the housing fin member 218, and covers only a part of the scroll member side end. This leaves a series of air discharge openings 225 uncovered so that the air introduced by the fan 159 is circulated around the device housing from the drive end to the scroll member end. is discharged through.

A liquid pump having stationary and orbiting scroll elements as shown in FIGS. 1-4 was constructed as shown in FIG. 61. Sealing ring 180 and oil finger 2
13, the housing cooling means was omitted. The pump operates at 900rpm and is SAE20 hydro
It was found that it pumps liquid oil with approximately the same efficiency as a gear pump with approximately the same capacity. The pump operated quietly, with no pressure pulsations.

When operating a pump, it may be desirable to submerge the pump itself in the liquid being pumped. Although there has not been a great demand for such pumps in the past, there has been an increasing demand in recent years for small pumps that can be submerged in the fuel tanks of automobiles or other self-propelled vehicles that use light fuels. Such pumps must be able to be completely immersed in the pumped fuel, such as gasoline or diesel oil, in order to be efficient. The reason behind the recent increase in demand for pumps having such characteristics is the demand for attachment of a release control device. Using this emission control device increases the temperature under the hood, where the fuel pump was previously located. Rising temperatures create steam that can clog the fuel pump, but this problem can be solved by placing the fuel pump in the fuel tank to isolate it from excessive temperatures and by connecting the fuel pump to the engine via high-pressure fuel lines. easily solved by

Placing the pump in the fuel tank of an automobile places as many demands on a pump that can be immersed in liquid as any other method of use; therefore, the pump of the present invention has the following characteristics: The detailed description assumes that it is used for such purposes. However, the pump of the present invention can also be used for liquids other than fuel oil.
It is capable of operating in environments other than in the liquid being pumped, and can be of any size, such as one that is larger than that consistent with the size constraints imposed on a pump when placed inside an automobile fuel tank. You will understand what is possible.

Additionally, the development of electronically controlled fuel metering systems to increase the efficiency of engine operation has placed additional demands on fuel pumps. This metering system requires high fuel delivery pressures that cannot easily be generated with the simple centrifugal pumps traditionally used in tank installations.

Among the requirements that fuel tank pumps must meet for use in passenger cars are that they must operate efficiently and reliably without maintenance for long periods of time, say 2000 hours;
185 pounds or approximately 31 gallons (84Kg or approximately
120) at a pressure of 12psig (gauge pressure 0.8Kg/ ^cm2 ), operates with a 12V DC motor with a maximum current of 6.3A, and can run for at least 10 minutes even when the tank is empty. . Additionally, the pump must be self-starting, operate with minimal noise, vibration, and output flow vibration, and be sized to pass through the opening of the vehicle's fuel tank. This means that the maximum pump diameter cannot exceed 17/8 inches (4.76 cm). The manufacturing cost of the pump must also be low. It will be readily appreciated that the types of pumps commonly used - centrifugal or conventional positive displacement pumps - are unlikely to meet all of these requirements. Therefore, it is necessary to look to other types of pumps for this purpose. It has been found that scroll-type liquid pumps meet all the requirements listed above and additionally offer very important advantages.

One embodiment of a scroll-type liquid pump of the present invention suitable for submersion into the fuel being pumped is shown in longitudinal cross-section in FIG. 62. The pump includes a main housing 240, a liquid inlet 241,
Liquid outlet 242 and scroll pump means 2
43, joint means 244, orbiting scroll drive means 245, motor means 246, and axial load support means 247. In the following detailed description of immersion pumps, it may be convenient to first discuss the motor and liquid outlet. This is because these elements of the pump are of more or less conventional design. Motor means 246 is an electric motor having an armature 248;
It consists of a stator magnet 249 located and retained within central housing portion 250 between a bearing housing 521 (described below) and skirt 252 of discharge end block 253. Armature 248 is mounted on drive shaft 254 and face commutator 255 is also mounted on drive shaft 254. Commutator 255 contacts carbon brushes 256 to which electrical connections are made via opposed screw terminals (see also FIG. 63) 257 extending outwardly from the pump housing. ing.

Liquid outlet 242 comprises a discharge conduit 258 in a discharge end block 253. A check valve 259 is provided in the discharge conduit 258 to prevent liquid from flowing back through the pump when the pump is not operating and during start-up. The check valve 259 shown in FIG. 62 has a ball 260.
is placed on the elastic ring 261 supported on the annular ring support 262, and the ported plate 26
Spring 26 held within conduit 258 by 4
It is held by 3. Of course spring 263
The strength of is the given fluid pressure for the fuel pump in a car's gas tank, for example about 1 psig
The valve 259 is strong enough to open when subjected to a gauge pressure of 0.07 kg/cm ² . pressure relief valve 26
5 is also provided. The relief valve 265 is the 62nd
It is shown in the figure to have a similar structure to the discharge valve 259. That is, it consists of a ball 266, a seat ring 267, a ring support 268, a spring 269, and a ported spring holding plate 270. The strength of spring 269 is selected to maintain relief valve 265 closed until the pressure inside the housing reaches a predetermined maximum hydraulic pressure, such as 12 psig (0.84 Kg/cm ² gauge pressure). The discharge and relief valves 259 and 265 shown in FIG. 62 are merely examples, and it is of course within the scope of the present invention to use any other suitable valve means.

The end of the drive shaft 254 is located inside the central recess 271a of the discharge end block 253, and the drive shaft 25
4 is supported and positioned by a shaft bearing 271. The main counterweight 272 is attached to the shaft 254 in order to counteract the forces created in a direction perpendicular to the axis of the pump due to the eccentricity of the pivoting element.
mounted on top. Main counterweight 27
In order to achieve complete dynamic balance by canceling the moments generated by 2, it is necessary to provide secondary counterweight means. In the embodiment shown in FIG. 62, this secondary counterweight is achieved either by incorporating a suitably located weight within the face commutator 255 or by distributing the weight suitably within the armature 248. provided.

Figures 64 and 65 show an alternative embodiment of the pump discharge end block and means for making the electrical connection to the motor. The discharge end block 273 has a stepped shape and its end is in the form of a skirt-like ring portion 274 which is sealed against the central housing portion 250 via a sealing ring 275 inside the pump. . Ring 274 functions to retain magnet 249 inside the pump. Carbon brushes 276 in contact with commutator 277 are held by opposed brush retainers 278 that extend through discharge end block 273 to connect with terminals 279. The end of the drive shaft 254 is within the recess 280 and the drive shaft 254 is positioned and supported by a bearing 281.

In the embodiment of FIG. 64, a separate secondary counterweight 282 is mounted on shaft 254. As can be seen from the top view shown in FIG. 65, the valve-controlled discharge conduit 283 and pressure relief valve 284 of FIG. 64 are of similar construction to those described with reference to FIGS. It is also provided for the embodiment.

In FIG. 62, the flow of liquid within the pump is indicated by arrows. Liquid enters through the suction port 241 and is pumped by the scroll pump 243 from the scroll pump chamber 285 to the housing 2.
40, flows around the motor and exits through valve 259. The pumped liquid thus acts as a lubricant and coolant for the pump components.

The scroll pump, the port mechanism, the axial load support means, the coupling means and the drive means for the scroll pump are illustrated in detail in Figures 67-77, where like elements are given the same references in these figures. numbered.

As can be seen from FIG. 66, the scroll pump 243 consists of a stationary scroll member 287 and an orbiting scroll member 288. Stationary scroll member 287 consists of an end plate 289 and an involute curved lap 290 that is either integral with an inner or opposing surface 291 of end plate 289 or attached to a separate member on inner surface 291 (e.g. (See U.S. Pat. No. 3,994,635). End plate 2
Around the 89 are keyways 2 spaced at uniform intervals.
92 and a key 293 (66th key) fixed to the inner wall of the bearing housing portion 251.
) to maintain the stationary scroll member fixed within the pump.

The end plate 289 of the stationary scroll member functions as the inlet side end face of the pump housing, and the end plate 289
a central boss 294 (FIG. 66) forming a suction conduit 295 configured to communicate liquid to the central region of the scroll pump through a central port 296 at 9;
have. As can be seen in FIG. 67, the stationary scroll element 287 is connected to the concave passage 12 of FIG.
4 and 125 respectively in terms of shape and function. It has an inner concave liquid transfer passage 296 and an outer concave liquid transfer passage 297. In this embodiment, the central port and the inner recessed liquid transfer passageway are one and the same. As an alternative embodiment, the central port of stationary scroll member 287 may be circular in shape and the inner concave liquid passageway may be in the same shape as shown in FIG.

As can be seen from FIG. 67, the orbiting scroll member 288 has the same shape as the stationary scroll member 287. The orbiting scroll member 288 is connected to the end plate 2
98 and fixed to the inner surface 300 of the end plate 298.
or an involute curved lap 299 integral with the inner surface 300. The lap 299 has an outer flank surface 301 and an inner flank surface 302.
and an end surface 303. As can be seen in FIG. 67, the orbiting scroll element 288 has an inner concave liquid transfer passageway 304 and an outer concave liquid transfer passageway 305 which correspond in form and function to the concave passageways 138 and 134 shown in FIGS. 43 and 44. and has.

The operation of the scroll pump of FIG. 62 is the same as that previously described, with moving pockets 306, 307 and 308 (FIG. 66) being formed by driving the orbiting scroll member 288. Changes in the volume of these pockets and in the fluid communication between the pockets cause fluid to move through the pump. As can be seen in FIG. 66, the peripheral discharge area 309 of the pump extends around the scroll involute trap and further around the end plate of the rotating scroll member.

The viscosity of liquids is much higher than that of gases, and the volume ratio in the pump is not more than 1.
, the effective radial seal between the pockets at the respective contact surfaces 337 and 303 of both laps need not be particularly stringent. As will be discussed in more detail in the following discussion of pump operation, the back pressure of the liquid flowing through the pump is sufficient to create the axial force necessary to urge the wrap and end plate into contact. In addition, the liquid flowing radially outward through the pump exerts a hydraulic pressure inside the pump that presses the flanks of the wraps of the scroll members together in a sealing direction when the flanks of the laps of the scroll members are in line of travel contact. arise. Pulsation-free operation of this immersion pump is accomplished in a manner similar to that described with respect to the scroll element of Figures 41-60.

The drive means, axial compressive load support means, and coupling means are shown in Figures 66-68. In the embodiment shown in these figures, the axial compressive load support means comprises a thrust ball bearing, generally designated 312. The thrust ball bearings 312 have a plurality of ball bearings 313 spaced apart at a desired distance by two parallel ball retaining rings 314 and 315 having equally spaced holes 316 shaped to receive the balls 313. It is shaped like it is being held. Retaining ring 31
4 and 315 are held apart by contact with the surface of ball 313, thereby forming a plurality of radial liquid passages 317 between them, allowing liquid to be discharged around the periphery. Scroll pump chamber 285 through passage 317 from region 309
flows into the The main load acting on the scroll member is a compressive load caused by liquid discharge pressure,
This load is supported by a thrust ball bearing 312 as an axial load supporting means. Scroll member wear is therefore minimized and pump life extended. Because the axial load support means can minimize wear on the scroll members, the pump of the present invention can be operated at considerably higher discharge pressures, thereby providing good sealing of the scroll, High efficiency enables operation with minimum power consumption.

During operation, two scroll members 287 and 2
The angular relationship of 88 must remain constant. This is accomplished through the use of a coupling member shown generally at 244 in FIG. 6th
The coupling member 244 shown in FIGS. 6 and 68 is substantially the same as the coupling member described in U.S. Pat. No. 3,994,633 (see FIG. 14 of that patent and its description). As can be seen in FIGS. 66 and 68, the coupling member consists of a ring 318 with keys 319 placed oppositely on one side, these keys 319 being located on the inner surface of the annular portion 321 of the bearing housing 251. It is slidably engaged with a keyway 320 provided. (The longitudinal cross-sectional view shown in FIG. 66 corresponds to the angled plane 66-66 shown in FIG. 68.
It is understood that only one set of the two pairs of keys 319 and keyways 320 provided facing each other is shown in FIG. 66 (see FIG. 62). I want to be ) second pair of keys 32 oriented 90 degrees offset from key 319
2 are provided facing each other on the opposite side of the coupling ring 318 and the orbiting scroll member 28
It is slidably engaged with a key groove 323 provided in the end plate 298 of No. 8. The coupling member 244 functions as a spring to provide an initial axial preload to the orbiting scroll member during pump start-up.

As discussed below in connection with Figures 72-77,
It is also possible to combine the functions of the axial load support means and the coupling means into one device component.

The orbiting scroll member driving means is shown in FIGS. 66 and 6.
This is shown in detail in Figure 8. As can be seen in FIG. 66, the drive shaft 254 is supported by a main shaft bearing 324 held within a shaft bearing housing 325. The shaft bearing housing 325 includes an outer annular ring portion 321, an inner bearing housing 326, and an inner annular ring portion 32.
7 and through the external main bearing housing 251
and become one. The end of the drive shaft 254 is formed into a flat short shaft 328, and this short shaft 328 fits into the keyway 329 of the orbiting scroll drive yoke 330.
(Fig. 68). With this construction, the orbiting scroll member is pushed outwardly by centrifugal force and hydraulic pressure until its involute wrap contacts the involute wrap of the stationary scroll member. be moved to.
In this moved position, the center 33 of the yoke 330
1 is spaced from the center 332 of the drive shaft 254 by a distance equal to the radius of orbit of the orbiting scroll member.
The drive yoke 330 is mounted in a scroll drive bearing 333 supported in a scroll drive bearing support ring 334 that is integral with the outer surface 335 of the pivoting school member 288 .

All-metal passages (drive yoke 330 and short shaft 328 and drive shaft 25
4) is formed by this scroll drive means.
The drive mechanism is designed to minimize friction losses by providing bearings, and is designed to minimize overturning moments on the orbiting scroll member and loads on the motor bearings. Due to this structure, the pump can withstand dry running, has high efficiency, and has a long service life.

As can be seen in FIGS. 66 and 68, the outer annular bearing housing ring 321 has a number of equally spaced liquid ports 336 that allow liquid to flow from the peripheral discharge area 309 to the scroll pump chamber. Motor room 28 through 285
It can flow into 6.

Figures 69-71 are partial longitudinal cross-sectional views of the inlet/scroll pump end of the pump, showing further three axial load support means in a pump incorporating independent coupling means; Examples are shown. In the embodiment of FIG. 69, scroll members 287 and 288 themselves function as axial load supporting means. namely, the lap 290 of the stationary scroll member and the orbiting scroll member.
and 299, when their respective contact end surfaces 337 and 303 contact the opposing surfaces of the end plates of the mated mating scroll members, i.e., the surface 300 of the pivoting end plate 298 and the surface 291 of the stationary end plate 289, respectively; Contact end surfaces 337 and 30
3 supports the load. The embodiment of Figure 69 is generally suitable for pumps requiring moderate discharge pressures.

The axial load support means shown in FIG. 70 consists of an annular thrust bearing 338 having a plurality of radial passages 339 extending therethrough. Flat surfaces 340 and 341 of thrust bearing 338 contact opposite surfaces 291 and 300 of the stationary and orbiting scroll members, thereby redirecting the axial compressive load of the pressurized liquid in the pump. The signal is transmitted to the thrust bearing. The thrust bearing is preferably made of an organic plastic, such as polyimide, and is preferably used in a pump in which the scroll member is also made of an organic plastic.

The embodiment of FIG. 71 is a modification of the embodiment of FIG. 70 in which an annular thrust bearing is used, but the thrust bearing is
An annular ring protrusion 3 integrated with the inner surface 291 of 7
It is made in the shape of 42. A number of spaced radial passages 343 are provided in the ring projection 342 to provide the necessary fluid communication between the discharge region 309 and the pump chamber 285. The axial load is applied to the surface 300 of the orbiting scroll end plate.
is supported by a flat surface 344 that is in contact with.

Figures 72-74 show a modification of the pump of the invention in which the axial load support means also function as the coupling means. The load bearing means includes surfaces 291 and 30 of the end plates of the stationary and orbiting scroll members.
It is adapted to move circularly within circular recesses 346 and 347 provided at 0, respectively.
It consists of a plurality of equally spaced spheres 345.
Balls 345 are maintained in radial and circumferential position by a ball retainer ring 348 having a through hole 349 therein. Figure 73 shows depression 3 when the scroll element is at one point in its orbital cycle.
46 and 347 are schematically shown. As can be seen from this figure, recesses 346 and 347 in the stationary and orbiting scroll members
The centers of the scroll members are located on the circumference of the same radius and coincide with the axial direction at a point in one cycle when all the tangent lines of both scroll members are parallel.

The dimensions of recesses 346 and 347 relative to the diameter D _s of the sphere and the radius of gyration R _p of the orbiting scroll member are shown schematically in FIG. 74. The ball 345 is
During one turning cycle, half the turning radius, or R
It must be able to travel a distance equal to _p /2. Therefore, the depression 346 (or 34
If the depth of 7) is equal to the radius R _S of the sphere, then the diameter D _I of the depression must be D _S +R _O. However, since the depth of recess 346 is less than R _S , D _I must also be slightly less than D _S +R _O . FIG. 74A shows a cross-sectional shape of the depression, and FIG. 74B shows a top view.
However, it is also within the scope of the invention to cut a recess with a suitable diameter in the form of a recess with beveled edges and straight sides.

FIG. 74C is an enlarged cross-sectional view of the recess and retainer ring, showing the end plate 298 of the orbiting scroll member.
It is intended to show how the involute trap (and the involute trap secured thereto) is free to pivot within the stationary scroll member while maintaining the desired angular relationship to the stationary scroll member.
The balls 345 have the same role as the multiple thrust ball bearing of FIG. 66 in that they support the axial compressive load on the scroll member, and therefore
The pump embodiment shown in FIG. 2-74 has the same excellent operating performance as the embodiment of FIG. 66. In the absence of a separate coupling member, a spring washer 350 is placed between the drive yoke 330 and the shoulder of the shaft 254 to keep the scroll axially preloaded during start-up.

Figures 75-77 show a modified version of the pump of the invention in which the coupling means also function as load-bearing means.
A coupling means, generally designated 351, is located between the end plates 289 and 298 of the stationary and orbiting scroll members. The coupling member is an annular ring 352 which is connected to the pivot end plate 29.
Two keys 353 are arranged facing each other and are slidably engaged with key grooves 354 provided in the surface 300 of 8.
and two opposing keys 355 oriented perpendicular to the keys 353 for sliding engagement in keyways 356 provided in the surface 291 of the stationary end plate 289 . As can be seen in FIGS. 76 and 77, the coupling member has a series of equally spaced supports 357. Support stand 357
flat surfaces 358 and 359 engage opposing scroll end plate surfaces 291 and 300;
Functions as axial compressive load support means. Further, a plurality of liquid passages 360 are provided in the joint member. As in the modified version of FIG. 72, a washer 350 is provided to create an axial preload during start-up.

In the embodiment of the pump shown in Figures 78-80, spherical members are used as keys for the axial compressive load support means and coupling means. The joint member is the 75th
It consists of an annular ring 361 having a support base 362 and a liquid passage 363, similar to the case of the joint ring 351 shown in FIG. However, there is no key on the coupling ring. A groove 364 is provided in the surface 365 of each support platform 362 that faces the surface 300 of the pivot end plate 298 . A groove 366 is provided in the face 300 of the end plate which corresponds in shape and axial direction to the groove 364 in the support platform. A load-bearing ball 367 (bearing member) is located within each pair of opposed grooves 364 and 366 to undergo joint motion.
The sum of the depths of the paired grooves is slightly less than the diameter of sphere 367. The edge-to-edge length of grooves 364 and 366 is less than or equal to D+R _o (D is the diameter of sphere 367). Similarly, grooves 368 are formed in the surface 370 of the support base 362 and the opposing surface 291 of the end plate 289 of the stationary scroll member.
and 369 (Figs. 79 and 80), and within each of these paired grooves a ball 371 is provided.
is positioned to receive joint motion. Groove 36
The longitudinal axes of 8 and 369 are grooves 364 and 366.
The axis is rotated 90 degrees. Balls 367 and 371 therefore support the axial compressive loads acting on the scroll members and, by constrained movement along the axis of the paired grooves in which they are placed, support the orbiting and stationary scroll members. maintaining the desired angular relationship between.

The axial load support and coupling means shown in Figures 81-88 is a modification of the means shown in Figures 78-80, using rollers instead of balls as the load support and coupling means. The coupling member has the same general shape as that of Figures 78-80 and is an annular ring 361 having equally spaced supports and fluid passageways 363 around its periphery. Four support stands 372 separated by 90 degrees from each other are combined with joint means. The remaining support platform 373 functions only as an axial load support means. Support stand 372
The surface 37 opposite the surface 300 of the pivoting end plate 298 of
4 is provided with a groove 375. Surface 300 is likewise provided with four corresponding grooves 376, allowing rollers 377 to run in a closed track formed by the two grooves. The sum of the depths of grooves 375 and 376 is slightly less than the diameter of the roller, and the travel distance of the roller is equal to the radius of gyration (R _o ). A groove 378 is also provided in a surface 379 of the support base 372 that faces the surface 291 of the end plate 289 of the stationary scroll member. Similarly, four grooves 380 corresponding to the grooves 378 are provided on the surface 291. As shown in FIGS. 81 and 83, the relationship between the orientations of the grooves 378 and 380 and the orientations of the grooves 375 and 376 is such that the axis of the roller 381 running in the grooves 378 and 380 is 90 degrees from the axis of the roller 377.
They form an angle of degrees. 78th
As with balls 367 and 371 in FIGS. 81 and 79, the modified rollers shown in FIGS. 81 and 82 have both axial load-bearing and joint functions.

A method of using the pump of the present invention is shown in FIG. The pump is immersed in the liquid to be pumped 382, which is contained in a tank 383, such as an automobile fuel tank. Pump outlet 2
The high pressure pipe 384 fixed to 42 is connected to the tank 383
It exits through a suitable outlet 385 provided in the housing and is adapted to be connected to a desired liquid receiver, such as a car vaporizer. Similarly screw terminal 257
A shielded wire 386 connected to exits through outlet 385 and is adapted to be connected to a power source. The filter 387 is the suction means 241 of the pump.
It is attached to a tank and is designed to filter out debris that may be present in the liquid or accumulate at the bottom of the tank.

Pumps constructed in accordance with the present invention are self-starting and can be left running dry for relatively long periods of time, such as 10 minutes or more, without loss of performance. The pump has minimal operating noise, vibration and vibration in the output flow, and dust entry will not cause permanent damage due to the radial compliance of the drive. The direction of liquid flow within the scroll member automatically creates a seal between the flanks of the scroll lap and a radial seal. The pump of the invention therefore does not require additional radial sealing means or means for counteracting the centrifugal forces acting on the orbiting scroll member.

Due to the unique flow pattern of the liquid within the pump, shown by the arrows in Figure 62, all components of the pump are completely automatically lubricated, and a simple one-way valve and pressure relief combined with the liquid delivery means. No valve means other than the valve is required.

The pump of the invention is particularly suitable for placement in a motor vehicle fuel tank. This means that the pump is small enough to fit through the inlet of an automobile's fuel tank (the maximum diameter of the pump is 17/8 (4.76 cm)), and the pump has a displacement of 12 psig (gauge pressure).
It is capable of delivering at least 185 pounds (84 Kg) of fuel per hour at a pressure of 0.844 Kg/cm ² ). Furthermore, the components of the scroll pump can be made (e.g., by molding) of suitable wear-resistant organic plastics, and the other pump components can also be made of similar plastics or metals. , can meet the demand for low cost for such an immersion fuel pump.

The initial objective was effectively achieved. Moreover, since the structure described above may be modified to a certain extent without departing from the scope of the invention, all that is shown in the above description and the accompanying drawings is by way of example only, and the invention is not limited thereto.

[Brief explanation of the drawing]

1 and 2 are top views of one embodiment of a stationary scroll element constructed in accordance with the present invention, particularly suitable for use in an inwardly directed scroll liquid pump. and a cross-sectional view. 3 and 4 are top and cross-sectional views of an orbiting scroll element for use in combination with the stationary scroll element of FIGS. 1 and 2; FIG. 5-20 show alternating lateral and longitudinal cross-sectional views of the stationary and orbiting scroll elements of the embodiment of FIGS. 1-4; The operation of the discharge port located in the center is shown. 21 and 22 are top views of another embodiment of a stationary scroll element constructed in accordance with the present invention, particularly suitable for use in a scroll-type liquid pump with outwardly directed liquid flow. FIG. 2 is a diagram and a sectional view. 23 and 24 are top and cross-sectional views of an orbiting scroll element for use in combination with the stationary scroll element of FIGS. 21 and 22; FIG.
Figures 25-40 show alternating lateral and longitudinal cross-sections of the stationary and orbiting scroll elements of the embodiment of Figures 21-24; The operation of the discharge ports located at the periphery is shown. Figures 41 and 42 are
FIGS. 2A and 2B are top and cross-sectional views of yet another embodiment of a stationary scroll element constructed in accordance with the present invention having both central and peripheral discharge ports and through which liquid may flow inwardly and outwardly; FIGS. be. 43 and 44 are top and cross-sectional views of an orbiting scroll element for use in combination with the stationary scroll element of FIGS. 41 and 42; FIG. Figures 45-60 show alternating lateral and longitudinal cross-sections of the stationary and orbiting scroll elements of the embodiment of Figures 41-44, with liquid directed inwardly or Figure 3 illustrates the operation of the discharge port of this embodiment when flowing outwardly. FIG. 61 is a longitudinal cross-sectional view of a scroll-type liquid pump constructed in accordance with the present invention. FIG. 62 is an enlarged longitudinal cross-sectional view of a scroll-type liquid pump constructed in accordance with the present invention, particularly suitable as an automotive fuel pump in which the pump is immersed in fuel; FIG. 63 is a plan view of the discharge end of the pump of FIG. 62; Figure 64 is the 6th
2 is a partial longitudinal cross-sectional view of a modified version of the pump of FIG. 2, showing further means for forming an electrical connection with the motor and further means for forming a secondary counterweight; FIG. . FIG. 65 is a plan view of the discharge end of the pump of FIG. 64. FIG. 66 is an enlarged longitudinal cross-sectional view of the suction side end of the scroll-type liquid pump of the present invention, showing the driving and coupling means, the scroll member, the port mechanism, and the axial load supporting means. Shown in detail. Figure 67 shows
The pump of Fig. 66 is placed perpendicular to the axis of the machine.
FIG. 6 is a cross-sectional view taken along plane 67-67 of the figure. 6th
FIG. 8 is a cross-sectional view of the pump of FIG. 66 taken along plane 68--68 of FIG. 66, perpendicular to the axis of the machine. 69, 70 and 71 show the axial load supporting means (66) of the pump of FIG. 66.
This figure shows three types of embodiments (other than the embodiment shown in the figures), all of which are separate elements from the joint member. Figure 72 shows an embodiment in which the axial load support means and the coupling member are combined into one device component. FIG. 73 is a cross-sectional view of the apparatus of FIG. 72 taken along plane 73-73 of FIG. 72, showing the location of each of the thrust ball bearings used. FIG. 74 details, in plan and cross-sectional view, the factors involved when using the thrust ball bearings of FIGS. 72 and 78. Figure 75 shows another embodiment in which the axial load support means and the coupling member are combined into one device component. 76 and 77 are a plan view and a sectional view, respectively, of the axial load supporting and coupling means of FIG. 75. Figure 78 shows
FIG. 3 is a further embodiment of the axial load bearing and coupling means, in which the ball member performs the dual functions of load bearing and coupling; FIG. 79 and 80 are a plan view and a sectional view, respectively, of the axial load supporting and coupling means of FIG. 78. FIG. 81 is a modification of the axial load support/coupling means of FIG. 78 in which the rollers perform the dual functions of load support and coupling. 82 and 88 are a plan view and a sectional view, respectively, of the axial load supporting and coupling means of FIG. 81. 8th
FIG. 4 is a sectional view of a tank containing liquid for immersing the pump of the invention. 10, 70, 120 and 287... stationary scroll elements, 11, 71, 121 and 289...
...stationary end plates, 12, 72, 122 and 290...
...Stationary involute trap, 13, 73 and 291 ...Stationary end plate inner surface, 16, 17, 76, 7
7,290a and 290b...flank surface, 1
8, 78 and 337...Lap end face, 20,7
9 and 294...Central boss, 23,81 and 123...Liquid port, 24,85,124,1
25, 296 and 297...stationary concave transfer passages, 25, 27, 86 and 87...concave transfer passage main boundaries, 30, 90, 130 and 288...
... Orbiting scroll element, 81, 91, 131 and 298 ... Orbiting end plate, 32, 92, 132 and 299... Orbiting involute trap, 33,
93 and 300...Swivel end plate inner surface, 34,3
5, 94, 95, 301 and 302...flank surface, 36, 96 and 303...lap end surface,
39, 97, 133, 134, 304 and 30
5...Swivel concave transfer passage, 40, 42, 97 and 98...Concave transfer passage main boundary line, 50, 51,
111, 112, 135, 136, 306 and 307...outer liquid pocket, 52, 113, 1
37 and 308...Central liquid pocket, 5
8, 110 and 309... peripheral area, 59 and 109... peripheral port, 65, 66, 144
and 145... open pocket, 150... stationary scroll member, 152... orbiting scroll member, 154... joint member, 155... drive mechanism,
156... Crankshaft assembly means, 157...
... Housing, 158 ... Oil reservoir, 159 ... Cooling fan, 160 ... Cover, 196 ... Drive shaft, 198 ... Crank plate, 201 ... Bearing mounting base, 202 ... Counterweight, 240 ...
...Main housing, 241 ...Liquid inlet, 242
...Liquid discharge port, 243...Scroll pump means, 244 and 351...Joint means, 245
... Orbiting scroll drive means, 246 ... Motor means, 247 ... Axial load support means, 254 ...
...drive shaft, 258 and 283 ...discharge conduit, 2
59...Check valve, 265 and 284...Pressure relief valve, 272 and 282...Balance weight, 285...Scroll type pump chamber, 292,
320, 323, 354 and 356...Keyway, 293, 319, 322, 353 and 35
5...Key, 312...Thrust ball bearing, 328
... short shaft, 330 ... orbiting scroll drive yoke, 338 ... annular thrust bearing, 342 ... annular ring protrusion, 345, 367 and 371 ...
Ball, 346, 347... recess, 350... spring washer, 352 and 361... annular ring, 35
7,362,372 and 373...Support stand, 3
81...roller, 383...tank, 384...
High pressure piping.

Claims (1)

[Scope of Claims] 1. A paired scroll member suitable for incorporation into a scroll-type liquid pump, comprising: (a) a stationary scroll member having a central liquid port, comprising: (1) a stationary end plate; (2) a stationary involute trap fixed to one side of the stationary end plate and having the shape of an involute curve of one and a half turns; (3) a stationary involute trap provided on the one side of the stationary end plate; (b) an orbiting scroll member arranged to be pivoted relative to the stationary scroll member by a drive means, the orbiting scroll member comprising: 1) a swiveling end plate; (2) a swiveling involute trap fixed to one side of the swiveling end plate and having the shape of an involute curve of one and a half turns; an orbiting scroll member comprising an orbiting concave liquid transfer passage provided on one side, the position and shape of the stationary and orbiting concave liquid transfer passages being such that the orbiting involute trap is characterized in that the passages are positioned and configured to open and allow liquid to flow substantially immediately after reaching a point in the swirl cycle forming three essentially closed liquid pockets. Paired scroll members. 2 a first major boundary line of the stationary concave liquid transfer passageway is in the form of a partial locus of the swirling involume trap edge; Paired scroll members according to claim 1, in the form of a partial trajectory of the utrap edge. 3 said stationary and swirling concave liquid transfer passages are (1) located inside said stationary and swirling involute traps, respectively, and in a straight line passing through the center of said stationary and pivoting end plates, respectively; and (2) a straight line parallel to the contact line drawn as a tangent to the generation radius of the rotating involute trap, or (2) outside the stationary and rotating involute traps, respectively. and (3) a curved line located at the stationary and 3. The paired scroll members of claim 2 located both inside and outside the orbiting involute trap. 4. The depth of the concave liquid transfer passageway is approximately equal to the thickness of the involute wrap, and the second major boundary of the outer concave liquid transfer passageway is separated by a distance equal to about twice the thickness of the wrap. 4. The paired scroll member of claim 3, wherein the outer concave transfer passageway extends along an arc of approximately 45 to 90 degrees. 5. A positive displacement liquid pump comprising: (A) paired scroll members comprising: (a) a stationary scroll member having a central liquid port; (1) a stationary end plate; (2) the stationary scroll member; (3) a stationary involute trap fixed to one side of the end plate and having the shape of a one-and-a-half turn involute curve; (3) a stationary concave liquid transfer passage provided on the one side of the stationary end plate; (b) an orbiting scroll member arranged to be rotated relative to the stationary scroll member by a driving means, comprising: (1) an orbiting end plate; (2) a rotating involute trap fixed to one side of the rotating end plate and having the shape of an involute curve of one and a half turns; (3) a rotating involute trap provided on the one side of the rotating end plate; a swirling concave liquid transfer passage; and the positions and shapes of the stationary and swirling concave liquid transfer passages are such that the swirling involute trap is adapted to the nature of the orbiting cycle. (B ) axial force applying means for forcing the scroll members into axial contact; (C) coupling means for maintaining a fixed angular relationship of the scroll members; and (D) liquid suction. (E) rotating the orbiting scroll member so that the side flanks of the involute trap and the end plate form a moving liquid pocket of varying volume; A positive displacement liquid pump, characterized in that it comprises a combination of driving means for forming a peripheral region around the periphery of the pump and a discharge region. 6 a first major boundary line of the stationary concave liquid transfer passageway is in the form of a partial locus of the swirling involume trap edge; 6. Positive displacement liquid pump according to claim 5, in the form of a partial trajectory of the utrap edge. 7 said stationary and swirling concave liquid transfer passages are (1) located inside said stationary and pivoting involute traps, respectively, and in a straight line passing through the centers of said stationary and pivoting end plates, respectively; (2) a straight line parallel to the contact line drawn as a tangent to the generation radius of the rotating involute trap; (3) a curved line located and having the same shape as the first principal boundary and radially outwardly spaced from the first principal boundary; or (3) the stationary and rotating 7. A positive displacement liquid pump according to claim 6, wherein the pump is located both inside and outside the involute trap. 8. The depth of the concave liquid transfer passageway is approximately equal to the thickness of the involute wrap, and the second major boundary of the outer concave liquid transfer passageway is separated by a distance equal to about twice the thickness of the wrap. 8. The positive displacement liquid pump of claim 7, wherein the outer concave transfer passageway extends along an arc of about 45 to 90 degrees. 9. The liquid inlet is (1) in communication with the peripheral area, and the liquid outlet is in communication with the liquid pocket;
(2) is electrically connected to an inner pocket of the liquid pockets, and the liquid ejection port is electrically connected to the peripheral region that functions as the ejection region; A positive displacement liquid pump according to claim 5. 10 A small gap is maintained between the side flanks of the involute trap as the drive means pivots the orbiting scroll member, thereby maintaining the substantial integrity of the liquid pocket while maintaining 6. A positive displacement liquid pump according to claim 5, wherein said drive means are arranged such that wear on said side flanks is substantially eliminated over a period of operation. 11. The drive means comprises: (a) a drive shaft whose end is in the crank plate and is rotatable on the axis of the machine; (b) extending from the orbiting scroll member and having a bearing mount and counterweight means; (c) a short shaft which is fixed and rotatable on an axis spaced parallel to the machine axis by a distance equal to the radius of orbit of the orbiting scroll member; 11. A positive displacement liquid pump according to claim 10, comprising a fixing means for fixing to a plate in a predetermined relationship to form said spacing. 12. A positive displacement liquid pump according to claim 11, wherein said axial force applying means comprises a thrust bearing acting between said bearing mount and counterweight means and said end plate of said orbiting scroll member. 13 Suitable for being immersed in the liquid to be pumped up, and forming a chamber containing the scroll member therein, having a liquid inlet at one end thereof and a liquid discharge outlet at the other end thereof. the drive means further includes a motor disposed within the chamber between the scroll member and the liquid outlet end of the housing; so that liquid flowing radially outwardly through the pump pumped by the scroll member flows around the drive means to exert a predetermined liquid pressure in the chamber to provide the axial force applying means. 6. A positive displacement liquid pump according to claim 5, wherein the positive displacement liquid pump is maintained internally. 14 a pressure-controlled one-way pump including a pressure relief valve, the liquid outlet being arranged to cause liquid to be discharged from the chamber when the liquid pressure within the pump reaches a predetermined magnitude; 14. Positive displacement liquid pump according to claim 13, comprising a discharge conduit associated with a valve. 15. A positive displacement liquid pump according to claim 13, including axial compressive load support means. 16. A positive displacement liquid pump according to claim 15, wherein said coupling means and said axial compressive load support means are a single element that functions as a coupling and load support means. 17. The positive displacement liquid pump of claim 13 including further axial force applying means for urging the orbiting scroll member into contact with the stationary scroll member during start-up. 18. A patent claim comprising primary counterweight means for counteracting forces produced in a direction perpendicular to the axis of the pump and secondary counterweight means for counteracting moments produced by the main counterweight means. A positive displacement liquid pump according to scope item 13. 19. The drive means is spaced parallel to and from the axis of the drive shaft, the end of which is in the form of a short shaft, by a distance equal to the radius of orbit of the orbiting scroll member during operation of the pump. 14. The positive displacement liquid pump according to claim 13, comprising an orbiting scroll member drive yoke. 20. The short shaft and the drive yoke are made of metal and form a metal-to-metal contact, so that there are no defects in the orbiting scroll member drive means, especially when the pump is running idle. 20. A positive displacement liquid pump according to claim 19, forming an effective heat transfer path for dissipating generated heat.