EP0534891B1

EP0534891B1 - Scroll compressor with dual pocket axial compliance

Info

Publication number: EP0534891B1
Application number: EP92630087A
Authority: EP
Inventors: Jeffrey J. Nieter; Anthony J. Marchese; Raymond L. Beblois; Thomas R. Barito
Original assignee: Carrier Corp
Current assignee: Carrier Corp
Priority date: 1991-09-23
Filing date: 1992-09-17
Publication date: 1996-04-17
Anticipated expiration: 2012-09-17
Also published as: KR930006329A; DE69209955T2; JPH05202865A; AU2529592A; AU650570B2; DE69209955D1; KR960004246B1; EP0534891A1; MX9205379A; TW223674B; JP3004483B2; BR9203702A

Description

Technical Field

This invention relates to scroll compressors, and more particularly to improving axial compliance between scroll elements thereby achieving higher efficiency in scroll compressors.

Background of the Invention

Scroll compressors have a wide range of applications where low to moderate compression ratios are desired, especially in the air conditioning and heat pump industries. This acceptance is attributed to high efficiency, fewer parts, and less noise and vibration when compared with competing compressors. A conventional scroll compressor includes a motor, which drives a shaft with an eccentric crank, causing orbiting motion of an orbiting scroll element. The orbiting scroll element has a scroll or spiral shaped protruding wrap, which interacts with a similarly shaped protruding wrap on a mating fixed element. Compression is achieved when the meshing coaction between the two protruding wraps shifts the gaseous fluid radially inward and simultaneously reduces the volume of the fluid.
However, internal leakage of pressurized fluid reduces the efficiency of scroll compressors. There are two types of leakage associated with scroll compressors, one is flank leakage, and the other is tip leakage. In both cases, the fluid in higher pressure pockets escapes through the gaps into lower pressure pockets. Flank leakage occurs when fluid from a pocket formed between the two protruding mashing wraps escapes at the flank surfaces where they come into contact with each other. Tip leakage occurs when fluid escapes between the end surface of the protruding wrap of each element and the base of the other element as they come into contact. Tip leakage is the more severe of the two because the effective total leakage path width for tip leakage is typically several times larger than that for flank leakage. Further, the compression process produces large axial loads that push the orbiting scroll element axially away from the fixed scroll element, thereby increasing the tip leakage. In addition to the axial forces driving orbiting scroll element away from the fixed scroll, there is also an overturning moment attempting to tip the orbiting scroll element out of the plane with the fixed scroll element.
Since close-tolerance manufacturing techniques are not adequate to prevent the loss of pressure due to tip leakage, other methods have been developed. One approach is to utilize various types of tip seals, as described in U.S. Pat. Nos. 4,395,205; 4,411,605; 4,415,317; 4,416,597. The end surface of the protruding wrap of either scroll element is equipped with tip sealing means which reduce the tip leakage. Although this method is effective for sealing, it requires complicated manufacturing, increases friction, and raises costs.
Another approach to decrease tip leakage is to apply compensating back pressure to force mating elements together. Higher pressure fluid is purposely bled from the compression chamber through a vent port into a back chamber, which is typically a single, relatively large chamber located behind the orbiting scroll. This provides a body of pressurized fluid which pushes the orbiting element against the fixed element and thus, reduces the gap between the tips of the protruding scrolls and the bases of the elements. Reducing the gap minimizes the leakage of fluid, resulting in the increase of pressure in the compression chamber.
For example, U.S. Pat. Nos. 4,384,831; 4,600,369; 4,645,437; 4,696,630; and 4,861,245, each disclose a scroll compressor having such a back chamber. Commonly-assigned U.S. Pat. Nos. 4,992,032 and 4,993,928 also disclose scroll compressors using the back pressuring technique. As disclosed therein, rather than a single back chamber, two sealed pressure chambers, one at intermediate pressure and another at discharge pressure, are disposed behind the orbiting scroll element and are designed to counteract the gas compression forces within the compression chamber and to bias the orbiting scroll element toward the fixed scroll element. However, the prior art back pressuring technique is designed to overcome the highest overturning moment experienced during the orbiting cycle and leads to excessive thrust force over the remainder of the cycle. The large thrust force causes excessive friction between the two mating parts and results in reduced efficiency of the scroll compressors.
Additionally, U.S. Pat. No. 4,557,675 discloses a method of adjusting pressure in the back chamber by positioning pressure-equalizing ports so that the pressure vented into the back chamber varies with changes in operating conditions. However, the back pressure remains relatively constant during any given steady-state condition, thus, the change in pressure, as the operating conditions vary, is intended to overcome the highest overturning moment and axial force, resulting in excessive thrust force during the remainder of the cycle and causing excessive friction, thereby reducing the efficiency of the scroll compressor.

Disclosure of Invention

An object of the invention is to increase the efficiency of scroll compressors by reducing frictional forces between the scrolls.
According to the present invention, pressurized fluid is vented from the compression chamber into at least one dynamic back chamber through a port in the scroll element, so that the back pressure will vary on a sub-cycle basis. A dynamic back chamber, characterized by a relatively small volume of the chamber and a large flow area port for supplying pressure fluid thereto, is located behind the orbiting element. In accordance with this invention, an efficient means of counteracting the overturning moment without producing excessive friction forces may be achieved by varying the back pressure on a sub-cycle basis.
These and other objects, features, and advantages of the present invention will become more apparent in light of the detailed description of a best mode embodiment thereof, as illustrated in the accompanying drawing.

Brief Description of Drawing

FIG. 1 is a diagrammatic, side elevation view of a scroll compressor in accordance with the present invention;
FIG. 2 is a sectioned plan view illustrating the meshing of the protruding scroll wraps of the scroll compressor shown in FIG. 1 so as to form compression pockets therebetween; and
FIG. 3 is an enlarged, partial, sectioned view of a portion of the scroll compressor of FIG. 1.

Best Mode For Carrying Out The Invention

Referring now to FIGS. 1-3, a scroll compressor 10 includes a fixed scroll 11 which is engaged with an orbiting scroll 13. The orbiting scroll 13 is driven by a shaft 17 which is driven by motor 15 in orbital movement relative to the fixed scroll 11. Fluid compression is achieved as scroll wraps 18, 20 protruding from the orbiting scroll 13 and the fixed scroll 11, respectively, mesh to form a plurality of compression pockets 19 therebetween to trap volumes of fluid. This orbital action displaces the pockets of trapped fluid spirally inward while simultaneously reducing fluid volume of the pockets thereby compressing the fluid trapped therein.
As best seen in FIG. 3, a flow of pressurized fluid is bled through the ports 21, 23 into back chambers 25, 27, respectively. The fluid in these chambers produces back pressure which pushes the orbiting scroll 13 towards the fixed scroll 11 in order to reduce tip leakage and counteract overturning moment. However, the back pressure produced is not constant over the entire cycle. Instead, it varies during the cycle to follow the fluctuations in the overturning moment, which acts on the orbiting scroll 13 and causes it to tip with respect to the fixed scroll 11. Thus, the back pressure created is just enough to counteract the overturning moment. When the overturning moment is high, greater back pressure is available to hold the orbiting scroll in place to avoid leakage. When the overturning moment is low, the back pressure is also less and thus, does not cause excessive friction loss. This effect is attained by providing at least one dynamic chamber in which the pressure fluctuates in proportion to the overturning moment.
In the embodiment shown, there are two ports 21, 23 and two corresponding chambers 25, 27. Port 23 supplies pressurized fluid into the static chamber 27. Port 21 supplies pressurized fluid into dynamic chamber 25. The distinction between the two is that static chamber has a relatively constant fluid pressure throughout the entire cycle, while the dynamic chamber has widely varying fluid pressure during the cycle. The static port/chamber combination has a small port diameter and a large chamber volume. The dimensions are selected in such a way as to produce sufficient damping so that pressure is nearly constant throughout the cycle.
The variation of pressure on a sub-cycle basis in the dynamic chamber is attained by properly sizing the port diameter and chamber volume parameters relative to each other. The dynamic port/chamber pair has a large diameter port 21 and small chamber volume 25. The dimensions are selected in such a way as to produce very little damping so that the pressure in the dynamic chamber follows the compression process. This achieves the pressure variation on a sub-cycle basis.
It has been found that in order to maintain substantially constant pressure in the static chamber, the ratio of port diameter to the cubed root of chamber volume should be relatively small. In order to provide widely varying pressure in the dynamic chamber the ratio should be relatively large. For example, when a compressor designed with a static chamber having the ratio of .05 and dynamic chamber having a ratio of .22 was tested, it exhibits a roughly 45% reduction in net axial force.
Although the embodiment illustrated has one dynamic and one static chamber/port combination, other combinations are possible. This invention encompasses any number of dynamic chamber/port combinations that is one or more, with or without any number of static chambers. Since the total back pressure force on the scroll is the sum of the forces generated by the constant pressure in the static chamber and the varying pressure in the dynamic chamber, the total back pressure varies over the orbiting cycle instead of remaining constant, as in the prior art.
Also, one port may lead to more than one chamber and vice-versa, more than one port may lead into one chamber, as long as the appropriate ratios of effective port diameter/cubed root of effective chamber volume are maintained. Another variation that may yield substantially similar results is that back pressure may be applied to the fixed scroll, as opposed to the orbiting scroll, wherein the fixed scroll is able to move axially. Although the exact position of ports is not critical to this invention and may depend on characteristics of each compressor, the port location selection should utilize the pressure variation inside the compression chamber in order to produce sufficient pressure in the back chamber.
Although the invention has been shown and described with respect to a best mode embodiment thereof, it should be understood by those skilled in the art that the foregoing and various other changes, omissions, and additions in the form and detail thereof may be made therein without departing from the scope of the invention as defined in the claims.

Claims

A scroll compressor (10) for compressing a fluid, including a first scroll means (13) having a base including a floor portion and a spiral wrap portion (18) extending perpendicularly from said floor portion of said first scroll means (13), a second scroll means (11) having a base including a floor portion and a spiral wrap portion said extending perpendicularly from said floor portion of said second scroll means (11), said spiral wrap (18) of said second scroll means (11) being similarly shaped to said spiral wrap of said first scroll means (13), said second scroll means (11) positioned relative to said first scroll means (13) such that said spiral wraps (18) mesh with each other to form compression pockets (19) therebetween, means for moving said first scroll means (13) in an orbiting path relative to said second scroll means (11) so that fluid compression is achieved in said compression pockets (19), characterized by:
a dynamic back pressure chamber (25) having a volume and disposed behind said base of one of said first and second scroll means, said dynamic back pressure chamber having a first volume; and

means for venting fluid (21) from a first selected one of said compression pockets (19) at a selected location into said dynamic back pressure chamber (25), said means for venting having a first effective flow diameter with a ratio of said first effective flow diameter to the cube root of said first volume being on the order of at least 0.2, thereby establishing a dynamic pressure therein which substantially varies over an orbiting cycle of said first scroll means (13) in proportion to the overturning moment generated during the compression process thereby counteracting the overturning moment.
The apparatus of claim 1, further comprising:
a static back pressure chamber (27) disposed behind said base of at least one of said first and second scroll means, said static back pressure chamber (27) having a second volume; and

means (23) having a second effective flow diameter for venting fluid from a second selected one of said compression pockets (19) into said static back pressure chamber (27) thereby establishing a static pressure therein which remains relatively constant over an orbiting cycle of said first scroll means (13).
The apparatus of claim 2, wherein:
said means (21) for venting fluid from the first selected compression pocket into said dynamic back pressure chamber (25) comprises a first fluid passageway (21) through said floor portion of said at least one of said first and second scroll means (11), said first fluid passageway (21) having a first end opening to the first selected compression pocket and a second end opening to said dynamic back pressure chamber (25); and

said means (23) for venting fluid from the second selected compression chamber into said static back pressure chamber (27) comprises a second fluid passageway (23) through said floor portion of said at least one of said first and second scroll means (11), said second fluid passageway (23) having a first end opening to the second selected compression pocket and a second end opening to said static back chamber (27), said second fluid passageway (23) having a second effective flow diameter.
The apparatus of claim 3, wherein:
a ratio of the second effective flow diameter to the cube root of said second volume of said static back pressure chamber (27) is relatively small relative to said ratio of said first effective flow diameter to the cube root of said first volume of said dynamic back pressure chamber (25).
A scroll compressor (10) for compressing a fluid, including a first scroll means (13) having a base including a floor portion and a spiral wrap portion (18) extending perpendicularly from said floor portion of said first scroll means (13), a second scroll means (11) having a base including a floor portion and a spiral wrap portion extending perpendicularly from said floor portion of said second scroll means (11), said spiral wrap portion of said second scroll means (11) being similarly shaped to said spiral wrap portion (18) of said first scroll means (13), said second scroll means (11) being positioned relative to said first scroll means (13) such that said spiral wrap portions mesh with each other to form compression pockets (19) therebetween, means (17) for moving said first scroll means (13) in an orbiting path relative to said second scroll means (11) so that fluid compression is achieved in said compression pockets (19), characterized by:
a dynamic back pressure chamber (25) having a first volume located behind said base of one of said first and second scroll means;

a static back pressure chamber (27) having a second volume much larger than said first volume and located behind said base of at least one of said first and second scroll means;

a first fluid passageway means (21) for venting fluid from a first selected one of said compression pockets (19) into said dynamic back pressure chamber (25), said first fluid passageway means (21) having a first effective flow diameter with a first ratio of the first effective flow diameter of said first fluid passageway means to the cube root of said first volume of said dynamic back pressure chamber (25) being relatively large thereby establishing a dynamic pressure within said dynamic back pressure chamber (25) which substantially varies over an orbiting cycle of said first scroll means (13) in proportion to the overturning moment generated during the compression process thereby counteracting the overturning moment; and

a second fluid passageway means (23) for venting fluid from a second selected one of said compression pockets into said static back pressure chamber (27), said second fluid passageway means (23) having a second effective flow diameter with a second ratio of the second effective flow diameter of said second fluid passageway means (23) to the cube root of said second volume of said static back pressure chamber (27) being relatively small relative to said first ratio thereby establishing a static pressure within said static back pressure chamber which remains relatively constant over an orbiting cycle of said first scroll means.