JPH0240092A - Scroll type compressor - Google Patents

Abstract

PURPOSE: To prevent leakage between scroll members by supplying axial force on a back surface of an orbiting scroll member toward a cooperating fixed scroll member. CONSTITUTION: When a compressor is actuated, the axial response of an orbiting scroll member 50 toward a cooperating fixed scroll member 48 is effected when the compressor compresses refrigerant fluid and release it to a housing chamber 110. When the housing chamber 110 is pressurized, the released pressure occupies the volume in the radial inner side as seen from an inner wall 166. A seal element 158 is expanded toward the radial outer side. The scroll member 50 is moved to the axial upper side away from a thrust surface 55.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an airtight scroll compressor, in particular,
comprising fixed and orbital scroll members in mesh;
The present invention relates to a compressor in which it is necessary to apply an axial force biasing the orbiting scroll member in the direction of the fixed scroll member for special sealing between the two.

A typical such scroll compressor comprises two opposing scroll members, each having a spiral wrap, where each wrap is adapted to each other to define a number of closed pockets. There is. As one scroll member orbits relative to the other scroll member, the pockets move between the radially outer suction port and the radially inner discharge boat to transport and compress refrigerant fluid.

In general, scroll compressors have proven to be quiet, efficient, and low maintenance for a variety of refrigeration system applications.

However, several design problems remain for the scroll compressor to achieve wide market acceptance and commercial success.

For example, during operation of the compressor, the pressure of the compressed refrigerant at opposing surfaces between the scroll members provides a force that forces the scroll members axially apart. This axial separation of the scroll members results in leakage in closed pockets at opposing surfaces between the dump tip of one scroll member and the surface of the opposing scroll member. Such leakage reduces the operating efficiency of the compressor and, in extreme cases, renders the compressor inoperable.

Attempts in conventional scroll compressors to resist separation forces on the scroll members during compressor operation have not shown entirely satisfactory results in preventing the aforementioned leakage. not present. One approach is to pre-apply a force sufficient to resist dynamic separation forces to the scroll members in the axial direction of the scrolls. However, this approach results in high initial frictional forces between the scroll members and/or hair rings when the compressor is installed, making it difficult to start the compressor. Another conventional approach is to ensure high manufacturing accuracy for the components and to provide separation forces by thrust bearings.

However, this approach not only requires an expensive thrust hair ring (but also requires high manufacturing costs to maintain high manufacturing accuracy).

Other conventional scroll compressor designs shown in a number of prior patents include providing an intermediate pressure chamber behind the orbital scroll member, which absorbs the upward force that opposes the separation force. Occurs at intermediate pressures. In such a design, the suction pressure behind the orbital scroll member is not sufficient to counteract the separation force, while the discharge pressure behind the orbital scroll member creates an excessive upward force that forces the scroll tips and surfaces. resulting in premature wear. However, establishing an intermediate pressure between the suction pressure and the discharge pressure must introduce strong interference between the intermediate pressure pocket and the discharge pressure region. Such leaks result in the compressor losing its effective operating condition.

Some other conventional scroll compressor designs directed to controlling the upward force applied to the orbiting scroll member against the separation force utilize a combination of gas refrigerant at suction pressure and gas refrigerant at discharge pressure. and is exposed to each region on the rear side of the orbital scroll member. Such compressor designs utilize various sealing means to separate the gas pressure regions. For example, it is known to mount an annular sealing element on a stationary frame member adjacent the bottom surface of the orbiting scroll member, thereby extending the sealing element towards the bottom surface and providing a sliding seal thereto. There is. A problem with such a seal structure is that orbital movement of the scroll member relative to the seal element alters the distribution of axial forces on the scroll member, thereby causing undesirable movement.

Another axial accommodation mechanism for scroll compressors is that regions of the bottom surface of the orbiting scroll member are exposed to oil under discharge pressure and to refrigerant fluid under suction pressure. The regions are sealingly separated by a flexible annular sealing element disposed between the orbiting scroll bottom surface and a rotating thrust surface having a radially extending plate-like portion of the driven crankshaft.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems with scroll compressors, and provides an axial force on the orbiting scroll to provide convenient sealing and to prevent leakage between scroll members that fit together. The purpose is to prepare.

The present invention is able to resist the tendency of the scroll members to separate axially during compressor operation, and to provide an actual axial force on the bottom surface of the orbiting scroll member towards the cooperating fixed scroll member. Providing an improved axial accommodation mechanism ameliorates the drawbacks of conventional scroll compressors as described above, namely, in the present invention, the sealing material is moved from a fixed location on the backside of the orbiting scroll member to an adjacent Extending towards and slidably sealing against the stationary thrust surface, the sealing material is exposed to discharge and suction pressures, respectively, regardless of orbital movement of the stationary thrust plate toll member. An axial accommodation mechanism is provided for the scroll compressor separating between fixed positions on the back side of the scroll compressor.

Further, in one form of the present invention, there is provided a hermetic scroll compressor that includes a housing having a discharge pressure chamber and a suction pressure chamber.

The fixed and orbiting scroll members each include a wrap element that interlocks to compress refrigerant fluid when the orbiting scroll member is orbited relative to the fixed scroll member. '' The orbital scroll member includes a plate-like portion having a back surface adjacent a fixed thrust surface. A seal is disposed intermediate the back surface and the fixed thrust surface to provide an airtight separation between the locations of the back surface of the plate exposed to the discharge and suction pressure chambers. The `` symbol sealing material is fixed to the orbital scroll member and is slidably joined to the thrust surface, and regardless of the orbital movement of the orbit scroll member, the `` symbol sealing material determines each exposed portion of the rear surface of the `` symbol. ing.

One feature of the present invention is that the sealing material is interposed in the orbital scroll member, and the fixed thrust surface supports the annular sealing element in an unattached state within the annular sealing groove provided on the bottom surface of the plate member. The point is that it is a thing. Still another feature of the invention is that oil under substantially discharge pressure is provided in the annular seal groove to assist in urging the annular seal element into a sealing condition against the thrust surface. It is. Still another feature of the invention is that the sealing material forms a hydrostatic seal, in which oil under discharge pressure is supplied to the annular sealing groove and from there towards the thrust surface. , to realize sealing without using an annular sealing element. In each of the dual series sealing arrangements, the seal orbits the orbiting scroll member and determines the portion of the bottom surface exposed to discharge and suction pressures.

An advantage of the scroll compressor of the present invention is that the axial force applied to the orbiting scroll member for the purpose of axially aligning the orbiting scroll member towards the fixed scroll member is transmitted through the orbital movement of the scroll member. , are substantially the same, thereby reducing undesirable movement of the orbital scroll member about its central axis.

Another advantage of the scroll compressor of the present invention is that the sealing between the portions of the bottom surface of the orbiting scroll member exposed to discharge and suction pressures provides a fixed position of each portion during the orbital movement of said scroll member. is to be achieved in an acceptable manner.

Yet another advantage of the scroll compressor of the present invention is that the sealing between portions of the bottom surface of the orbiting scroll member that are exposed to discharge and suction pressures eliminates the need for sealing elements to be affixed to other compressor components. This is achieved with a simple seal without any seals, and the problem of positional seal leakage can be avoided.

Another advantage of the scroll compressor σ of the present invention is that, in one form, sealing between portions of the bottom surface of the orbiting scroll member exposed to discharge and suction pressures is present on opposing surfaces between the pressure regions. The point is that the release pressure is greater than the additional source of release pressure would be required.

Another advantage of the scroll compressor of the present invention is that the axial compliance of the orbiting scroll member in the direction of the fixed scroll member is effectively achieved without excessive leakage between the discharge pressure region and the suction pressure region of the compressor. It is at the point where it is done.

Yet another advantage of the scroll compressor of the present invention is that it is independently reliable, low cost and easy to produce a substantially determined axial force of the orbiting scroll member in the direction of the fixed scroll member. It is equipped with an axial adaptation mechanism that can be manufactured in a number of ways.

In one form, the scroll compressor of the present invention includes a gas-tight housing having a discharge pressure chamber under discharge pressure and a suction pressure chamber under suction pressure. Here, the fixed scroll member has a spiral fixed wrap element, and similarly the orbiting scroll member includes a plate-like portion having a front surface and a back surface. The surface has a spiral-shaped orbital wrap element thereon, whereby the stationary and orbital wrap elements establish at least one pocket of refrigerant fluid that is compressed by orbital motion of the orbital scroll member relative to the stationary scroll member. The fixed and orbital wrap elements are interlocked in such a manner. The fixed thrust surface is adjacent to the rear surface of the plate member. A sealing material is interposed in the orbital scroll, and the fixed thrust surface airtightly separates the back surface of the plate member exposed to the discharge pressure chamber and the suction pressure chamber. This seal sets each point on the back surface of the plate in its determined position despite the orbital movement of the orbiting scroll member. In addition, the said sealing material may be partially arrange|positioned in the sealing groove in the bottom surface of the said plate-shaped member, and may be an annular sealing element. In such a configuration, the annular seal element is preferably supported in the annular seal groove in an unattached state.

In one form, the invention further provides a hermetic scroll compressor having discharge and suction pressure chambers. Here, an oil sump is provided in the discharge pressure chamber. The stationary and orbiting scroll members also interlock to establish at least one pocket of compressed refrigerant fluid due to the orbital movement relative to the stationary scroll member. The bottom surface of the orbital scroll member has an annular seal groove formed therein. A surface to the fixed slab 1 is provided adjacent to the bottom surface of the orbiting scroll member. A sealing mechanism cooperating between the orbital scroll member and the stationary thrust surface is hermetically separated between each portion of the orbital scroll member exposed to discharge and suction pressures. The sealing mechanism sets locations on the bottom surface of the orbital scroll member in fixed positions despite the orbital movement of the orbital scroll member. In the above form of the invention, the sealing mechanism is operated by supplying oil fluid from the oil reservoir to the annular sealing groove. For example, oil is supplied to the grooves via axial passages in the crankshaft and via radial passages in the orbiting scroll member. One feature of the invention is that the sealing means is a hydrostatic seal provided by flowing oil from an annular sealing groove in the direction of the thrust surface.

Another feature of the invention is that the sealing mechanism is an annular sealing element partially disposed within the annular sealing groove. the sealing element extends from the groove toward the thrust surface;
It is in contact with here.

The oil in the annular groove provides a biasing force on the annular seal element toward the thrust surface.

Hereinafter, preferred embodiments of the present invention will be specifically described with reference to the drawings. In particular, as shown in FIGS. 1-3, the illustrated compressor has a housing designated by the numeral 12. The housing comprises a top cover plate 14, a central portion 16 and a bottom portion 1B, where the central portion 16 and bottom portion 18 may alternatively be constructed as an integral body member. The three nozzing parts are hermetically secured to each other by welding or brazing.

Attachment is such that a flange 20 is welded to the bottom 18 of the compressor for mounting the compressor in a vertically upward position. Disposed within the hermetically sealed nozzle 12 is an electric motor, generally designated 22, which includes a stator 24 and a rotor 26. Stator 2 above
4 is equipped with wings 28. The rotor 26 has a central hole 30 therein, into which a crankshaft 32 is mounted by fitting. The terminal cluster 34 is A
It is provided in the central portion 16 of the pufferfish 12 and connects the motor 22 to a power source.

Compressor 10 also includes an oil sump 36 located at its bottom 18. Centrifugal oil extraction tube 38
is the counter hole 4 at the lower end of the crankshaft 32.
The oil extraction tube 3 is press-fitted into the
8 is of conventional construction and includes a vertical paddle (not shown) therein. The oil inlet end 42 of the withdrawal tube 38 extends downwardly into the open end of a cylindrical oil cup 44, which provides a quiet area into which high quality, non-agitation oil is directed.

The compressor 10 includes a scroll compression mechanism 46 enclosed in the housing 12.

The compression mechanism 46 typically includes a fixed scroll member 48, an orbiting scroll member 50, and a main bearing frame member 52. As shown in FIG. 1, fixed scroll member 48 and frame member 52 are mounted together, with multiple attachments being attached to top cover plate 14 by means of ports 54. As shown in FIG. Accurate positioning between the fixed scroll member 48 and frame member 52 is accomplished by a pair of locating pins 56. The frame member 52 is provided with a plurality of mounting pads 58 to which the stator 24 of the motor is attached by means of bolts 60 to which the stator 24 is mounted.
4 and the rotor 26, an annular gap is provided between the rotor 26 and the rotor 26.

The fixed scroll member 48 has a flat plate 62 having a surface 63.
and a spiral locking wrap 6 extending axially from surface 63.
It is equipped with 4. Similarly, orbital scroll member 50 has a planar plate 66 having a back surface 51, a top surface 67, and a spiral orbital wrap 68 extending axially from said surface 67. The fixed scroll member 48 and the orbiting scroll member 50 are mated together so that the fixed pump 64 and the orbital wrap 68 are adapted to each other. Furthermore, the surface 63.67 and the holes 64, 68
is manufactured and machined such that the tip of the pump 6468 hermetically joins each opposing surface 67,68 during a compression operation when the stationary and orbiting scroll members are energized axially with respect to each other. Ru. Alternatively, the radially outermost portion of the surface 61 is slidably supported and ridged opposite the bottom surface 69 of the fixed scroll member 48 .
9 extends further radially inward than shown in the figure.

The main bearing frame member 52 includes an annular, radially inwardly projecting portion 53 that faces axially adjacent to the back surface 51 and has a fixed thrust surface 55 oriented opposite thereto. ing. The back surface 51 and the thrust surface 55 are in substantially parallel planes and axially oriented according to mechanical tolerances and in an amount that allows axially compliant movement of the orbiting scroll member 50 toward the fixed scroll member 48. has an interval.

As shown in FIGS. 1 and 2, the main hairring frame member 52 further includes a downwardly extending hairring portion 7.
0. Supported by press fit in the bearing portion 70 is a conventional sleeve bearing arrangement having the bearing 72 and the lower bearing 74. Two sleeve bearings are preferred over one long sleeve hair ring in that they are easier to assemble within the bearing portion 70 to provide an annular space 73 therebetween. The crankshaft 32 is therefore rotatably journalled within the hair rings 72,74.

Crankshirts 1-32 include converging thrust 1-plates 76 extending radially outwardly from their sidewalls. Balance weight 77 is attached to thrust plate 76 by bolts 75 or the like. In the preferred embodiment shown herein, the diameter of the thrust plate 76 is smaller than the diameter of the internal lower portion 9 defined by the inwardly projecting portion 53 of the frame 52, so that the crankshaft 32 is 9 may be inserted downwardly. Once the crankshaft 32 is installed, the balance weight 77 is attached to the crankshaft via a mounting hole (not shown) extending through the frame member 52.

This attachment ensures a clearance surrounding the perforated thrust plate 76 in the portion of the bouncing chamber 10 at the discharge pressure.

What is attached to the top of the crankshaft 32 is
This is an eccentric crank mechanism 78. In a preferred embodiment, the crank mechanism 78 is located off-center with the shaft hole 8.
1 is provided with a cylindrical roller 80 passing through the roller. An eccentric crank pin 82 constituting the upper eccentric portion of the crankshaft 32 is received in the hole 81, thereby allowing the roller 8
0 is eccentrically supported about an eccentric crank pin 82.

Orbital scroll member 50 includes a lower hub portion 84 defining a cylindrical wall 85 for receiving roller 80. The roller 80 is rotatably journalled within the wall 85 by means of a sleeve bearing 86 press fit into the wall 85.

Each of sleeve bearings 7274 and 86 is preferably a steel lined bronze bushing.

When crankshaft 32 is rotated by motor 22, roller 80 in eccentric crank pin 82 and wall 85
The operation causes the orbiting scroll member 50 to move in an orbit relative to the fixed scroll member 48. The rollers 80 rotate slightly about the crank pin 82 so that the crank mechanism 78 functions as a conventional rocking link axial compliance mechanism to facilitate a hermetic seal between the stationary wrap 64 and the track wrap 68. . The orbiting scroll member 50 is prevented from rotating about its own axis by means of a conventional Oldham ring mechanism consisting of an Oldham ring 88 and a pair of Oldham keys 9092 associated with each of the orbiting scroll member 50 and frame 52. Ru.

Referring to the operation of the compressor 10 in this preferred embodiment, refrigerant fluid at suction pressure is directed through a suction tube 94 attached to the top cover plate 14 by silver brazing or welding and received in a counterbore 96. It will be destroyed. Suction pressure chamber 98 typically includes fixed scroll member 4
8 and frame member 52. Refrigerant is introduced into the chamber 98 from the suction pipe 94 through a suction passage 100 defined by an array of holes in the top cover plate 14 and fixed scroll member 48 .

When the orbiting scroll member 50 is orbited, the refrigerant fluid within the suction pressure chamber 98 is compressed radially inwardly by moving the closed pocket defined by the stationary wrap 64 and the orbit wrap 68.

Refrigerant fluid under discharge pressure in the innermost pocket between the wraps is transferred to the surface plate 62 of the fixed scroll member 48.
The compressed refrigerant discharged through said port 1 (12) enters a discharge fill chamber 104 defined by the underside of the top cover plate 14. A radially extending duct 106 formed in the top cover plate 14 and an auxiliary extension duct 108 extending along the side of the fixed scroll member 48 and frame member 52 carry the compressed refrigerant of the discharge fill chamber 104 to the housing 12. As shown in FIG. The discharge pipe 112 allows the refrigerant within the housing chamber 110 to be delivered to a refrigeration system (not shown) in which the compressor is incorporated.

The compressor 10 also includes the moving parts of the compressor, namely:
A lubrication system is provided to lubricate the scroll member, crankshaft and crank mechanism. An axial oil passage 120 is provided within the crankshaft 32 and communicates with the tube 38.
It extends upward along the central axis of 2. At a central location along the length of the crankshaft 32, an offset radial branch oil passage 122 intersects the passage 120 and at the top of the crankshaft 1 32 into an opening 124 in the top of the eccentric crankpin 82. It is extending. When crankshaft 32 rotates, oil supply tube 38 draws lubricating oil from oil sump 36 and moves it upwardly through oil passages 120 and 122. Upper and lower hair ring 72.
74 communicates with oil passages 120 and 122 by means of planar (not shown) and radial passages (not shown) formed by crank shirt l-32 located proximate bearings 72 and 74. is achieved.

In FIG. 4, lubricating oil pumped upwardly through Offsen I oil passage 122 is present in crankshaft 32 through an opening 124 located at the top of eccentric crank pin 82.

The lubricating oil supplied from the hole 124 is applied to the bottom surface 14 of the wall 85.
0 and fills the chamber 138 within the wall 85 defined by the top surface of the crank mechanism 78 containing the roller 80 and crank pin 82. Oil in chamber 138 flows downwardly along the interface between roller 80 and sleeve bearing 86 and along the interface between bore 81 and crankpin 82 for lubrication thereto. Flat surfaces (not shown) may be provided on the outer cylindrical surface of roller 80 and within crankpin 82 to ensure lubrication.

Now referring to FIG. 4, lubricating oil under discharge pressure is provided in wall 85 to the lower central portion of orbital scroll member 50 by the lubrication system described above. Therefore, when lubricating oil fills the chamber 138, an upward force is exerted on the orbiting scroll member 50 on the fixed scroll member 4.
Acts towards 8. The magnitude of this upward force is the bottom 14
determined by a surface area of 0, which is insufficient to provide the required axial accommodation force. To this end, hub portion 84 increases the upward force on orbital scroll member 50.
The annular portion of the back surface 51 immediately adjacent, ie, circumferentially, is exposed to the refrigerant fluid under discharge pressure, as described further below.

The axial accommodation mechanism of compressor 10 in some embodiments of the invention will be further described with reference to FIGS. 4-12. Typically, the set position of the back surface 51 is exposed to discharge and suction pressures, thereby creating a substantially constant pressure distribution acting on the orbiting scroll member 50 upwardly toward the fixed scroll member 48. Ru. As a result, movement of the orbiting scroll member 50 about the central axis is minimized. Furthermore, an annular sealing mechanism 150 cooperating between the back surface 51 and the adjacent fixed thrust surface 55 provides for a radially inner portion 154 and a radially outer portion 156 of the back surface 51 to be exposed to discharge and suction pressures, respectively. airtightly separate the space. As further described herein, the sealing mechanism 150 includes an annular sealing groove 152 formed in the back surface 51.

In the embodiments of FIGS. 4 to 7, the sealing mechanism 15
0 includes an annular resilient sealing element 158 supported in a non-seated manner in a sealing groove 152. In the preferred embodiment, the radial thickness of the seal element 158 is less than the radial width of the seal groove 152, as best shown in FIGS. 6 and 7. In FIG. 6, the seal element 158 is shown in an inoperative state with the compressor stopped, and the axial thickness of the seal element 158 is greater than the axial depth of the seal groove 152, and the thrust surface 5
5 to the back surface 51.

6, the annular seal groove 152 includes a radially inner wall 160, a radially outer wall 162, and a bottom wall 164 extending therebetween. Similarly, annular sealing element 15
8 is generally rectangular and has a radially inner surface 166, a radially outer surface 168, a top surface 170, and a bottom surface 172. In the non-operative state of FIG. 6, seal element 158 has a diameter less than the diameter of outer wall 162 such that outer surface 168 is slightly spaced from outer wall 162.

During operation of the compressor, axial conformation of the orbiting scroll member 50 toward the fixed scroll member 48 occurs as the compressor compresses and discharges refrigerant into the housing chamber 110. When housing chamber 110 is pressurized, a discharge pressure occupies the volume seen radially inwardly from inner wall 166 in FIG. 6, thereby causing sealing element 158 to move radially outwardly, as shown in FIG. The scroll member 50 is expanded and moved axially upward away from the thrust surface 55. As a result of the axial movement of the scroll member 50, an increased space is created between the back surface 51 and the thrust surface 55. The sealing element 158 moves downwardly toward the thrust surface 55 under the influence of gravity and/or the Venturi effect caused by the initial fluid flow between the bottom surface 172 and the thrust surface 55 . As a result, the discharge pressure increases from the bottom wall 16
4 and the top surface 170. As can be seen from the foregoing, the discharge pressure acting on the inner surface 166 and top surface 170 of the sealing element 158 creates a force distribution on the sealing element and directs it axially downwardly towards the thrust surface 55. , and is biased radially downwardly toward the outer wall 168 to provide a seal thereto.

As previously mentioned, when the orbiting scroll member 50 moves axially upward, the sealing element 158 moves downwardly toward the thrust 1-face 55, thereby creating a space between the back face 51 and the thrust face 55. Sign. To facilitate this initial sealing action, a number of radial grooves 57 may be provided in the back surface 51, as shown in FIGS. 13 and 14. and (, groove 57 is axially deeper than bottom wall 164 and is configured to expose top surface 170 to discharge pressure within housing chamber 110 prior to sealing operation, as shown in FIG. 14). Extending radially inward.

Therefore, the sealing element 158 is forced to move downward upon starting the compressor.

Several alternative embodiments of sealing mechanism 150 are shown in FIGS. 8-12 and described herein. All relate to the deformation of the orbital scroll member in the preferred embodiment, whereby fluid communication means are provided within the deformed orbital scroll member 50' to provide fluid communication from chamber 138 to annular seal groove 152 at a discharge pressure. Provides lubricating oil supply. Further, as illustrated in FIGS. 8 and 9, the scroll member 50' is attached to the bottom surface 14 of the wall 85.
The oil passage 174 extends from the opening in the bottom wall 164 of the seal groove 152 to the opening in the bottom wall 164 of the seal groove 152.

The oil passage 174 is a solid axial passage 176, the passage 1
There are four passages 178 extending radially from 76 and four axial passages 180 extending from each passage 178 to bottom wall 164 of seal groove 152.

Providing the oil passage 174 not only aids in the seal mechanism 150 utilizing an annular resilient seal element, but also allows for a hydrostatic seal configuration as illustrated in FIG. 10. In such a configuration, the compressor 10
The manufacturing tolerances become tighter as the gap between the back surface 51 and the thrust surface 55 becomes smaller. In this way,
Oil supplied to the sealing groove 152 via the oil passage 174 flows into said groove and also acts against the thrust surface 55 to seal between the main gas region of the housing chamber 110 and the suction pressure chamber 98.

Oil creating a hydrostatic seal has a tendency to leak into the suction pressure chamber, so that a minimum clearance between the back surface 51 and the thrust surface 55 effectively controls the oil velocity in the refrigerant system. It must be maintained to prevent it from getting too high. However, some leakage of oil is necessary for lubrication of the scroll wrap and the like.

11 and 12 illustrate another embodiment of the seal mechanism 150, in which an annular seal element 158 is associated with an oil passageway 174. The operation of this seal structure is substantially the same as that previously described in the embodiment of FIGS. 6 and 7, with the additional feature that the oil passage 174 allows The goal is to provide means to ensure that they work properly. Furthermore, the oil flows through the gap between the sealing element 158 and the sealing groove 152, i.e., the top surface 170 and the bottom surface 164.
Flows from passageway 180 into housing chamber 110 through the gap between and between inner surface 166 and inner wall 160 .

In various embodiments described herein, the sealing mechanism 150 includes a seal between each set portion of the back surface 51 that is orbited by the orbiting scroll member 50, thereby reducing the distribution of upward forces on the back surface 51. Advantageously, it remains substantially constant regardless of its orbital motion. This is due in part to the possibility of different seal profiles for the sliding seal against the fixed thrust surface 55.

Providing a fixed thrust surface to which the seal profile slides seals represents several significant advantages. For example, the relative movement between the seal element and the seal face is minimal, thereby reducing frictional forces and increasing the durability of the seal. Additionally, leakage through the seal location is more effectively controlled.

It is also noted that with the seal profile described herein, leakage is minimized due to the lack of seal attachment means and the composite multi-piece seal profile.

The annular sealing elements described herein are preferably constructed of Teflon material. In addition, glass-filled Teflon,
A mixed material of Teflon, carbon and Lydon is preferred to provide the sealing element with the necessary stiffness to resist elongation into the void due to pressure differentials. Furthermore, the surface with which this Teflon seal contacts is preferably cast iron.

[Brief explanation of the drawing]

Figure 1 shows the scroll compressor of the present invention, 1-- in Figure 3.
2 is a vertical sectional view of the compressor in FIG. 1 taken along line 2-2 in FIG. 3 in the direction of the arrow, and FIG. Fig. 1 is a plan view of the compressor, Fig. 4 is an enlarged cutaway view of the compressor shown in Fig. 1, Fig. 5 is an enlarged bottom view of the orbital scroll member of the compressor shown in Fig. 1, and Fig. 6 is a non-operating view. The first illustrating the annular sealing element in the state
7 is an enlarged sectional view of the compressor of FIG. 1 showing the annular seal element in an operating state; FIG. 8 is an enlarged sectional view of the compressor of FIG. 7 shows an enlarged fractured section of a scroll compressor in another embodiment, in which oil is supplied through passages extending radially within the scroll compressor, and reference numerals are used identically for the same components as in FIGS. 1 to 7; FIG. 9 is a bottom view of the orbiting scroll member of the compressor of FIG. 8; FIG. 10 is an enlarged cut-away cross-sectional view of the compressor of FIG. 8, particularly showing a static seal without an annular seal element; The figure is an enlarged cut-away cross-sectional view of the compressor shown in Fig. 8 which uses an annular seal element and shows the compressor in a non-operating state, and Fig. 12 shows the compressor shown in Fig. 8 with the annular seal element shown in Fig. 11 in an operating state. FIG. 13 is an enlarged cutaway view of an orbital scroll member of a compressor showing another embodiment of the present invention in which radial grooves are used to facilitate sealing; FIG. 13 is an enlarged cutaway view of the compressor of FIG. 1 incorporating the orbital scroll member of FIG. 13 with the annular seal element shown in an inoperative state; FIG. DESCRIPTION OF SYMBOLS 12... Sealed housing, 48... Fixed scroll member, 50... Orbital scroll member, 55... Fixed thrust surface, 64... Fixed wrap element, 66... Plate-shaped portion, 68... - Orbit wrap element, 98... suction pressure chamber, 110... discharge pressure chamber, 150...
Track sealing means, 152... annular sealing groove, 154,
156... location, 158... annular seal element.

Claims (12)

[Claims] (1) A sealed housing (12) with a discharge pressure chamber (110) under discharge pressure and a suction pressure chamber (98) under suction pressure; a spiral fixed wrap element (64)
and an orbiting scroll member (50) having a plate-like portion (66) having a front face and a back face, said front face having an orbital wrap element (68) thereon; In a scroll compressor, the stationary and orbital wrap elements are in mesh with each other to establish at least one pocket of refrigerant fluid that is compressed by orbital motion of the orbiting scroll member relative to the stationary scroll member. the fixed thrust surface (55) adjacent to the back surface and each portion (154, 156) of the back surface of the plate member exposed to the discharge pressure chamber and the suction pressure chamber; The orbital scroll member and the fixed thrust surface are provided with an orbital sealing means (150), and the sealing means is provided at a fixed position on the back surface of the plate member regardless of the orbital movement of the orbiting scroll member. A scroll compressor characterized in that each location (154, 156) is set. (2) The back surface (51) of the plate member has an annular seal groove (
Scroll compressor according to claim 1, characterized in that the sealing means (150) comprises an annular sealing element (158) partially disposed in the groove. (3) The scroll compressor according to claim 2, wherein the annular seal element (158) is supported in the annular seal groove (152) in a non-attached state. (4) The seal element (158) is connected to the seal groove (1
A scroll compressor according to claim 2, wherein the scroll compressor extends from the thrust surface (52) towards the thrust surface (55) and is slidably sealed therein. (5) A frame (52) is attached to the fixed scroll member (48), and the fixed thrust surface (52) is attached to the fixed scroll member (48).
The scroll compressor according to claim 1, wherein 5) is constituted by a portion of the frame. (6) Each location (1
54,156) comprising a radially inner portion (154) exposed to said ejection pressure chamber (110) and a radially outer portion (156) exposed to said suction pressure chamber (98). 1 scroll compressor. (7) The annular seal groove (152) has inner and outer walls (160, 162) in the radial direction and a bottom wall (1
64), and the sealing element (158).
) is in sealing contact with the radially outer wall and is spaced from the radially inner wall and the bottom wall such that compressed refrigerant fluid can be brought therebetween from the discharge pressure chamber (110). Scroll compressor according to claim 2, characterized in that the sealing element (158) is biased against the radial outer wall and towards the thrust surface (55). (8) The back surface (51) of the orbital scroll member has at least one radial groove formed therein, the radial groove being interlocked from the bottom wall (164) of the sealing groove to the discharge pressure chamber. extending radially inwardly, thereby applying a discharge pressure to said sealing element (158).
8. The scroll compressor according to claim 7, wherein the radial groove is initially set at a surface between the bottom wall of the seal groove and the bottom wall of the seal groove. (9) a sealed housing (12) comprising a discharge pressure chamber (110) under discharge pressure and a suction pressure chamber (98) under suction pressure; an oil sump (36) in said discharge pressure chamber; a fixed scroll member (48) having a fixed wrap element (64); and a top surface (67);
) and a bottom surface (51) and having a spiral-shaped orbital wrap element (68) on said top surface, said stationary and orbital wrap elements being connected to said stationary scroll member. In a scroll compressor, the scroll compressor is mated to establish at least one pocket of refrigerant fluid to be compressed by orbital movement of the orbiting scroll member, the bottom surface of the orbiting scroll member having an annular sealing groove (152) therein. and a fixed thrust surface (55) adjacent the bottom surface of said orbiting scroll member, and sealing means (150) cooperating between said orbiting scroll member and said fixed thrust surface to said sealing means is adapted to separate and seal between respective portions (154, 156) of the bottom surface of said orbiting scroll member exposed to a pressure chamber and a suction pressure chamber; Regardless of the orbital movement of the plate member, each of the locations (154, 156) is set at a fixed position on the back surface of the plate member, and means (174) for supplying oil from the oil reservoir into the seal groove is provided. A scroll compressor characterized by: (10) The sealing means (150) includes a hydrostatic seal formed by a flow of oil from the annular seal groove (152) toward the thrust surface (55). 9 scroll compressor. (11) Said sealing means (150) is partially disposed within said annular sealing groove (152) and extends therefrom towards and in airtight contact with the thrust surface (55). ), wherein the oil in the annular seal groove applies a biasing force to the annular seal element toward the thrust surface. (12) The annular seal groove (152) has a radial inner wall (
160), a radially outer wall (162) and a bottom wall (164) therebetween;
158) is in airtight contact with the radially outer wall, and the annular seal groove (152) is in airtight contact with the radially outer wall and between the radially inner wall and the bottom wall.
spaced apart to allow the passage of oil therein, thereby biasing the sealing element against the radial outer wall and towards the thrust surface (55). 11 scroll compressors.