JPS62233491A - Rotary compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION FIELD OF INDUSTRIAL APPLICATION The present invention relates to Ll-clicon compaction, and more particularly, during the compaction process, a plurality of components are PP! The present invention relates to a compressor that forms a moving rotary assembly.

BACKGROUND OF THE INVENTION Many types of conventional rotary compressors exist. A common type of rotary vane type combiner 1 is the coater vane type combiner +J', in which a stator defines a chamber and a rotor rotates within this chamber. This rotor is driven by a motor. It is fixed to the foot. The rotor and chamber wall are typically cylindrical, the chamber is larger than the rotor, and the rotor rotates eccentrically with respect to the chamber wall. The rotor in such a mechanism has blades or ronds extending outwardly from and contracting with respect to the rotor to create a variable volume compression region.

According to a typical device, U.S. Patent No. 4.118°160
A retractable blade that rotates about a pin is mounted on the outer circumferential surface of the rotor, as shown in No. 1, Vol. The rotor is mounted on a drive shaft that is eccentric to the central axis of the surrounding stator. As the rotor rotates, the blades extend outwardly relative to the body of the rotor. A generally similar type of compressor is shown in U.S. Pat. No. 4,415,322 and U.S. Pat. No. 1,995,755.

According to the roller revane compressor disclosed in U.S. Pat. Extending in and out of the liner that rotates the rotor inside. A similar rotary sliding vane type compressor is disclosed in U.S. Pat. No. 3,917.438.

Such a structure can be improved. For example, the number and types of components attached to the rotor can be reduced. Furthermore, the no-load horsepower and starting torque of such machines, which tend to be relatively high, can be lowered. Relatively high no-load power demands and starting torques result from continued compression at no-load, and such a structure may reduce the relative role of the inlet boat and open boat over a range of compression ratios. Determined.

Some existing compressors have rotor and stator t! There are some products that cause excessive wear over a wide range due to frictional forces, but this l! ! IJX forces can be reduced. Radial vane type units have limited spread of the vanes around the base rotor due to bending moments acting on the vanes.

This means that the size of the stator and the stator are determined by
-Limit the rise and position of the taboa.

It is desirable that the structure of these [1-cri compressors be improved.

SUMMARY OF THE INVENTION The present invention provides an O-type compressor having a stator defining a compression chamber.

The compression chamber is typically cylindrical and has an inlet and an outlet. The inlet and IJF outlet are in the radial direction on the outer circumferential surface of the chamber,
This means that it can be positioned axially at both ends of the chamber.

The plurality of components are positioned to rotate eccentrically within the chamber. These components have an outer peripheral cross-sectional shape of l1Thl-, which is similar to a comma shape. These components are on the right side of the enlarged end, or head, which tapers toward the reduced end, or tail. The enlarged end has a convex section with a radius r connected to a concave section with a radius r. Each of these cross sections has an radius larger than radius r [
They are connected by a convex section with a radius R. The relational expression between the radius R and the radius r is preferably expressed as follows: 11=r+r, /S i n (180/n). Here, n indicates the total number of constituent elements.

These components are intermeshed to form a rotor assembly having a generally cylindrical cross-section and a radius equal to R'b. These components are pivoted for rotation within the chamber.

During normal operation, J3 is between an inner position where the components are substantially in mesh and an outer position where adjacent components rotate outside of the mesh position, with the adjacent components rotating in rotation. do. In the area of the outer position J3, an expanded working volume is defined which receives working fluid from the artificial body. When a component continues to rotate or pivot, the component continues to rotate or pivot.
It will move inwardly and define a reduced working volume that communicates with the output r+ chamber.

According to a preferred embodiment, the compact assembly has an actuator f-J that meshes all of the constituent elements into a substantially cylindrical shape;
Turn the Jita to the right. [In a so-called cylindrical case, the components closely fitted together in the chamber rotate without any substantial compression of the working fluid L. This allows for no-load operation with the low power required and provides a mode of generating low starting torque.

According to a preferred embodiment, these components have the same cross-sectional shape; they are protruding or, on the contrary, shaped like a persimmon cut to the required length.

DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION Referring to FIG. 11, an end view of four compressor elements 10 intermeshed at 1° to form a cylindrical shape is shown. The combination of components is referred to as rotor assembly 12. The rotor assembly, which is generally cylindrical in shape, has a radius R (FIGS. 2 and 3) from the central axis 8. Component 10 defines a central opening 14 1 , the component is a part of a rotary compressor, generally designated 6 . 1 shows holes 16 extending partially into each component 10, whereas FIGS. 2 and 3 show holes 16 extending fully into each component 10.

FIG. 2 shows one component 10. FIG.

Hole 16 provides an area for the component to pivot during operation. The outer periphery of the cross section of each component 10 has a comma shape, and has a shape that becomes tapered from the enlarged head 18 to the reduced tail 20. The component is defined by three radial elements. A first radius r defines head 18 and extends from center point 22 . 1st
The radius r of defines the head by a convex arc between points a and d. A second radius r extends between points C and C and defines a concave arc. The point is a smooth inflection point between the first convex arc ab and the second concave arc bc. In this way, the point marks the point of contact of two adjacent non-intersecting circles with geometrically equal radii. For manufacturing purposes, point C is the small radius end. The third radius [( extends between points C and z1 and defines another convex arcuate Ca.

At point a, the radius changes smoothly from R to r. Thus, geometrically, the tangent at J3 to the circle of radius r at point a is the same as the tangent at point a to the circle of radius R. R is greater than "゛. Preferably, R
The relationship between and r is presented in the following equation: Here, n indicates the total number of common-shaped components forming the rotor assembly. The total number of components 10 forming rotor assembly 12 is two or more, as described above. The size and amount of compression of the inlet boat 32 and outlet boat 34 required for this compressor suggests that a compressor of the type disclosed has between four and eight components 10. Six components are more preferred. The larger the total number of components 10, the smaller the component size, the smaller the displacement volume and stator diameter for a given rotor assembly, and the larger the central inactive area 14. 6
In the case of a rotor assembly with 10 components, the central circular bar contacting each component 10 has a radius r equal to each component 10.

As shown in FIGS. 1 and 3, the center point 22 of the convex head 18 of each component 10 is connected to the center point 22 of a regular polygon 24 with sides equal to the total number of components 10 forming the rotor assembly 22. It is located at the intersection of two adjacent sides. When the components 10 are fully intermeshed to form a normal cylindrical shape, the inflection point is located at the intersection of the contour of the component 10 and the regular polygon 24.

Not shown in Figure 3 J: Sea urchin, composition type ¥? 410 is housed within the compression chamber 26 of the stator 28. The compression chamber 26 is
Preferably, it has a cylindrical shape whose cross section is defined by a circle having a center point 30 and a radius S.

The radius S of the stator compression chamber 26 is greater than the radius R of the cylindrical rotor assembly 12. Center point 8 of rotor assembly 12 is offset from center point 30 of compression chamber 26 . The center point 8 is located on the longitudinal axis 52 of the mated components, and the center point 30 is located on the longitudinal axis 53 of the compression chamber 26 of the stator.

The gas arc 28 further defines an inlet region 1a32 and an outlet region 34 in fluid communication with the compression chamber 26. These areas can be radially or axially oriented and the boat shapes of many scales can be equally shaped. FIG. 3 shows the extent of the axial inlet region 32 and outlet region 34.

Working fluid is drawn into the compression chamber 26 from this axial inlet region 32 and compressed fluid is discharged from the axial outlet region 34. When the component 1o rotates within the compression chamber 26 and pivots around the center point 22, the enlarged working volume 36
(FIG. 4) is shaped in the area adjacent to the inlet area 32, and the reduced actuating body vJ38 is shaped in the area adjacent to the outlet area 34. The working volume is defined between two adjacent components 10 and the wall 40 of the compression chamber 26 .

f) The J volume is maximum in the part adjacent to the inlet region J" and minimum in the part adjacent to the flf II region 34, and repeats between these.

FIG. 5 shows a preferred practical arrangement for positioning and rotating components within the compression chamber. Hole 1 of component 10
6 extends across the axial length of the component. A pivot pin 42 is positioned through the hole 16. Pivot pin 42 is positioned between minor end plate 44 and front end plate 46, each of which has a cavity 48. The pivot pin 42 is preferably fixed to the end plate 44.46. It will be readily apparent which of the many mounting configurations to choose. For example, the pivot pin extends partially into configuration MIA 10;
Can be used at one end or both ends. Swivel pin 42
can be completely fixed to one or both ends of the component 10, and the corresponding end play!・Rotates within the cavity.

According to the actual embodiment (not shown in FIG. 5), the rear end plate 44
is fixed to the shirt 1-50 forming part of the structure for rotating the component 10. The shaft 50 is arranged along a longitudinal axis 52.

The shaft 50 is driven by a motor (not shown).

The end plate t~44 has a circular protrusion 5/I which contacts or through a small space C1 the surrounding component 10 reducing the leakage path. The front end plate 46 has four holes 56 through which actuators 58 pass. The actuator 58 has an extension 60 and the compressor 6 has a means for axially moving the actuator 58, such as a pneumatic, hydraulic or electrical actuation controller.
-Roller 62 is on the right.

As best shown in FIGS. 6 and 7, the extension 60 is positioned within a groove 64 of the component 10, and the groove 64 of the component 10 has a cam surface 66.

The extension portion 60 and the cam surface 66 interact with each other in phase n, so that the extension portion 60 is moved by the axial movement of the actuator 58.
applies a force to the camming surface 66, which causes the component 10 to snugly mesh with the outer diameter of the conventional cylindrical rotor 12. Other means of engaging configuration \l'A10 can be employed as well.

With particular reference to FIGS. 4 and 6, in operation, component 10 is rotated within compression chamber 26 such that the desired orientation is
As shown in the figure. Typical operating speeds are 1800 or 3600 rl)m. The centrifugal force generated in the tail section 20 at this rotational speed is caused by the outer and outer sides of the meshing cylinders.
There is a tendency to turn i10. Rotation axis 5 of component 10
2 is located within the compression chamber 26, which allows the component 10 to pivot outwardly for a greater distance near the inlet area 32, and in the vicinity of the outlet area td.
34, its movement is restricted by the wall 40 of the compression chamber 26. In this way, the centrifugal force exerts an outward movement on the components 10, but the order of magnitude of these components is 1r! 1 is restrained by the chamber wall or an extension of the chamber wall or other mechanical restraint means acting as a camming surface of the component 10. Other cam or gear structures may be used to bias or guide the components during rotation.

It passes through the population area 32 and continues rotating.
Forces attempting to move the 0 outward are resisted by the increased pressure differential across the component. As component 10 rotates through a compression cycle, compressible working fluid enters expanded working volume 36 from inlet region hlt32 and is compressed to a smaller volume and higher pressure. The pressure acting on the exposed convex surface Ca is higher than the pressure acting on the exposed small concave surfaces.

This counterforce is intended to offset a portion of the centrifugal force and allow the friction generated by the frictional interaction between the tail of the component 10 and the compression chamber wall 40 to be reduced. Additionally, uncompressible fluid may be present at the start of an oil injection compressor or cold compressor or under other circumstances. The presence of a volume of incompressible liquid between mutually adjacent components 10 could be detrimental to the combrella V and its operation. Generates a force that tends to rotate the element.

Actuation in the opposite direction to the preferred direction described above is also possible. In this case, the force resulting from the pressure differential across the component 10 will be added to the centrifugal force acting on the component.

However, the above-mentioned self-release effect is reduced to 1 due to the presence of liquid.
I can't get over it.

Compressed working fluid is discharged from outlet region 34.

The rotation axis 52 is arranged so that a portion 40' of the chamber wall has a circular arc with a radius R in order to close the part of the component 10 adjacent to the partition wall N140 between the outlet region 34 and the inlet region 32. The rotor is positioned above the radius of the cylindrical rotor. The portion of the compression chamber wall between the inlet region and the outlet 1'' region is contoured with a radius R to facilitate separation.

As is clear from the drawing, the components meet at surfaces defined by convex and concave portions of equal radius r.

Sliding and pivoting movements between adjacent components during one cycle occur smoothly.

With particular reference to FIG. 6, it will be seen that the compressor according to the invention can be loaded by placing the component 10' in a substantially cylindrical, fully interlocking configuration without shrinkage. I try not to. 11. The safety valve (not shown) is constructed in an unloaded state.11. 'i, correspondingly operative to communicate with either the inlet region 32 or the outlet region 34 to prevent backflow of fluid through the compression chamber.

In this case, sufficient driving force is required to overcome the situation where the vehicle comes to a standstill. This configuration is a star l-
This is desirable when a relatively lower starting torque is required.

The components of the compressor according to the present invention consist of a variety of vane and rotary compressors typically used in compressors. Particularly when no hydraulic pressure is applied, the construction type f410 can be constructed from 44 materials of the self-sliding type. Although the outer diameter in cross section of each of the components 10 of the disclosed type of compressor is the same, the article of manufacture can include an elongated structure cut to the desired axial dimension of each component 10. Products can be manufactured by extrusion or plastic molding,
For example, the product may be a sheet metal product, a sintered metal product, or a ceramic product. The density of the material selected for manufacture of components 10 affects the centrifugal force exerted on the tail 20 of each component. For this reason, it is desirable to vary the material density in the cross-section of the component to increase or impede external forces. For example, it is desirable to have a certain design that is considered in relation to the size and rotational speed of the rotary assembly.

Many []-taclean compressor systems utilize stator chambers that are shaped somewhat differently than cylindrical. It is clear that the structure of the compressor disclosed herein is consistent with such configurations. Many other variations are possible as well without departing from the spirit of the disclosure. Therefore, within the scope of the appended claims, the detailed description and drawings are to be considered as one example only and the invention is not intended to be limited thereto.

[Brief explanation of drawings]

FIG. 1 is a plain end view of rotary compressor components arranged in an interlocking configuration in an embodiment of the present invention, and FIG. Figure 3 is a cross-sectional view of the compressor of the present invention in which the compressor components of the present invention are closed inward, and Figure 4 is a perspective view showing the compressor components in the outward direction. FIG. 5 is a longitudinal cross-sectional view of an embodiment of the rotary compressor of the present invention; FIG. FIG. 7 is a cross-sectional view of the compressor; FIG. 7 is a perspective view of the compressor components with cams interacting with the actuator; DESCRIPTION OF SYMBOLS 10... Compressor component, 12... Rotor assembly, 14... Center part]] part, 16... Hole, 18...
...Extended head, 20...Reduced tail, 22.
・Center point, 24 ・Regular polygon, 26・
...Stator compression chamber, 28...Stake, 30...
・Center point, 32...enter [1 area, 34・
...Exit area, 40...Wall, 42...Swivel pin, 44...Rear end brake 1~. 4G...
- Front 9i nibrate. Applicant: Joy Manufacturing 11 Ring Company

Claims (29)

[Claims] (1) a stator defining a generally cylindrical compression chamber, an inlet area to the compression chamber, and an outlet area from the compression chamber; a plurality of meshing elements having substantially the same shape; means for rotating meshing elements of the invention, said meshing elements being sufficiently meshable to form a generally cylindrical rotor and disposed so as to be movable relative to each other within said compression chamber during rotation. A rotary compressor, characterized in that the compressor forms an expanded working volume adjacent to the inlet region and a contracted working volume adjacent to the outlet region. (2) the meshing elements are sufficiently meshable to form a generally cylindrical rotor having a radius R, and the radius R is less than the radius S of the generally cylindrical compression chamber; A rotary compressor as claimed in claim 1. (3) The rotary compressor according to claim 1, wherein each of the meshing elements has a comma-shaped cross section. (4) The cross-sectional shape of the meshing element is characterized by consisting of a continuous line of a first convex part with radius r, a second concave part with radius r, and a third convex part with radius R larger than radius r. A rotary compressor according to claim 1. 5. A rotary compressor as claimed in claim 4, characterized in that the meshing elements are meshable to form a generally cylindrical rotor of radius R. (6) A patent characterized in that the first convex portion defines an expanded head that tapers toward a reduced tail defined by the second concave portion and the third convex portion. A rotary compressor according to claim 4. (7) The rotary compressor according to claim 4, wherein when the total number of meshing elements is n, the radius R is expressed as R=r+r/sin (180/n). (8) The rotary compressor according to claim 1, wherein each of the meshing elements is rotatably attached to a pivot pin. (9) The rotary compressor according to claim 8, wherein the rotating means comprises a rotatable rear end plate fixed to the pivot pin. (10) each of the pivot pins extends axially through the mating element, the rotation means comprising a rotatable forward end plate engaging one end of the extension of each pivot pin; and said rotatable rear end plate; 10. A rotary compressor according to claim 9, characterized in that the swivel pins are engaged with other extensions of each of the pivot pins. (11) The rotary compressor according to claim 10, wherein at least one of the backs of the plate is fixed to a rotatable shaft. (12) The rotary compressor according to claim 11, wherein the shaft is eccentric with respect to the substantially cylindrical rotor. 13. The rotary compressor of claim 1 further comprising means for interlocking the meshing elements to form a generally cylindrical rotor. (14) Each of the engaging elements includes a groove extending in the axial direction, and the engaging means includes a plurality of extensions, each of which is engaged with a corresponding groove. A rotary compressor according to claim 13. (15) Each of the extensions is fixed to an axially movable actuator, and the groove is formed on a cam surface such that upon axial movement of the actuator, the engagement element forms a generally cylindrical shape. 15. The rotary compressor according to claim 14, wherein the force is applied so as to mesh with the outer diameter of the shaped roller. (16) a plurality of identically shaped components interlockable to form a generally cylindrical rotor and alternately extendable to define an expanded working volume and a contracted working volume; an inlet region and an outlet region; a stator defining a generally cylindrical compression chamber having a cylindrical compression chamber; A rotary compressor, characterized in that it receives working fluid from an inlet region on a component defining said compressive action and discharges working fluid to an outlet region on a component defining said contraction action. (17) Claim 1, wherein each of the same-shaped components has a comma-shaped cross section.
The rotary compressor described in item 6. (18) Each of the constituent elements having the same shape is composed of a first convex portion having a radius r, a second concave portion having a radius r, and a third convex portion having a radius R larger than the radius r. The rotary compressor according to feature 16. (19) Claim 17, characterized in that when the total number of components having the same shape is n, the radius r is expressed as R=r+r/sin(180/n).
Rotary compressor as described in section. (20) a stator defining an annular chamber having a predetermined radius of curvature and having a radially located peripheral inlet region and a radially located peripheral outlet region; and a plurality of identically shaped components; means for rotating components, said components being meshable to form a generally cylindrical rotor having a radius less than said radius of curvature;
and wherein the rotary compressor is slidable relative to one another to define an expanded working volume adjacent the inlet region and a contracted working volume adjacent the outlet region. (21) The cross-sectional shape of each of the same-shaped components is a continuation of a first convex portion with radius r, a second concave portion with radius r, and a third convex portion with radius R larger than radius r. 21. The rotary compressor according to claim 20, wherein the rotary compressor is composed of a wire. (22) The rotary compressor according to claim 20, wherein when the total number of components having the same shape is n, the radius r is expressed as R=r+r/sin (180/n). . (23) A rotatable shaft, a plate fixed to the shaft and rotating together with the shaft, and a plurality of identically shaped components arranged continuously and meshably to form a substantially cylindrical rotor shape. a stator surrounding said component and defining a generally cylindrical compression chamber eccentric to said shaft, said component slidably repositioning and cycling between a contracted and expanded configuration. a rotary compressor, wherein the compression chamber has an inlet region adjacent to the component in an expanded configuration and an outlet region adjacent to the component in a contracted configuration. . (24) The cross-sectional shape of each of the same-shaped components includes a first convex portion with a radius r, a second concave portion with a radius r, and a third convex portion with a radius R (7) larger than the radius r. 24. The rotary compressor according to claim 23, wherein the rotary compressor is configured to form a continuous line. (25) The rotary compressor according to claim 23, wherein when the total number of components having the same shape is n, the radius R is expressed as R=r+r/sin (180/n). . (26) The cross-sectional shape of the main body extending in the axial direction is composed of a continuous line of a first convex part with radius r, a second concave part with radius r, and a third convex part with radius R larger than radius r. Rotor element for rotary compressor. (27) The rotor element according to claim 26, wherein the rotor element has a comma-shaped cross section. (28) The rotor element according to claim 26, wherein when n takes an integer from 4 to 8, the radius R is expressed as R=r+r/sin(180/n). (29) The rotor element according to claim 28, wherein n is 6.