JPH01155088A - Vortex compressor and assembly method thereof - Google Patents

Abstract

PURPOSE: To secure seal function with no relation to a disposing direction by controlling a backpressure of two stages so as to eliminate a major part of an axial load applied to a revolving scroll. CONSTITUTION: Oil is supplied between wraps under a lower intermediate pressure by holes 21-7 and 21-8, and oil is supplied between wraps under an upper intermediate pressure by holes 21-10 and 21-11. Thus a pressure difference with respect to a sump is generated, and the oils under the lower and the upper intermediate pressures act on the back of a revolving scroll 21 prior to being supplied between the wraps so as to maintain a balance with respect to an axial force to separate a fixed scroll and the revolving scroll 21. A hub 21-1 has a thrust plane with respect to a crankshaft, and a lubrication oil passageway is formed in a V-shaped groove arranged in two diametral ends of the thrust plane.

Description

DETAILED DESCRIPTION OF THE INVENTION BACKGROUND OF THE INVENTION A spiral machine, which can be used to compress, expand or pump fluid, comprises two spiral members each having a circular end plate and a helical or involute-shaped wrap. is included. Such spiral members are maintained circumferentially and radially curved so that when two wraps are engaged, a plurality of lines of contact are formed or separated by a minimum gap between the wraps. defines at least one pair of fluid pockets or chambers. One spiral member is stationary while the other spiral member is pivoted by an eccentric shaft and a rotation limiting joint. The relative pivoting movement of the two spiral members causes the contact line or minimum gap to move along the curved surface of the wrap, thereby causing a volumetric change in the trapped space within the fluid pocket. Such a capture space can be increased or decreased depending on the direction of the pivoting movement. Generally, since several entrapment spaces exist at the same time, several contact lines or minimum gaps exist at the same time, and each of them moves along a lap, with the movement pointing towards the center or discharge part within the compressor casing. There is. Within the compressor casing, the compressed gas creates forces that axially separate the spiral members, resulting in high thrust loads and tip leakage. Additionally, horizontal and vertical devices typically require a light design. The original shape of a spiral machine is vertical and elongated. Therefore, due to the size and packaging of the equipment unit, it is generally preferable to mount the spiral machine horizontally.

In traditional vertical volute compressors, the motor is mounted at the bottom of the volute mechanism, and therefore has a somewhat elongated shell and a basic centrifugal compressor that requires high lift forces across the motor to lubricate the highly loaded bearings. It would include a pump, a tilt-sensitive gravity lubricant separation mechanism for returning lubricant to the sump, and a precision metering oil injection device with constant sealing performance.

SUMMARY OF THE INVENTION In the best embodiment, a high hermetic spiral compressor is sealed by a combination of tight tolerance control and oil injection. In addition to the sealing function, such oil also provides a lubricating function, creating the need for effective separation of the oil from the exhaust gases. The sump is isolated and the oil pumping motion is produced by the centrifugal pumping motion of the crankshaft and by the differential pressure between the sump pressure at the compressor discharge pressure and the intermediate pressure when the oil is injected into the volute. Ru. When placed vertically, the motor is mounted on top of the volute member, thereby allowing the vortex generated at the outlet pipe inlet to be utilized for centrifugal separation of the oil. Generally, even when placed horizontally, the device operates satisfactorily and the load deviation due to the motor is small.

An angle of at least 15-20 degrees from the horizontal is required for the oil to return to the sump by gravity.

The object of the invention is to provide a volute compressor that is independent of the installation direction.

Another object of the invention is to provide a spiral compressor that does not require axial or radial seals.

Yet another object of the present invention is to provide a centrifugal compressor that combines tight tolerance control and oil injection to provide a sealing function.

Another object of the present invention is to provide an axial thrust bearing that incorporates two stages of backpressure control to counteract most of the axial loads on the swirling volute. These and other objects, which will become clear below, are achieved by the present invention.

In essentially high-tight spiral compressors, oil injection is used for sealing, to provide a back pressure differential to counteract axial loads, and to provide lubricating oil. Since the sump is isolated and maintained at compressor discharge pressure, the pressure differential provides the force necessary to deliver the lubricating oil onto the bearing surfaces and to the injection point. When placed vertically, the motor is placed on a spiral member whose weight acts in conjunction with the back pressure differential to counteract the axial loading.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIGS. 1 to 4, reference numeral 20 generally indicates a stationary spiral having a wrap 22;
3 schematically shows a swirling volute with a The chambers numbered A to M and 1 to 12 respectively indicate the suction, compression, and discharge stages, respectively, and chamber M is the one that is connected to the discharge port 25 when the device is operated as a compressor. A common chamber is formed. chamber 4
11 and D to K are each in the shape of a helical crescent or lunette extending approximately 360°, the ends of which are the contact lines or minimum clearance points between the spiral wraps. For example, if point It will be clear that this results in losses or reduced efficiency. To minimize losses due to leakage, it is usually necessary to maintain minimal tolerances, use positive mechanical tip seals, and rotate at high speeds. However, in the present invention, the sealing function is achieved by using oil injection. Referring again to FIGS. 1-4, it will be appreciated that chambers 1-12 are symmetrical with respect to chambers A-L, except that they are located on either side of wraps 22 and 23. It will be.

To explain FIGS. 5 to 8, the fixed spiral 20
is approximately disk-shaped with a spiral-shaped portion, and the wrap 22 is defined by removing the spiral-shaped portion. spaced apart on both ends in the diametrical direction, and approximately 3 in the circumferential direction.
Two recesses 20-1 and 20-2 extending 0 DEG are formed at the periphery of the fixed spiral 20, thereby defining shelves 2 DEG-3 and 20-4, respectively. As shown in detail in FIG.
-5 is fluidly connected to the outlet 25 to form part of the discharge channel and extends between the installed recesses 20-1 and 20-2. Suction pipe 1 to hole 20-6
6 is received, whereby hole 20-6 functions as an inlet.

Hole 20-6 has a groove 20-7 formed on its inner surface to receive an O-ring as described below. Additionally, a counterbored axial hole 20-8 is provided for receiving an assembly bolt.

-17= Axial hole 20-9 receives the oil pickup tube and forms part of the lubricant flow path.

Axial holes 20-10 form part of the oil return flow path.

To explain Fig. 9 to Fig. 12, the swirling spiral 2
1 has a wrap 23 and a boss 21-1 on the opposite side thereof. An axial hole 2]-2 is formed in the boss 21-1. Radial bore 21-3 terminates within bore 21-2 and has a set screw 26 or other suitable structure inserted at its other end. The axial hole 21-4 is an annular groove 21
-14 and terminates within the hole 21-3, both of which form a part of the lubricating oil flow path.

Holes 21-5 and 21-6 arranged at both diametrical ends intersect with axial holes 21-7 and 21-8, respectively. A radial hole 21-9 is formed in boss 21-1 and intersects axial hole 21-10. An axial bore 21-11 extends through the swirling volute 21.

Axial holes 21-7.21-8.21-10 and 21-
11 terminates in a wrap 23, thereby providing a lubricant flow path for sealing between wraps 22 and 23. More specifically, holes 21-7 and 21-8 provide oil between the wraps at a lower intermediate pressure;
Holes 21-10 and 21-11 provide oil between the wraps at an upper intermediate pressure, thereby creating a pressure differential to the sump. In addition, (=f), the oil at such lower intermediate pressure and upper intermediate pressure acts behind the swirling volute 21 before being supplied between the wraps, thereby serving to separate the volutes 20 and 21. Balance against axial force is maintained.

The radial grooves 21-12 and 21-13 cooperate with the Oldham joint in the usual manner. The boss 21-1 has a thrust surface relative to the crankshaft, and V-shaped grooves 21-15 arranged at both diametrical ends provide a lubricating oil flow path across the boss 21-1.

As shown in detail in FIG.
has a thin shaft portion 30-1, a main shaft portion 30-2, a flange portion 30-3, and an eccentric shaft portion 30-4 in this order. Axial hole 3
0-5 substantially terminates in a diametrical hole 30-6. Holes 30-5 and 30-6 form part of a lubricant flow path and define a centrifugal pump. When assembled, the crankshaft 30 is received within a bearing head, which is shown in detail in FIGS. 13-15.

The main shaft portion 30-2 of the crankshaft 30 is received and supported within a bore 32-1 provided in the crankcase or bearing head 32, while the elongated shaft portion 30-1 extends outwardly from the bearing head. There is. Hole 32-1 is located within tubular portion 32-5 and communicates with hole 32-4 via annular shoulder 32-2 and annular recess 32-3.

The shoulder portion 32-2 controls upward axial movement of the crankshaft 30 due to electromagnetic force during startup or unbalanced gas pressure during abnormal operation. Radial throwers 1-32-6 and 3 are located within an annular recess 32-8 provided on surface 32-9.
2-7 are formed, such slots cooperating with Oldham joints in the usual manner. A sleeve portion 32-10 is disposed coaxially around the tubular portion 32-5, and both of them form an annular recess portion 32 for accommodating oil.
-11 is formed, and the oil collected there is passed through the passage 32.
-12. As shown in detail in FIGS. 13 and 14, the bottom of the recess 32-11 is divided by webs 32-20 into four sections each spaced apart by an angle of 90'; Stiffness is provided by such a web.

An annular shoulder 32-13 is formed on the inner wall of sleeve portion 32-10 and supports the stator of the motor. An annular recess 32-14 is formed in the bore 32-1 to define oil debris, which supplies a quantity of lubricating oil to lubricate the crankshaft and journal surfaces. Recesses 32-15 and 32-16 are formed on the outer wall surface of the sleeve portion 32-10 and are arranged at both ends in the diametrical direction and extend in the axial direction. 20-1 and 20-2. Radial notches 32-17 and 32-18 form sleeve portion 3.
2-10 through recesses 32-15 and 32, respectively.
-16. Screw (, 1 axial hole 3
Pol l-40 is accepted within 2-21. 1st
The counterweight shown in FIG. 7 is mounted in a suitable manner on the flange portion 30-3 of the crankshaft 30, so that the dynamic forces due to the eccentric shaft portion 30-4, the swirl volute 21 and the Oldham joint 36 are The imbalance of is canceled out.

18 to 20, reference numeral 14 generally indicates a volute compressor, which is composed of an upper shell 15-1, an intermediate shell 5-2, and a bottom shell 15-3. It has a shell 15 consisting of three parts.

The shells 15-1 to 15-3 are welded together, with a portion of the top shell 15-1 and the bottom shell 15-3 being fitted into the middle shell 15-2, and the two of the top and bottom shells being welded together. The ends of the two shells define a shoulder that allows the compressor structure to be held in position as explained below. Suction pipe 1
6 and discharge pipe 17 extend within the middle shell 15-2 and the upper shell 15-1, respectively, and are suitably sealed by welding or the like. In addition, the suction pipe 16 is received in the hole 20-6 of the fixed volute 20, and the suction tube 16 is received in the hole 20-6 of the fixed volute 20, and the
It is sealed against the inside of shell 15 by ring 18. The eccentric shaft portion 30-4 of the crankshaft 30 is received in the hole 21-2 of the tubular boss 2]-1 of the swirl 21, and as shown in FIGS. 18 to 20, the eccentric shaft portion 30-4 The end of 4 is within the enlargement of hole 21-2, and the two are kept out of contact to prevent edge effects. The crankshaft 30 and the swirling volute 21 rotate together in the bore 32-4 with the flange portion 30-3 and the counterbalance m34, while the boss 21-1 is held against the pivoting movement of the swirling volute 2]. Shoulder portion 32-2 and tubular boss 21
The flange portion 30-3 disposed between -1 also functions as a thruster. The Oldham joint 36 is connected to the annular recessed portion 32
-8, radial grooves 21-12 and 21-13, and radial throwers I-32-6 and 32-7, whereby the Oldham joint 36
1 and the bearing head 32 in the usual manner, whereby the movement of the swirling volute 2] is limited to a swirling movement. A spacer ring 38 is attached between the stationary volute 20 and the bearing head 32 by a plurality of assembly bolts 40, which have port seals 41 to prevent leakage from the threads. The spacer ring 38 prevents the bolt 40 from being tightened so tightly that movement of the swirl volute 21 and the Oldham joint 36 is impeded. As best illustrated in FIG. 19, the spacer ring 38 has a pair of axially extending recesses 38-1 and 38-2 located at both diametrical ends.

If necessary, the spacer ring 38 is attached to the bearing head 3.
2 or as part of a fixed volute 20. However, for manufacturing reasons it is preferred that the spacer ring 38 is a separate part, since if it were a separate part the thickness of the spacer ring could be selected depending on the thickness of the plate or disc of the swirling volute 2. Because it can be done.

Crankshaft 30, bearing head 32, rotating spiral 2
1. The spacer ring 38, Oldham joint 36 and fixed volute 20 are all assembled together by bolts 40 as described above, and the stator 44-1 of the motor 44
is shrink fit into bearing head 32, thereby engaging stator 44-1 with annular shoulder 32-13 and holding it in place. When the stator 44-1 is fitted into a certain position, the rotor 44-2 is shrink-fitted onto the thin shaft portion 30-1 of the crankshaft 30. Rotor counterweight 44
-3 and 44-4 are provided on the rotor 44-2, thereby canceling out the inertia forces and moments of inertia exerted by the movement of the swirling volute 21 and the eccentric shaft 30-4. . The center of gravity of the swirling spiral 21 is the hole 2
It will be appreciated that the balance is maintained such that it lies on the 1-2 axis.

An oil pick-up tube 50 is inserted into the axial hole 20-9 provided in the stationary volute 20.

After that, the crankshaft 30, the bearing head 32, the rotating volute 21, the spacer ring 38, the Oldham joint 36, the fixed volute 20, the oil pickup pipe 50 and the motor 4.
4 is inserted into the intermediate shell 15-2. An opening 15- in which the suction pipe 16 is provided in the intermediate shell 15-2.
4 through O-ring 18 into hole 20-6, and then secured in place by welding or other suitable means. A gasket 19 is placed on the machined underside of the stationary volute 20, and the bottom shell 15-3 is then inserted into the intermediate shell 15-2 thereby forming a gasket between the bottom shell 5-3 and the stationary volute 20. One is tightened and then fixed to the intermediate shell 15-2 by welding or other suitable method. The upper shell] 5-1 is then inserted into the intermediate shell 15-2, thereby engaging the sleeve portion 32-10 of the bearing rad 32, and then secured to the intermediate shell 15-2 by welding or other suitable means. be done. Gasket 19 ensures separation of exhaust gas and lubricating oil. Once the assembly as described above is completed,
The internal compressor structure is mounted and equipped in a manner that is readily practicable in the production process.

In operation, as best illustrated in FIGS. 5 and 18, gaseous refrigerant is introduced into the centrifugal compressor 14 via the suction pipe 16 and through the holes 20-6. It reaches into the space surrounding the wraps 22 and 23. Such gaseous refrigerant is compressed in the manner illustrated in FIGS. 1-4. Referring now to FIGS. 7 and 19, compressed gaseous refrigerant is introduced through outlet 25 into bore 20-5 where the refrigerant fluid is divided into two portions. A first portion of the refrigerant flow sequentially passes from the hole 20-5 through a flow path defined by the inner surface of the intermediate shell 15-2 and the recesses 20-1, 38-1, and 31-15, and flows in the radial direction. The compressed refrigerant is introduced into the discharge pipe 17 through the notch 32-17 and beyond the stator 44-1, and the compressed refrigerant is supplied to the apparatus through the discharge pipe. Similarly, a second portion of the refrigerant flow passes from hole 20-5 through a channel defined by the inner surface of intermediate shell 15-2 and recesses 20-2, 38-2 and 32-16 in the radial direction. It passes through the notch 32-18, passes over the stator 44-1, and reaches the discharge pipe 17. intermediate shell 1
5-2 has a large body exposed to the atmosphere, and since the compressed refrigerant circulates while contacting the shell 15 before being discharged from the shell 15, the temperature of the discharged gas is effectively lowered. provides efficient cooling. Such a flow path requires the refrigerant to flow past the rotating rotor 44-2, so that the gas and oil mist is effectively centrifuged, thereby causing the oil to flow through the discharge pipe 17.
removed from the compressed refrigerant gas supplied to the The flow of refrigerant is indicated by the arrows in FIGS. 18 and 19. Second
The centrifuged oil flows downward, as shown by the arrows in Figure 0, through the holes in the motor 44 (not shown), the curved passageway (not shown) on the outer surface of the stator 44-1, and the sleeve portion 32-1. Recessed portion 32-11 through the inner surface of 10
leading to.

Since the interior of shell 15 is at compressor discharge pressure, such pressure can be used in conjunction with a centrifugal pump to supply lubricating oil defined by holes 30-5 and 30-6 in crankshaft 30. .

More specifically, the oil sump 48 defined by the bottom shell 15-3 is at compressor discharge pressure, and the oil pick-up tube 50 extends below the oil level. As long as such conditions are met, oil will be supplied through the oil pick-up pipe 50 if it is connected to a region at a pressure lower than the compressor discharge pressure. The location of the inlet of the oil pick-up tube 50 will need to be considered when the device is placed in a position other than a substantially vertical position. For example, when the compressor 14 is located at 20 degrees from the horizontal, the inlet of the oil pickup tube 50 may have to be located on one side of the shell 15. 1st
0 and 20 in detail, the compressor discharge pressure acts on the oil level in the oil sump 48, and this pressure causes oil to be introduced into the oil pick-up pipe 50, from where the oil is in turn sent to the shaft. It is introduced into the bottom of the axial hole 21-2 in the lower part of the eccentric shaft part 30-4 through the directional hole 20-9, the axial hole 21-4 and the radial hole 21-3. Due to the movement of the swirl vortex 21, the hole 21
-4 will be in motion relative to holes 20-9, but these holes are constrained such that there is always a lubricant flow path formed therebetween. To further explain, the hole 21-4 intersects the annular groove 21-14, thereby allowing the fixed volute 20 and the swirling volute 2
Lubricating oil is provided for lubrication of the thrust bearings between the two. Swirling vortex 2 whose pressure is below the discharge pressure of the compressor
A portion of the lubricating oil flows out from the hole 30-5 due to the pressure difference between the back pressure of the oil sump 1 and the discharge pressure of the compressor acting in the oil sump 48 alone or in combination with the centrifugal force of the hole 30-6. It flows into the hole 30-6, which acts as a centrifugal pressure pump, and is then conducted at a higher pressure than the compressor discharge pressure into the annular chamber defined by the annular recess 32-14 and the crankshaft 30 with a raised head. A seal against discharge gas is thereby provided.

Lubricating oil flows upwardly and downwardly from the annular recess 32-1.4, thereby lubricating the crankshaft 30. The lubricating oil that passes through the passage in the eccentric shaft portion 30-4 and flows upward,
From the bearing head 32 it flows downwardly along the tubular section 32-5 into the annular recess section 32-11 where it joins the lubricating oil which has flowed down by gravity after being centrifuged from the discharge gas as described above. . Lubricating oil is drained by gravity from the annular recess 32-11 via one or more oil drain passages 31-12, each of which in turn connects to the hole 38-3 of the spacer ring 38 and the fixed volute 20. It is connected to the oil reservoir 48 via the hole 20-11. This passage is the only passage that returns to the oil sump 48, and the compressed refrigerant that has passed through the hole passes through the gasket 1.
9 prevents oil from leaking into the oil reservoir 48. For example, even if refrigerant droplets get mixed into the lubricating oil and reach the liquid level in the oil sump or the rotor, the presence of a single gasket will prevent the lubricating oil from leaking and returning to the discharge passage. Ru. The compressor will thus operate safely even when completely submerged in lubricating oil.

An annular recess portion 3 defined by the hole 32-1 between the crankshaft 30 and the journal portion of the eccentric shaft portion 30-4
The lubricating oil flowing downwardly from 2-14 flows into an upper intermediate pressure chamber at a pressure below the discharge pressure and defined by bore 32-4, or within such a chamber, the eccentric shaft 30-4 and the counterbalance. The weight 34 rotates and the boss 21-1 pivots.

The lubricating oil supplied into the bottom of the axial hole 21-2, which is a part of the lubricating oil, is supplied to the eccentric shaft portion 30-4, the hole 21-2 and
The lubricating oil flows through the gap between the grooves 21 and 15, and the oil flows through the hole 32.
-4 into an upper intermediate pressure chamber. The entrained refrigerant is flushed by the lubricating oil flowing into the upper intermediate pressure chamber. Hole 32-
4, the upper intermediate pressure chamber is defined by the spacer ring 3.
8 and an annular recess 32-8 in constrained fluid communication with an annular lower intermediate pressure chamber within which the Oldham fitting 36 moves and forms a swirling volute. 21 turns. The constraint between the upper intermediate pressure chamber and the lower intermediate pressure chamber is the plane 32.
−9 and the swirling spiral 21. Hole 3
The lubricating oil in the upper intermediate pressure chamber defined by 2-4 serves to provide a seal, but once inside said chamber, the lubricating oil is forced between the flange portion 30-3 and the counterweight 34 and the shoulder portion 32-2. Works to lubricate. When properly balanced for thrust loads, shoulder 32-2 will be unloaded.

The lubricating oil and flushed refrigerant flowing out of the upper intermediate pressure chamber defined by hole 32-4 are transferred to hole 2-4.
1-9 and 21-10 to the wraps at a first point and through holes 21-11 to the wraps at a second point, such lubricating oil providing a seal between the wraps 22 and 23. , the compressed gaseous refrigerant is confined at a pressure below the compressor discharge pressure. As the lubricating oil flows into the lower intermediate pressure chamber defined by the spacer ring 38 and the annular recess 32-8, the lubricating oil leaks between the contact surfaces of the surface 32-9 and the swirling volute 21, thereby preventing such contact. The surfaces are lubricated, but the lubricating oil pressure decreases while moving from the upper intermediate pressure chamber to the lower intermediate pressure chamber. The lubricating oil in the lower intermediate pressure solenoid chamber defined by the spacer ring 38 and the annular recess 32-8 is
Lubricate the Oldham joint 36, and then lubricate the holes 21-7 and 21-8.
through holes 21-10 and 2 to provide a seal between the wraps, thereby providing a seal between the wraps.
1. A compressed gaseous refrigerant is confined at a pressure below that of the lubricating oil supplied via -11. Hole 21
-7.21-8.21-10 and 21-1.1 are in fluid communication with the gas compressed between the wraps but at a pressure below the discharge pressure, and therefore the oil sump at the discharge pressure. A pressure difference is created and the necessary pressure difference is provided for the oil to flow.

The volute compressor 14 according to the invention can operate by using two backpressure chambers even when a single magnitude of backpressure acts on the vortex 21, but the rotation of the counterweight 34 The motion agitates the lubricating oil thereby removing saturated refrigerant contained within the lubricating oil. As a result of centrifugal force, the lubricating oil is moved outward from the center of rotation and the separated gaseous refrigerant is injected back into the volute along with the oil, thereby increasing efficiency. The remaining lubricating oil passes between the sealing surfaces defined by surface 32-9 and swirl volute 21 and is introduced into the lower intermediate pressure chamber defined by spacer ring 38 and annular recess 32-8; The thrust surface and Oldham joint 36 are lubricated by this. After that, the lubricating oil is poured into hole 21-5.
and 21-6, and is sprayed into the swirl element via holes 21-7 and 21-8, respectively. Because the axial forces are balanced by the two backpressures in each chamber, the pressure in the lower intermediate pressure chamber is lower than if the entire backpressure chamber were exposed to a single intermediate pressure. The pressure differential between the suction plenum and the lower intermediate backpressure chamber is thus reduced, thereby reducing the potential for leakage.

While the best embodiment of the invention has been illustrated and described, other modifications will occur to those skilled in the art. Accordingly, the invention should be limited only by the scope of the claims that follow.

[Brief explanation of the drawing]

Figures 1 to 4 are schematic diagrams showing the relative positions of the wraps rotated by 90°. FIG. 5 is a front view of the fixed spiral. FIG. 6 is a cross-sectional view taken along line 6--6 of FIG. FIG. 7 is a cross-sectional view taken along line 7--7 of FIG. FIG. 8 is a cross-sectional view taken along line 8--8 of FIG. FIG. 9 is a front view of the swirling spiral. FIG. 10 is a cross-sectional view taken along line 10-10 of FIG. FIG. 11 is a cross-sectional view taken along line 11--11 of FIG. 9. FIG. 12 is a cross-sectional view taken along line 12--12 of FIG. FIG. 13 is a partially cutaway bottom view of the bearing head. FIG. 14 is a cross-sectional view taken along line 14--14 of FIG. 13. FIG. 15 is a cross-sectional view taken along line 15'-15 of FIG. 13. FIG. 16 is an axial cross-sectional view of the crankshaft. FIG. 17 is a schematic diagram of a counterweight. FIG. 18 is a vertical cross-sectional view of the centrifugal compressor along a section corresponding to line 6--6 of FIG. FIG. 19 is a vertical cross-sectional view of the centrifugal compressor along a section corresponding to line 7--7 of FIG. FIG. 20 is a vertical cross-sectional view of the centrifugal compressor along a section corresponding to line 8--8 of FIG. A-M...Chamber, 1-12...Chamber, ]4
...Vortex compressor, 15...Shell, 15-1...
・Upper shell, 15-2...Middle shell, 15-3・
...Bottom shell, 15-4...Opening, 16...Suction pipe, 17...Discharge pipe, 18...○Ring, 19...
·gasket. 20...Fixed spiral, 20-1.20-2...Recessed part, 20-3.20-4...Shelf, 20-5.20-
6...hole, 20-7...groove, 20-8.20-9.
20-10...hole, 21...swirling spiral, 21-1
... Boss, 21-2 to 21-11 ... Hole, 21-1
2-21-15...Groove, 22.23...Wrap, 2
5...Discharge port, 26...Fixing screw, 30...Crankshaft, 30-1.30-2...Shaft portion, 30-3...
Flange part, 30-4... Eccentric shaft part, 30-5.30
-6...hole, 32...bearing head, 32-1
... Hole, 32-2... Shoulder part, 32-3... Recessed part, 32-4... Hole, 32-5... Tubular part, 32-
6.32-7...Slot. 32-8... Recessed portion, 32-9... Surface, 32-1
0...Sleeve part, 32-11...Recess part, 32
-12...Aisle, 32-13...Shoulder, 32-14
．． 32-15.32-16... Recess portion, 32-1.
7.32-18...notch, 32-20...web, 32-21...hole, 34...counterweight, 36...
・Oldham joint. 38... Spacer ring, 38-], 38-2... Recessed part, 38-3... Hole, 40... Bolt, 41...
- Bolt seal, 44...Motor, 44-1...Stator. 44-2...Rotor, 44-3.44-4...Balance weight, 48...Oil sump, 50...Oil pickup pipe Patent applicant Carrier Corporation fee
Masa Akashi, Patent Attorney
Tsuyoshi FIG, 7 FIG, 2 ・I FIG, 3 ■; FIG, 4 FIG. / 6271

Claims (5)

[Claims] (1) A highly gas-tight volute compressor capable of being used in any position tilted between the vertical and horizontal directions within an angle of at least 20°, having an intermediate shell and one gas-tight a top shell and a bottom shell received and attached in a suitable manner to said intermediate shell to form a shell; said top shell being secured by bolts with a spacer device interposed therebetween and within said airtight shell; a bearing head device and a stationary volute device disposed between the shell and the bottom shell, the bearing head device being configured to engage the top shell and the stationary volute device engaging the bottom shell. a bearing head arrangement and a stationary volute; a rotating volute movable relative to said stationary volute; and a rotation operably mounted on said volute to prevent rotation of said volute. a restriction device; a first end extending upwardly through the bearing head device; and a second end of the swirling volute, the swirling volute being disposed at the second end and capable of driving the swirling volute. a crankshaft arrangement having an eccentric shaft portion coupled to the crankshaft arrangement; a rotor fixedly attached to the first end of the crankshaft arrangement; and a stator at least partially received within the bearing head arrangement. a suction device for supplying refrigerant to the fixed volute device and the rotating volute device; a discharge device extending axially from the upper shell; and a motor device for supplying lubricating oil to the volute compressor. an apparatus for defining a lubricating oil distribution channel for the lubricating oil distribution channel, the lubricating oil distributing channel having one end fluidly connected to the lubricating oil distributing channel and the other end disposed within the bottom shell defining an oil sump. an oil pickup tube, the second end configured to be positioned below the liquid level of the sump and in a selected direction of the centrifugal compressor; A volute compressor comprising: (2) A highly airtight spiral compressor, comprising a casing device having an inlet and a discharge pipe extending through the casing device, and a wrap formed inside the casing device. a stationary volute, the wrap being configured to be in fluid communication with the inlet at an outer portion; a swirling volute having on one side a wrap delimiting a closed space and a boss having an axial hole on the other side; a crankshaft device having an eccentric shaft portion for producing movement of the swirling volute device, the crankshaft device being supported in the crankshaft device and being received in the axial hole of the boss; a bearing head arrangement through which the other end of the shaft arrangement extends; a motor arrangement operably coupled to the other end of the crankshaft arrangement for rotating the crankshaft arrangement; a fixed volute device and said bearing head device cooperate to define a chamber within which said volute volute device can move; a rotation limiting device for cooperating to limit the motion of said swirling volute to a pivoting motion relative to said stationary volute; and an oil disposed within said casing arrangement having oil at compressor discharge pressure. a sump; and directing oil from the sump into the axial hole of the boss to provide a thrust force to maintain the stationary volute and the rotating volute against the forces of compressed gas between the wraps. A volute compressor comprising: a feeding device; and a volute compressor. (3) A casing device which is a highly airtight spiral compressor and has an inlet and a discharge pipe extending through it in the axial direction; a fixed spiral device having a helical wrap, the wrap being configured to have an outer portion in fluid communication with the inlet and an inner portion having an axial outlet; and the shaft; at least two radially extending recesses provided in the periphery of the fixed volute device and cooperating with the casing device to form a fluid passage; a swirling volute having on one side a helically shaped wrap disposed within the casing device and cooperating with the wraps of the stationary volute device to define a plurality of enclosed spaces; a crankshaft device having opposite ends, one end of which is operably coupled to produce motion of the swirling device; a bearing head arrangement extending therethrough and including a sleeve portion, the other end of the arrangement being operably coupled to the other end of the crankshaft arrangement for rotating the crankshaft arrangement; a motor arrangement including a rotor and a stator disposed at least partially within a bearing head arrangement; and a motor arrangement comprising a rotor and a stator disposed at least in part within a bearing head arrangement; and a motor arrangement disposed at an outer periphery of the sleeve portion and cooperating with the casing arrangement to provide the fixed volute arrangement and the casing arrangement. at least two recesses configured to communicate with each of the fluid passages defined therebetween; and at least two recesses configured in the sleeve portion of each of the recesses to form communication between the fluid passages. a radial notch configured to distribute the fluid passageway inwardly toward the motor device; and a radial notch configured to distribute the fluid passageway inwardly toward the motor device; a rotation limiting device for limiting movement of the device to a pivoting motion relative to the fixed volute device; an oil sump disposed within the casing device; and a device for lubricating the volute compressor; During operation, a gaseous refrigerant is introduced between the casing device and the wrap through the inlet, is confined in a closed space by the cooperation of the wraps, is compressed, and is supplied to the axial outlet. and such compressed refrigerant is divided into a plurality of streams, each of which in turn connects one of the radially extending discharge ports to the fluid passageway between the stationary volute device and the casing device. a corresponding one of the fluid passages in thermal contact with the atmosphere for heat exchange, and a continuity of the fluid passage defined between the sleeve portion and the casing device, the flow being flowing through a corresponding one of the radial notches;
A spiral compressor characterized in that the motor device is cooled before the gaseous refrigerant passes through these fluid passages and passes through the axially extending discharge pipe. (4) A method of assembling a highly airtight centrifugal compressor that can be used in any position tilted between the vertical and horizontal directions at an angle of at least 20 degrees, comprising at least a portion of the counterweight. mounting a counterweight on the flange portion of the crankshaft such that the counterweight is disposed radially outwardly of the eccentric shaft portion of the crankshaft; and a chamber for locating a rotation limiting device operatively coupled to the swirling volute. one end extending through the bearing head and received in the bore of the whirlpool boss to define a thrust member between the bearing head and the whirlpool boss by a flange portion of the crankshaft. disposing the crankshaft having the eccentric shaft portion together with a spacer ring and a rotating volute between a fixed volute and a bearing head and fixing the crankshaft with bolts; and fitting a stator of a motor into the bearing head, and fixing the crankshaft with a spacer ring and a rotating volute; on the end of the crankshaft extending through the bearing head; and inserting the assembly consisting of the crankshaft, bearing head, fixed volute, rotating volute, spacer, rotation limiter and motor into the intermediate shell. inserting the suction pipe into the intermediate shell and fixing it in a fixed position to fluidically connect the suction pipe and the suction gas supply; defining a portion of the oil distribution passage; inserting an oil pick-up pipe into a hole provided in a fixed volute, whereby the inlet end of said oil pick-up pipe is placing the lower shell defining the sump below the liquid level of the sump; inserting the lower shell defining the sump into the intermediate shell and engaging the fixed volute; and attaching the lower shell to the intermediate shell in a suitable manner. inserting an upper shell including an axially disposed discharge tube into said intermediate shell and engaging said bearing head; and said assembly being held in position by said upper shell and said lower shell. The upper shell is connected to the intermediate shell such that the upper shell is held stationary and the compressor can be operated at a preselected position determined by the position of the inlet end of the oil pickup tube within the sump. installation method in a suitable manner and assembly method including the steps of . (5) A method of lubricating a centrifugal compressor with high airtightness, maintaining the oil sump at the compressor discharge pressure, and lubricating the inlet located below the liquid level in the oil sump and the inlet of the centrifugal pump. creating a pressure differential in a first fluid passageway having a fluidically connected outlet, thereby causing lubricating oil to flow from the sump to the centrifugal pump; and lubricating oil supplied to the centrifugal pump. supplying lubricating oil to the first and second crankshaft lubrication passages at a pressure higher than the compressor discharge pressure; and introducing lubricating oil from the first crankshaft lubrication passage to the inside of the shell of the centrifugal compressor. , the lubricating oil is passed through the second crankshaft lubricating passage in order to lubricate the first thrust surface, passed through the first chamber, and introduced into the second chamber, thereby being introduced into the second chamber. A lubrication method comprising the steps of: lubricating a rotation limiting device arranged therein; and returning the lubricating oil after the lubricating action to the oil reservoir.