US3434656A

US3434656A - Lubrication system for rotary vane compressors

Info

Publication number: US3434656A
Application number: US667841A
Authority: US
Inventors: Friedrich O Bellmer
Original assignee: Worthington Corp
Current assignee: Worthington Corp
Priority date: 1967-09-14
Filing date: 1967-09-14
Publication date: 1969-03-25
Anticipated expiration: 1986-03-25
Also published as: FR1600862A

Description

March 25, 1969 F. o. BELLMER LUBRICATION SYSTEM FOR ROTARY VANE' COMPRESSORS Filed Sept. 14, 1967 Sheet INVENTOR BELLMER FREDRCH O BY N' March 25, 1969 no. BELLMER 3,434,656l

` LUBRICATION SYSTEM FOR ROTARY vANE coMPREssoas Filed sept. 14, 1967 sheet 2 of 2 INVENiTOR FRIEDRICH O. BELLMER United States Patent O 3,434,656 LUBRICATION SYSTEM FOR ROTARY VANE rCOMPRESSOIRS Ihfiedrich 0. Bellmer, East Orange, NJ., assignor to Worthington Corporation, Harrison, NJ., a corporation of Delaware Filed Sept. 14, 1967, Ser. No. 667,841 Int. Cl. F04c 29/02, 23/02; F04d 29/06 U.S. Cl. 230-207 2 Claims ABSTRACT F THE DISCLOSURE A lubrication system for a sliding vane rotary com presser in which lubricating oil under pressure is supplied to a longitudinal groove in the trailing side of each vane slot as the vane passes the suction port so that oil will be distributed along the trailing side of the vane as the rotor turns. The oil is supplied to the grooves from an arcuate port in an end wall adjacent to the compressor suction inlet and at the same radial position as the longitudinal grooves. A corresponding drain port in the other end wall allows the grooves to be flushed before being relled with Oil.

Background of the invention This invention relates to sliding vane rotary compressors and more particularly to lubricating systems for these compressors. Systems of this type may be found under U.S. Patent Classifications 230, Subclass 207, 152.

The usual methods of lubricating the vanes in a sliding vane rotary compressor is to either inject oil directly into the compression chamber or to spray oil into the suction passages. In either case, lthe oil tends to be thrown out against the cylinder housing wall and does not eectively lubricate the rotor slots, where lubrication is needed due to the sliding movement of the vanes in and out under high loads. Besides `the poor efficiency of said vane lubricating system, the injection of oil into the compression chamber requires a controlled flow of oil to eliminate the danger of overloading and damaging the compressor.

On low speed compressors, central lubrication systems have been utilized in which oil under pressure flows through a central bore in the drive shaft and into the rotor slots filling up the space behind the vanes. The combined effect of the oil pressure and centrifugal force tends to force the lubricant outward along the slots so as to lubricate the vanes. The diiculty with these systems is that at high speed there is a tendency to develop hydraulic lock of the vanes when the vane is moving inward and the oil cannot bleed from the slot fast enough. This type of system is shown in U.S. Patent Nos. 3,016,184, 2,827,226 and 1,928,300.

Summary of the invention This invention overcomes these difficulties in the prior art lubrication system and provides a low cost efficient lubricating system which effectively lubricates the vanes in the areas where they are in contact with the rotor slots by supplying oil directly to the space between the trailing sides of the vanes and rotor slots.

Accordingly, it is an object of this invention to provide lubrication of the vanes at a point where they contact the rotor slot without lling up the space behind the vanes.

Another object of this invention is to provide a lubrication system for a sliding vane rotary compressor in which either a low pressure pump or the compressor discharge pressure can be used as the motive force for an effective lubrication system.

It is a further object of this invention to provide a low cost, simple lubrication system for a sliding vane rotary compressor which will insure lubrication for the trailing side of the vanes and for the vane tips.

lt is a further object of this invention to provide a lubricating system for a sliding vane rotary compressor` which does not require a high pressure oil pump.

It is a further object of this invention to provide a lubricating system for a sliding vane rotary compressor which supplies lubricating oil to the vanes only when they are subject to a low gas pressure so as to prevent blowback of oil to the pumping system due to compressed gas pressures acting on the oil supply system.

These and other objects will become more apparent from the following description of several embodiments of this invention.

Drawings FIGURE 1 is a vertical sectional viewl taken through the axis of a compressor embodying this invention.

FIGURE 2 is a sectional view taken through lines 2 2 of FIGURE l.

FIGURE 3 is a vertical sectional view taken through the axis of a compressor embodying a second embodiment of this invention.

FIGURE 4 is a sectional view taken through lines 4-4 of FIGURE 1.

FIGURE 5 is a schematic showing the relationship between the oil supply ports in the top and bottom end plates and three positions of a vane as it passes between the ports.

Referring particularly to FIGURES 1 and 2 there is shown a single stage double chamber sliding vane rotary compressor in a hermetically sealed motor compressor assembly 2. The compressor assembly includes a main support housing 4 which cooperates with upper shell member 6 and lower shell member 8 to form a compressor section and a motor section. An electric motor stator 10 is attached to the main support housing while a motor armature `12 is attached to the drive shaft 14 by a key 16. The armature drive shaft assembly is supported for rotary motion by the

roller bearings

18 and 20. A rotor 22 is attached to the drive shaft 14 by a key 24 for rotation in an elliptical shaped chamber formed by the housing 26, a bottom closure plate 28 and a top closure plate 30. The closure plates and housing are held together and fixed to the main support housing by appropriate clamping means, not shown.

Gas enters the assembly at inlet 32, is deflect-ed by baie 33 and is drawn into the compressor suction 36 via passage 34 after it has circulated over the electric motor elements to provide a cooling effect. Compressed gas leaves the compressor through discharge passages 38 and ows into compartment 40 where most of the oil entrained in `the gas is separated from the gas as the gas passes downward and around the deecting member 44. The compressed gas leaves the discharge compartment via outlet 46. The inside of the upper shell is lined with a noise damping material 47 to reduce the noise caused by the compressor.

The rotor is driven in `the direction of arrow 48 of FIGURE 2 and is furnished with radial slots 50` within which vanes 52 are freely movable so that as the rotor turns the outer ends of the vanes will tend to be held in engagement with the inner surface 54 of the elliptical cylinder 26 by centrifugal force. The compressor shown is a two chamber compressor in which there are two complete compression cycles for each cell formed between adjacent vanes as the motor makes one complete revolution in the cylinder housing. As an individual cell moves across the suction ports 36, the cell is charged with gas at suction pressure. As the rotor continues to rotate, the effective volume of the cell is decreased so that when the gas is discharged from the cell through the discharge passages it is at a much higher pressure than the suction pressure. As the rotor continues to turn, the cell is again charged with gas at suction pressure as it passes the second suction port and the cycle is then repeated.

The lubrication system includes a first reservoir 56, which is in the *discharge chamber and therefore at compressor discharge pressure, and a second reservoir 58 which is in the motor chamber and therefore at suction pressure. Float valve assembly 60 in line 62 holds the high pressure reservoir at a predetermined level so as to maintain a liquid seal between the high pressure side of the lubrication system and the low pressure side. An oil pump y64 is adapted to pump oil from the low pressure reservoir to symmetrical

arcuate ports

68 and 69 in the upper plate via central passage `67 in the drive shaft and

passages

71 and 73. The ports are located at an annular position adjacent to the suction passages. Longitudinal channels or grooves 70 extend axially along the trailing side of each slot. Each of the channels 70 registers with the

ports

68 and 69 as the vane passes the suction passages. The bottom plate 2S contains cooperating

arcuate ports

72 and 75 which begin at the same point as the ports in the upper plate but which are shorter than the ports in the upper plate so as to cut off communication between the ports in the bottom plate and the grooves 70 in the rotor before cutting oi communication between the ports in the top plate and the grooves. This is shown schematically in FIGURE which shows a port in the bottom plate superimposed over a port in the top plate and three positions of a vane as it passes these ports.

Ports

72 and 75 drain into low pressure reservoir 58 via oil return lines 74 and 76. Lubricating oil flows to the

bearings

18 and 20 via lines 77. Lubricating oil coming from the bearings ows down lines 7S and is thrown out into the suction gas stream by a spinner 79 where it is carried into the suction of the compressor to provide additional lubrication.

It will be apparent that the pump 64 will keep the

arcuate ports

68 and 69 in the top plate supplied with oil at all times While lines 74 and 76 will drain the

ports

72 and 75 in the lower plate. Referring to FIGURE 5 particularly, it will be seen that as rotor groove 70 iirst registers with the ports 68 and 72 (position a) lubricating oils will ow from the upper port through the groove and back to drain via the lower port and drain passages. This will till the groove 70 with a fresh supply of relatively cool oil. As the rotor continues to turn, the lower port will be cut off While the upper port continues to supply oil to the groove to insure that it is filled with oil (position b) until the upper port is also closed off (position c). As the rotor moves from the suction area into the compression portion of the cycle both the upper and lower ports are closed to prevent the high pressure in the cells between the vanes from acting against the pump pressure. As the rotor continues to turn, the oil in groove 70 -will be distributed along the trailing side of the vane. Some oil will be thrown out and will ow to the tips of the vanes to seal and lubricate between the vane tips and the cylinder wall. Some oil will ow inward and will get behind the vane where it will eventually discharge into the suction line via passage 79. It will be apparent that this lubrication cycle will repeat itself for each vane as it passes the suction ports.

FIGURE 4 is a sectional View showing the

arcuate ports

72 and 75 in the bottom plate 28 and the passages 77 for supplying oil to the

roller bearings

18 and 20.

FIGURE 3 shows another embodiment of the invention which differs from that shown in FIGURE l primarily in the means for supplying lubricating oil to the longitudinal grooves in the rotor. The basic compressor operation is identical to that shown in FIGURE l and it will not be described in detail.

1n this embodiment lubricating oil is supplied to the ports in the upper plate from a lubricating oil reservoir 80 maintained in the high pressure chamber. This reservoir will be at a pressure equal to the compressor discharge pressure which provides a convenient source of oil under high pressure. The oil is supplied to the upper ports 81 and `83 via filter 82 and

passages

84, 86 and 88. Restriction limits the maximum flow of oil. Oil being drained from the ports in the bottom plate 92 in the lower plate is fed to the bearings 94 and 96 via lines 9S, 99 and 160. The radial holes 102 provide a bypass for preventing a buildup of oil around the lower bearing 96. Passages 104 allow the oil to flow down to spinner 106 which causes the oil to be thrown out and into the flow path of suction gas entering the compressor at inlet 10S. A portion of the oil will be picked up by the suction flow and will be carried directly into the inlet. Some oil will not be picked up by the gas stream and will collect at the bottom of the motor housing 110. A small pump 112 pumps this oil directly into the inlet chamber 114 via

passages

116, 118 and 120.

Since the oil which drained into the motor housing can only be returned to the high pressure side of the system by being carried in the gas stream entering the compressor, there is a double lubrication effect, with the same oil which is supplied to the grooves in the rotor slots being carried back through the compressor along With the gas stream. It is therefore necessary to limit the flow of oil to the grooves. In the embodiment shown in FIGURE 1 any excess oil supplied to the slots is merely recirculated whereas in the embodiment of FIGURE 3 excess oil which passes through the grooves must become part ofthe gas flow entering the compressor at the same rate so as to maintain the reservoir in the high pressure side of the system.

Although a compressor embodying this invention has many applications, it can be used to particular advantage in a compression refrigeration cycle in which the gas being compressed is a refrigerant, such as Freon R-lZ and R-22.

What is claimed is:

1. A lubricating system for a sliding vane rotary compressor of the type having a slotted rotor with a plurality of vanes movable inward and out-ward thereof, a casing for the rotor having a cylindrical wall for guiding the vanes in their in and out movement, end walls closing the cylinder and circumferentially spaced gas inlet and outlet ports in the cylinder wall, the lubricating system comprising:

(a) an axially extending groove in the trailing side of each vane slot;

(b) an arcuate port in each end wall adjacent the suction inlet and at the same radial position as the grooves in the rotor slots so that each groove will pass between the ports as the rotor turns;

(c) means for supplying lubricating oil under pressure to the port in one end wall; and

(d) -means for draining oil from the port in the other enid wall; whereby each groove will be flushed and resupplied with oil each time it passes the inlet port.

2. The lubricating system as delined in claim 1 wherein the arcuate port being supplied oil is longer than the arcuate port being drained of oil so that the grooves in the trailing sides of the slots will be completely illed with oil after passing between the ports in the end walls.