JPH0128231B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement of a slide vane type rotary compressor, which prevents the occurrence of chattering noise during startup and steady operation, improves the sealing performance in the compression chamber, and improves its compression. Its purpose is to increase effectiveness.

In general, a slide vane type rotary compressor has a compression chamber in a space defined by a cylinder block with a cylindrical or elliptical hollow part and front and rear side plates to rotate the rotor. The rotor is provided with a vane groove oriented in the radial direction, and the vane is provided in the vane groove so that it can freely move in and out of the compression chamber. The compressing effect is obtained by rotating the vane, but the conventional method of applying back pressure to this vane is to use the lubricating oil stored in the separation chamber through the discharge pressure. A commonly used method is to supply lubricating oil into the vane groove and push out the vane through the lubricating oil. However, with this method, although the extrusion action of the vane can be reliably obtained and the lubrication and sealing action in the vane groove can be effectively obtained, the power consumption is large and the wear loss at the vane tip is large. In addition to this, in the method described above that uses discharge pressure to obtain the vane extrusion action, lubricating oil is used until a constant discharge pressure is obtained in the compressor. The disadvantage is that the vane cannot be forcibly pushed out. In other words, at the time of startup, the compression action is obtained by pushing out the vanes through the action of centrifugal force until a constant discharge pressure is obtained. The state in which the vane is pushed into the compression chamber by the action of force is extremely unstable, and it goes without saying that no effective compression action can be obtained during this period, and the vane may collide with the cylinder block. As a result, a problem arises in that a chattering sound is generated.

The present invention is an attempt to improve the conventional situation as described above, by providing an oil supply groove on the side plate side corresponding to the rotation locus of the back pressure chamber provided at the base of the vane groove. The oil supply groove is provided so that it can communicate with the lubricating oil reservoir provided in the separation chamber and the compression chamber during the compression stroke, and at the time of startup, the refrigerant gas whose pressure is slightly increased in the compression chamber is supplied. By supplying the vane into the vane groove, it is possible to forcibly push the vane out into the compression chamber at the same time as the rotor starts, which prevents the generation of charing noise at the time of start-up. The lubricating oil stored in the vane groove is supplied to the oil supply groove through discharge pressure, and a portion of the lubricating oil is sent into the back pressure chamber formed at the base of the vane groove, thereby improving the lubrication and sealing properties in the vane groove. By improving the sealing effect in this part, it is ensured that the vane is pushed into the compression chamber, which prevents chattering noise during steady operation, and also prevents some of the lubricating oil from being generated. The feature is that the sealing performance of each compression space defined between each vane is improved by feeding the compressor into the compression stroke of the compression chamber, thereby increasing the compression effect.

That is, the gist of the present invention is to provide an oil supply groove to one of the front and rear side plates provided along both end surfaces of the rotor in correspondence with the rotation locus of the back pressure chamber formed at the base of the vane groove. The oil supply groove is provided in such a way that when the tip of the vane slides into the top position, the back pressure chamber of the vane groove into which the vane is inserted communicates with the oil supply groove. The oil supply groove is configured to communicate with a lubricating oil reservoir formed in the separation chamber and the compression stroke of the compression chamber, respectively.

Compressors structurally similar to the present invention include:
Of the pair of front and rear side plates that slide on both the front and rear end surfaces of the rotor, an annular oil groove is provided on the inner surface of the rear side plate along the rotation locus of the vane groove.
The oil groove communicates with the lubricating oil reservoir, while relief holes are provided discontinuously in the front side plate to correspond to the rotation locus of the vane groove, and the relief holes communicate with the suction stroke of the compression chamber. Japanese Utility Model Publication No. 45-30767 proposes a compressor in which a part of the lubricating oil supplied to the vane groove is connected to the suction hole of the compression chamber through a relief hole. It is characterized by improving the lubricity and sealing performance in the compression chamber by sending it during the stroke, and at the time of startup, the compressed refrigerant gas is pumped into the vane groove during the compression stroke of the compression chamber. This object is completely different from that of the present invention, which is characterized in that the vanes are pushed into the compression chamber at the same time as the rotor is started by supplying the rotor, thereby preventing the generation of chattering noise at the time of start-up. Furthermore, the above compressor is significantly different from the present invention in that it suffers from the following problems.

When the lubricating oil in the vane groove is sent into the compression chamber during the suction stroke, the refrigerant gas that is being compressed in the compression chamber is superheated and expanded, resulting in an increase in motive energy and a rise in discharge temperature.

Immediately after the operation is stopped, a large amount of lubricating oil in the vane groove flows into the compression chamber.

Back pressure is applied to the vanes via discharge pressure, and back pressure is applied to the vanes throughout the entire stroke from suction to discharge, thereby increasing power energy.

Specific embodiments of the present invention will be described below with reference to illustrative drawings. 1 to 3 are drawings showing a first embodiment, and 1 indicates a housing forming the outer shell of the compressor. The housing 1 is made up of a rear housing 2 having a bottomed cylindrical shape with an opening at one end, and a front housing 3 covering the opening of the rear housing 2. 4
1 is a cylinder block built into the housing 1, and the cylinder block 4 is formed into a hollow cylindrical shape with openings at both front and rear ends.
Reference numerals 5 and 6 denote a pair of front and rear side plates built into the housing 1 so as to cover both the front and rear openings of the cylinder block 4, where 5 is a front side plate and 6 is a rear side plate. Reference numeral 7 denotes a drive shaft which is disposed horizontally between both side plates 5 and 6 with its center line offset relative to the cylinder block 4, and a rotor 8 is integrally fixed to the drive shaft 7. The rotor 8 is built into the cylinder block 4 so that a part of its outer peripheral wall can slide against the inner wall surface of the cylinder block 4, and there is a space between the outer peripheral wall of the rotor 8 and the inner wall surface of the cylinder block 4. A compression chamber 27 is formed. 9
... indicates vane grooves carved at four locations on the rotor 8. Each vane groove 9 is provided in a penetrating manner in the longitudinal direction of the rotor 8, that is, in the axial direction, between both the front and rear end surfaces, as shown in FIG. Each vane groove 9 has a back pressure chamber 9' at its base, into which a vane 10 is fitted so as to be freely retractable.

A suction chamber 11 is provided between the front housing 3 and the front side plate 5, and a connection port 11' for a suction pipe (not shown) is provided. Further, the front side plate 5 has an inlet port 12 opened corresponding to one end of the compression chamber 27, that is, a starting end along the rotational direction of the rotor 8. On the other hand, at a position corresponding to the other end of the compression chamber 27, that is, the terminal end along the rotational direction of the rotor 8, a part of the cylinder block 4 is cut out to form a discharge chamber 13 between the cylinder block 4 and the inner wall surface of the rear housing 2. The discharge chamber 13 and the terminal end of the compression chamber 27 are communicated with each other by a discharge port 14. Reference numeral 15 indicates a discharge valve that covers the discharge port 14, and reference numeral 16 indicates a retainer that regulates the opening angle of the discharge valve 15.

Reference numeral 17 denotes a lubricating oil separation chamber formed between the rear wall portion of the rear housing 2 and the rear side plate 6, and the separation chamber 17 communicates with the discharge chamber 13 through a through hole 18 opened in the rear side plate 6. A filter 19 is provided at the tip of the through hole 18. A connection port 17' for a discharge pipe (not shown) is opened in the separation chamber 17, and a reservoir 20 for lubricating oil separated by the filter 19 is formed at the lower end of the separation chamber 17. Ru. 21 is the rear side of the rear side plate 6,
The bearing cover 21 is fitted in a position corresponding to the bearing portion of the drive shaft 7 supported on the rear side plate 6, and the bearing cover 21 is provided with a bearing chamber 21'. On the other hand, an oil supply groove 22a and a pressure groove 23 are formed on the inner surface of the rear side plate 6, that is, the surface that comes into sliding contact with the rear end surface of the rotor 8. The oil supply groove 22a and the pressure groove 23 are provided in an arc shape along the base of the vane groove 9 provided on the rotor 8 side, that is, along the rotation locus of the back pressure chamber 9' provided in the same portion.

The oil supply groove 22a is connected to the other end of the compression chamber 27, that is, the rotor 8.
The discharge port 14 is provided on the terminal end side along the rotational direction of the discharge port 14 . More specifically, as shown in FIG. 2, when the tip of the vane 10 is in sliding contact within the range S at the top position, the back pressure chamber 9' formed at its base communicates with the oil supply groove 22a. It is set up so that it can be obtained. And the oil supply groove 22a
is the reservoir 2 formed at the lower end of the separation chamber 17.
0 through an oil supply hole 24 rising from the reservoir 20. Further, an injection hole 25 extends from the oil supply groove 22a, and its tip opening 25' is provided so as to face the compression chamber 27 during the compression stroke. That is, the compression chamber 27 is provided so as to be intermittently communicated with the back pressure chamber 9' of each vane groove 9 provided on the rotor 8 side via the injection hole 25 and the oil supply groove 22a. The tip opening 25' of the injection hole 25 has a relatively discharge port so as to obtain a compression pressure state in which the average value of the compression pressure is lower than the discharge pressure and the minimum value of the compression pressure is higher than the suction pressure. It is located near 14.

On the other hand, the pressure groove 23 is provided so as to be continuous with the oil supply groove 22a from the starting end side along the rotational direction of the rotor 8, that is, from the top position to a position corresponding to the opening of the suction port 12. The pressure groove 23 is provided so as to communicate with a compression chamber 27 via a pressure guiding path 26. That is, a pressure guiding groove 26a extends from the pressure groove 23, and the pressure guiding groove 26a is connected to the bearing chamber 21'.
The same bearing chamber 2
A pressure guiding hole 26b extends from the pressure guiding hole 2'.
The tip opening of 6b is provided so as to face the suction stroke side of the compression chamber 27. In addition, the pressure guide path 26 and the pressure groove 2
3 may be communicated directly without using a bearing.

FIG. 4 is a drawing showing the second embodiment,
Oil supply grooves 22b are formed on the inner surface of the front side plate 5, that is, on the surface in sliding contact with the front end surface of the rotor 8, in correspondence with the oil supply grooves 22a formed on the rear side plate 6 side. An injection hole 25 extends from the oil supply groove 22b, and its tip opening 25'
is provided so as to face the compression stroke of the compression chamber 27.

Next, its effect will be explained. In the first embodiment shown in FIGS. 1 to 3, when the compressor stops operating, the pressures of the suction chamber 11, compression chamber 27, discharge chamber 13, and separation chamber 17 are balanced. is in a state of However, when the pressure of each part is balanced like this, if an electromagnetic clutch (not shown) provided at one end of the drive shaft 7 is connected and operated to operate the compressor, the driving force of the engine is transferred to the drive shaft 7. A state is obtained in which the drive shaft 7 and the rotor 8 rotate together. As the rotor 8 rotates, each vane 10 inserted into each vane groove 9 jumps out into the compression chamber 27 due to the action of centrifugal force, and rotates within the compression chamber 27 from the starting end toward the terminal end. The state is obtained. And like this, each vane 1
The refrigerant gas sucked into the compression chamber 27 through the negative pressure generated in the compression chamber 27 by starting rotation with the refrigerant 0 ... protruding into the compression chamber 27 is partitioned by each vane 10 ... In this way, the vanes 10 are pushed out into the compression chamber 27 due to the action of the centrifugal force and begin to rotate. The inside of the compression chamber 27 has the effect of slightly compressing the refrigerant gas during the compression stroke. In the compression chamber 27, a pressure state slightly higher than that in other parts is obtained, although momentarily. (The refrigerant gas compressed in the compression chamber 27 is sent to each other part, so that the same pressure state as in the compression chamber 27 will be obtained in each part eventually.
There is a time lag before the pressure becomes the same as inside 7. ) During the compression stroke, the compression chamber 27 is in communication with the oil supply groove 22a through the injection hole 25, so that part of the refrigerant gas slightly compressed during the compression stroke of the compression chamber 27 as described above. is sent into the oil supply groove 22a through the injection hole 25. That is, the injection hole 2 in the compression chamber 27 is located in the oil supply groove 22a.
The same pressure state as in the opening position No. 5 is obtained. On the other hand, when the tip of the vane 10 slides in the range S at the top position through the rotation of the rotor 8, the back pressure chamber 9' formed at the base of the vane groove 9 into which the vane 10 is inserted is filled with the oil. A state of communication with the groove 22a is obtained. By establishing a state in which the back pressure chamber 9' communicates with the oil supply groove 22a, the refrigerant gas in the oil supply groove 22a is sent to the back pressure chamber 9'. That is, there is also a compression chamber 27 within the back pressure chamber 9'.
As in the compression stroke, a slightly higher pressure state is instantaneously obtained. Since a slightly high pressure state is obtained in the back pressure chamber 9' in this way, the vane 10 is pushed out into the compression chamber 27 through the same pressure state, and its tip touches the inner wall surface of the cylinder block 4. A state of sliding contact is obtained. That is, the vane 10 is pushed out at the same time as the rotor 8 is activated,
The tip portion can be brought into sliding contact with the inner wall surface of the cylinder block 4, and an effect of preventing the occurrence of chattering noise can be obtained.

As described above, the state in which the back pressure chamber 9' of the vane groove 9 communicates with the oil supply groove 22a is instantaneously disconnected. The back pressure chamber 9' of the vane groove 9 which is out of the oil supply groove 22a is shielded by both the front and rear side plates 5 and 6. Since the back pressure chamber 9' is shielded by the left and right plates 5 and 6, the refrigerant gas sent into the back pressure chamber 9' is sealed in the back pressure chamber 9' under a slightly higher pressure state. Ru. In this way, by filling the back pressure chamber 9' with refrigerant gas under a slightly high pressure state, the state in which the vane 10 is pushed out is maintained.

Back pressure chamber 9' of vane groove 9 into which vane 10 is inserted
When the back pressure chamber 9' is rotated to a position corresponding to the pressure groove 23, the back pressure chamber 9' is released from being shielded by the front and rear side plates 5, 6 and is now in communication with the pressure groove 23. It will be done. Therefore, the pressure groove 23 is provided so as to communicate with the compression chamber 27 near the suction stroke via the pressure guiding path 26.
Since the same pressure state (the same pressure state as the suction pressure or a pressure state slightly higher than the suction pressure) is obtained in the pressure groove 23 as at the opening position of the pressure guiding hole 26b, the pressure is increased as described above. By communicating the back pressure chamber 9' of the vane groove 9 with the groove 23, the refrigerant gas in the pressure groove 23 is fed into the back pressure chamber 9'. By feeding the refrigerant gas in the pressure groove 23 to the back pressure chamber 9' in this way, the refrigerant gas supplied in the back pressure chamber 9' is sealed in a state in which it communicates with the oil supply groove 22a. At the same time, the vane 10 is continuously pushed out into the compression chamber 27, and a state is obtained in which the vane 10 is rotated while its tip is brought into sliding contact with the inner wall surface of the cylinder block 4.

When the back pressure chamber 9' of the vane groove 9 into which the vane 10 is inserted has rotated to the terminal end of the pressure groove 23, the back pressure chamber 9' is no longer in communication with the pressure groove 23, and the back pressure chamber 9' Again, both front and rear side plates 5,
6. Since the back pressure chamber 9' of the vane groove 9 is shielded by the front and rear side plates 5 and 6, the back pressure chamber 9' is filled with refrigerant gas, and through the filling action of the refrigerant gas. The state in which the vane 10 is pushed out toward the compression chamber 27 is maintained. The refrigerant gas sealed in the back pressure chamber 9' gradually leaks into the compression chamber 27 as the vane 10 rotates in the compression chamber 27 toward the terminal end. The vane 10 is pushed back into the vane groove 9 and the volume of the back pressure chamber 9' is gradually reduced. The pressure to compensate for the leakage of refrigerant gas as described above and to push out the vane 10 is reserved. That is, the vane 10 is pushed out toward the compression chamber 27, and its tip is inserted into the cylinder block 4.
A state is obtained in which the cylinder rotates during the compression stroke while being in sliding contact with the inner wall surface of the cylinder. Also, in this way, the vane 10 is connected to the compression chamber 2.
Since the action of pushing out in seven directions is obtained through the relatively low pressure in the compression chamber 27 at the beginning of the compression stroke, the friction loss at the tip of the vane 10 can be reduced.

As described above, each vane 10 is pushed out toward the compression chamber 27, and while its tip portion is in sliding contact with the inner wall surface of the cylinder block 4, the inside of the compression chamber 27 is pushed out from the starting end toward the terminal end. By rotating, the refrigerant gas sucked into the compression chamber 27 at the suction port 12 is forcibly sent from the starting end toward the terminal end within the compression space defined by each vane 10. In this way, the refrigerant gas is sent through the compression chamber 27 from the starting end toward the terminal end while being partitioned into a certain compression space via each vane 10. The effect of compressing is obtained. The refrigerant gas compressed in this way is then transferred to the discharge port 14 and the discharge chamber 1.
3. It is sent into the separation chamber 17 through the through hole 18. The refrigerant gas sent into the separation chamber 17 passes through the filter 19 to separate the lubricating oil contained in the refrigerant gas, and the lubricating oil becomes oil droplets and falls into the reservoir 20, while the lubricating oil is separated. The cooled refrigerant gas is sent to the discharge pipe through the connection port 17'.

Then, the refrigerant gas compressed in this way is discharged into the discharge chamber 1.
3 and into the separation chamber 17, the pressure in the separation chamber 17 is gradually increased. When the pressure exceeds the pressure near the tip opening 25' of the injection hole 25, the lubricating oil stored in the reservoir 20 is pushed up inside the oil supply hole 24 via the discharge pressure in the separation chamber 17 and is supplied with oil. It is supplied to the groove 22a. A portion of the lubricating oil supplied to the oil supply groove 22a is supplied into the back pressure chamber 9' in a state where the back pressure chamber 9' communicates with the oil supply groove 22a. The lubricating oil supplied into the back pressure chamber 9' acts as back pressure on the vane 10 fitted into the vane groove 9, and is also supplied into the gap formed between the vane groove 9 and the vane 10. , lubrication and sealing effects can be obtained for the same gap. This sealing action significantly acts to prevent leakage of the refrigerant gas sealed in the back pressure chamber 9' during the compression stroke. That is, during the compression stroke, the refrigerant gas sealed in the back pressure chamber 9' leaks out, pushing the vane 10 into the compression chamber 27, and maintains a state in which the tip thereof is in sliding contact with the inner wall surface of the cylinder block 4. As a result, the tip of the vane 10 separates from the cylinder inner wall surface, causing the cylinder block 4 to
Collision occurs between the refrigerant and the inner wall surface of the back pressure chamber 9', resulting in the generation of a chattering sound.However, by achieving the sealing effect described above, leakage of the refrigerant gas sealed in the back pressure chamber 9' is prevented and the back pressure chamber 9' is prevented from leaking. It is possible to ensure that the pressure within the pressure chamber 9' increases and prevent chattering noise from occurring.

A portion of the lubricating oil supplied into the vane groove 9 is further supplied into the gap formed between the inner wall surfaces of both the front and rear side plates 5 and 6 and the end surface of the rotor 8, and acts to lubricate and seal the gap. is obtained.

Another part of the lubricating oil supplied into the oil supply groove 22a is supplied into the compression chamber 27 through the oil supply hole 24. By supplying lubricating oil into the compression chamber 27, the sliding portions of the vane 10 that are in sliding contact with the cylinder block 4 and both the front and rear plates 5, 6 can be lubricated and sealed. That is, the sealing performance in the compression space defined by each vane 10 is improved, and the effect of reliably maintaining the compression pressure of the refrigerant gas in the compression space, in other words, the effect of increasing the discharge pressure is obtained. Although this oil has a high temperature, since it is injected into the highly compressed gas, the gas temperature has also increased, so there is no risk of excessive gas heating or expansion.

In the second embodiment shown in FIG.
Most of the lubricating oil pushed up and supplied into the oil supply groove 22a is supplied into the back pressure chamber 9'. The lubricating oil supplied into the back pressure chamber 9' acts as a back pressure to the vane 10, while the same lubricating oil is supplied into the gap formed between the vane groove 9 and the vane 10 to provide lubrication and Similar to the first embodiment, the lubricant can provide a sealing effect and is also supplied into the gap formed between the front and rear end surfaces of the rotor 8 and the front and rear side plates 5 and 6, thereby providing lubrication and sealing in the same area. However, the lubricating oil supplied into the back pressure chamber 9' is sent into the oil supply groove 22b formed in the back pressure chamber 9' and the front side plate 5 side in a state where the oil supply groove 22b is aligned with the back pressure chamber 9'. The lubricating oil fed into the oil supply groove 22b is fed into the compression chamber 27 through the injection hole 25. The lubricating oil thus supplied to the oil supply groove 22a passes through the back pressure chamber 9' and the oil supply groove 22b to the compression chamber 27.
By sending the lubricating oil into the interior, the flow of the lubricating oil is smoothed, and the lubricating oil is lubricated and sealed between the end faces of the vane 10 and the end faces of the front and rear side plates 5 and 6, and the lubrication between the vane groove 9 and the vane 10 is achieved. And the sealing action can be effectively performed over the entire area. Note that the sealing effect is more strongly required at lower speeds of rotation, but the lower the speed, the more easily the lubricating oil enters the back pressure chamber, so the sealing effect is greater.

The present invention is constructed as described above, and includes:
With the above configuration, the vanes can be forcibly pushed out at the same time as the rotor rotates at the time of startup, and as a result, it has become possible to prevent the occurrence of chattering noise at the time of startup.

Furthermore, the lubrication and sealing properties of the back pressure chamber in the vane groove can be improved during steady operation, and as a result, it has become possible to prevent the occurrence of chattering noise during steady operation.

Furthermore, during steady operation, it is possible to improve the sealing performance within each compression space defined within the compression chamber by the vanes, and as a result, it has become possible to improve the compression effect and increase the discharge pressure.

[Brief explanation of drawings]

1 to 3 are drawings showing the first embodiment, in which FIG. 1 is a side sectional view showing the entire compressor, FIG. 2 is a sectional view taken along line A-A in FIG. 1,
FIG. 3 is a sectional view taken along the line BB. Figure 4 is the second
FIG. 2 is a drawing showing an embodiment of the present invention, and is a side sectional view showing the entire compressor. 1...Housing, 2...Rear housing, 3
...Front housing, 4...Cylinder block, 5...Front side plate, 6...Rear side plate, 7...Drive shaft, 8...Rotor, 9...Vane groove, 9'...Back pressure chamber, 10 ……
Vane, 11... Suction chamber, 11'... Connection port, 1
2... Suction port, 13... Discharge chamber, 14... Discharge port, 15... Discharge valve, 16... Retainer, 17
...Separation chamber, 17'...Connection port, 18...Through hole,
19... Filter, 20... Reservoir, 21...
Bearing cover, 21'...Bearing chamber, 2
2a, 22b...Oil supply groove, 23...Pressure groove, 24
... Oil supply hole, 25 ... Injection hole, 25' ... Tip opening, 26 ... Pressure guide path, 26a ... Pressure guide groove, 26
b...Pressure hole, 27...Compression chamber.

Claims (1)

[Scope of Claims] 1. Inside a space formed by a cylinder block having a cylindrical or elliptical hollow part and formed into a cylindrical shape, and a pair of front and rear side plates that cover the front and rear openings of the cylinder block. A compression chamber is provided in the rotor to allow the rotor to rotate freely, a plurality of vane grooves are carved in the radial direction in the rotor, and a vane is fitted into each vane groove so as to be freely retractable into the compression chamber. The rotary compressor is a rotary compressor consisting of a rotary compressor, and one of the side plates is provided with an oil supply groove corresponding to the rotation locus of the back pressure chamber formed at the base of the vane groove. The back pressure chamber of the vane groove into which the vane is inserted is provided in such a way that it communicates with the oil supply groove when the vane is in sliding contact with the top position, and the oil supply groove is connected to the lubricant reservoir formed in the separation chamber and compressed. A slide vane rotary compressor characterized in that the compressor is provided so as to communicate with the compression strokes of the chambers. 2 A oil supply groove is carved in the other side plate in correspondence with the oil groove carved in the one side plate, and the oil supply groove carved in the one side plate communicates with the reservoir in the separation chamber. 2. The slide vane rotary compressor according to claim 1, wherein the oil supply groove cut into the other side plate communicates with the compression stroke inside the compression chamber.