JPS59180095A - Lubricating oil excessive supply preventing mechanism in compressor - Google Patents

Abstract

PURPOSE:To prevent the excessive supply of oil for a compression chamber by a method wherein an oil path is closed by a control valve mechanism provided in an oil supplying path connecting the oil sump and the compression chamber under a condition that the compressor has been stopped. CONSTITUTION:Under a condition that the operation of the compressor is stopped, a pressure in the compression chamber 6 leaks to the side of a suction chamber 9 through a gap formed between a rotor 5 as well as vanes 8...8 and both side plates 3F, 3R, therefore, pressures of respective parts in the compression chamber 6 become the same as a suction pressure. As a result, pressures in a high pressure chamber 23 and a low pressure chamber 24 become the same in the control valve mechanism 21 for opening and closing a path, which is provided in the oil supplying path 20 connecting the oil sump 17 and the compression chamber 6. A spool 22 is energized toward the high pressure chamber 23 by a spring 25 and blocks the oil supplying path 20, therefore, supply of oil for the compression chamber 6 is stopped and the excessive supply of the oil may be prevented.

Description

Detailed Description of the Invention Technical Field The present invention relates to a mechanism for preventing oversupply of lubricating oil in a compressor, and more specifically, a mechanism for lubricating sliding parts of a compression chamber using oil separated from compressed gas. The present invention relates to a lubricating oil supply mechanism installed in a lubricating oil supply mechanism.

In conventional compressors, one method of lubricating the sliding parts of the compression chamber is to separate the compressed gas from the compressed gas into a separation chamber (discharge chamber) d.
Conventionally, a method has been commonly used in which oil stored at the bottom is fed into the compression chamber via the pressure within the separation chamber.

However, in the above method, when the operation is stopped due to the operating state, a high pressure state remains in the separation chamber even after the operation is stopped, resulting in a problem that oil is supplied to the compression chamber. . That is, the oil supplied to the compression chamber after the operation is stopped accumulates in the compression chamber, thereby inducing liquid compression when the engine is restarted.

As an improvement plan for the above problem, for example, in a slide vane compressor, the oil reservoir formed at the bottom of the oil separation chamber is connected to the oil supply hole for applying back pressure to the vane formed in the compression chamber. An on-off valve is provided in the oil supply passage, and the on-off valve is connected to the compression stroke of the compression chamber, more specifically, the pressure immediately before being discharged from the discharge hole (hereinafter referred to as "pressure at the end of the compression stroke Pal"), and the pressure in the separation chamber. The on-off valve (2) is opened by the differential pressure generated between the pressure (discharge pressure) of A method of closing the oil supply passage to stop the supply of oil to the compression chamber (JP-A-55-134'785).

Alternatively, a check valve is provided in the communication part of the discharge port in a SKU IJ, - type compressor to prevent backflow from the discharge pipe when the compressor is stopped, and a discharge chamber (separation chamber) is installed. An oil injection passage is provided that communicates the oil reservoir formed at the bottom of the oil reservoir with the compression stroke of the compression chamber (more specifically, the position near the discharge hole), and the oil stored in the oil reservoir is transferred to the discharge chamber (separation chamber). Method of injecting into the compression chamber via the discharge pressure in the
No. 2) etc. have been proposed, but in the former method, the pressure JJP2L at the end of the compression stroke and the pressure Pd in the separation chamber are not always higher than the pressure Pa at the end of the compression stroke. That is, when high compression ratio operation is performed at low speed operation, the pressure "Pa" in the separation chamber may become higher than the average pressure acting on the pressure guiding hole of the pressure Pa at the end of the compression stroke (
(See FIG. 12), in this case, a problem arises in that the on-off valve is not opened during operation.

Also, in the latter method, when the compressor is not operating, the compressed gas sent into the discharge chamber flows backward through the discharge hole and the compression chamber and escapes toward the suction chamber (
Therefore, it is not suitable for compressors for vehicle air conditioning, which are frequently turned ON and OFF).In addition, even when the compressor is operating, some compressed gas flows back into the compression chamber and expands again, resulting in a large power loss. This causes a problem. As a means to prevent backflow from the discharge chamber to the compression chamber, there is a method of installing a discharge valve at the opening of the discharge hole (Utility Model Application No. 57-152490). Although the above problem can be resolved if a In other words, the same oil is stored in the compression chamber and causes a hydraulic pressure chamber when the engine is restarted.

Purpose of the Invention The present invention is an attempt to improve the conventional situation as described above. The purpose is to obtain an oil control mechanism.

Structure of the Invention In other words, the present invention opens the oil supply passage to the sliding part of the compression chamber when the compressor is operating, and at the same time closes the oil supply passage when the compressor stops operating. The operation of the compressor can be improved by providing a control valve that opens and closes the control valve using the differential pressure that occurs between the compression stroke of the compression chamber and the suction stroke of the suction chamber or compression chamber. The oil supply is cut off at the same time as the engine stops, thereby preventing oil from accumulating in the compression chamber and ensuring that the control valve can be opened and closed in any operating state. The gist of the present invention is that an on-off valve is provided so as to be movable forward and backward so as to intersect with an oil supply passage that communicates an oil reservoir formed at the bottom of an oil separation chamber with a compression chamber. A high-pressure chamber that communicates with the compression stroke and a low-pressure chamber that communicates with the suction chamber or the suction stroke of the compression chamber are provided facing each other, and the on-off valve is pressed toward the high-pressure chamber when the compressor is stopped, blocking the oil supply passage. The reason is that it is configured so that it is in a state where it can be used.

EXAMPLES Specific examples of the present invention will be described below with reference to illustrative drawings. 1 to 4 are drawings showing a first embodiment, that is, an embodiment for a slide vane type compressor, and (1) shows a housing forming the outer shell of the compressor.

The housing (1) includes a rear housing (IR) formed into a bottomed cylindrical shape with an opening at one end, and a front housing (IR) that covers the opening of the rear housing (IR).
F). (2) is a cylinder block built into the rear housing (R), and the cylinder block (2) is formed into a hollow cylindrical shape with openings at both front and rear ends. (3F) (3R) is a pair of front and rear side plates built into the rear housing (IR) so as to shield both the front and rear openings of the cylinder block (2), (3F) is a front side plate, (3R) ) Shows the side plate. (4) is a drive shaft installed horizontally between (3F) and (3R) with its center line offset to the cylinder block (2), and the rotor is attached to the drive shaft (4). (5) is solidified integrally. The rotor (5) is built into the cylinder block (2) so that a part of its outer peripheral wall can slide against the inner wall surface of the cylinder block (2), and the outer peripheral wall of the rotor (5) and Cylinder block (
A compression chamber (6) is formed between the inner wall surfaces of 2). (7)
. . . are vane grooves carved at four locations on the rotor (5), and each vane groove (7.0.5) is the first groove in the longitudinal direction of the rotor (5), that is, in the axial direction. As shown in Figure 1, it is provided in a ['] shape between the front and rear end surfaces. Each vane h'7 (7)... has a back pressure chamber (7Y) at its base, and the vane ( 8) ... is inserted and inserted freely.

Front housing (IF) and front side play
) (3F) is provided with a suction chamber (9), and the front side play (3F) is provided with a suction chamber (9) corresponding to one end of the compression chamber (6), that is, the starting end along the rotational direction of the rotor (5). Suction hole 00 is opened. On the other hand, a part of the cylinder block (2) is cut out at the other end of the compression chamber (6), that is, at a position corresponding to the terminal end along the rotational direction of the rotor (5), so that it is connected to the inner wall surface of the rear housing (IR). A discharge chamber 0]) is formed therebetween, and the discharge chamber α1) and the terminal end of the compression chamber (6) are communicated through a discharge hole (2). 0■ indicates a discharge valve that covers the discharge hole 02, and '0■' indicates a retainer that regulates the opening angle of the discharge valve 0K.

O → is the oil separation chamber formed between the rear wall of the rear housing (IR) (3R), and the through hole Q that opens to the separation chamber (04) (3R) is A filter (l[9
is provided. In addition, at the lower end of the separation chamber (141) there is formed a reservoir Q of oil that is separated by the filter 〇〇.The inner surface of the rear side play (3R),
That is, an oil supply groove (c) and a pressure groove 01 are carved in the sliding surface of the rotor (5) that comes into sliding contact with the rear end surface of the rotor (5). Oil supply groove (to) and pressure groove 0
The kettle is provided in an arc shape along the rotation locus of the back pressure chamber CRT provided at the base of the vane groove (7) provided on the rotor (5) side, that is, between the vane grooves (7).

The oil supply groove (T) is located at the other end of the compression chamber (6), that is, the rotor (5).
) is provided on the terminal end side along the rotational direction so as to correspond to the discharge hole 02. More specifically, as shown in FIG. 2, when the tip of the vane (8) slides into contact with the starting end of the compression chamber (6) from the top position, a back pressure chamber C is formed at the base of the vane (8).
It is provided so that RT can communicate with the oil supply groove (G). The oil supply groove (to) is provided so as to communicate with the reservoir part α formed at the lower end of the separation chamber 04 via an oil supply passage extending up from the same temperature part Q7. Also, a control valve mechanism eυ is provided in the rear side play (3R) in correspondence with the oil supply passage (1).

The control valve mechanism e◇ is provided with a spool handle that is slidable in a direction intersecting the oil supply passage handle, and a high pressure chamber (c) and a low pressure chamber are located at both ends of the spool (a). (c)
are set up facing each other. The high pressure chamber (6) communicates with the compression chamber (6) at a position closer to the compression stroke via the pressure hole.
Also, the low pressure chamber (F) is connected to the compression chamber (6) via the pressure conducting hole (C)'.
It is provided so as to communicate with the intake stroke at a position near the suction stroke. A spring (C) is interposed in the low pressure chamber (C), and is normally biased toward the high pressure chamber to close the oil supply passageway.

On the other hand, the pressure groove 00 is provided so as to be continuous with the oil supply groove a frame from the starting end side along the rotational direction of the rotor (5), that is, from the top position to a position corresponding to the opening of the suction hole 00. The pressure groove 0I is provided so as to communicate with the compression stroke of the compression chamber (6) via a pressure guiding path (c).

5 to 9 are drawings showing a second embodiment, that is, an embodiment for a scree type compressor, (3], F
) is the front housing, (31R) is the rear housing, and 0 is the cylinder block. A front side plate (33F) is interposed between the cylinder block 0 and the front housing (31F), and 1) A rear side play (33R) is interposed between the rear housing (31R) and the rear housing (31R).

A front bearing chamber (34F) is provided between the front side brake (33F) and the front housing (31F), and a rear bearing chamber (34R) is provided in the rear side brake (33R). Each pair of bearings is in the bearing chamber (a 4F) (34R).
are provided facing each other, and each bearing has a section (35F) (35
R), (35F) and (35R), a pair of rotors are horizontally suspended in parallel. The rotor consists of a male rotor (36A) with a plurality of protruding ridges protruding along the helical direction, and a female rotor (36B) with a plurality of four ridges engraved along the helical direction. (36A) (36
B) is provided so that the protruding stripes and the four stripes can be selectively engaged with each other.

In addition, in the hollow part of cylinder block 0, a compression chamber (b) is formed in the gap formed between the inner wall surface of cylinder block 6 and the two rotors (36A) (36B). A suction chamber (g) is formed by communicating with (b).

And (to)' indicates the inlet.

On the other hand, the rear housing (31R) and the rear side plate (
33R) A discharge chamber is formed between the two. The discharge chamber 09 is provided so as to communicate with the compression chamber (B) through a discharge hole, and a discharge valve (4) is provided at the open end of the discharge hole ring on the discharge chamber side.
1) is provided so as to be able to open toward the discharge chamber (G). (41f indicates a glue retainer for adjusting the opening angle of the discharge valve 03.

The discharge chamber (2) has the above-mentioned discharge valve (4]) and a retainer.
(4) A filter 02 is provided to surround y, and a separated oil reservoir θ is formed at the bottom.The filter 02 is passed from the reservoir ring through the side plate (33R) and the inside of the cylinder block 0. An oil supply passage is extended, and its tip is provided so as to face the compression chamber.The oil supply passage (b) corresponds to the control valve mechanism.
is provided.

In the control valve mechanism (c), a spool θ is provided so as to be movable forward and backward so as to intersect with the oil supply passage (3), and a high pressure chamber θ and a low pressure chamber (2) are provided facing each other at both ends of the spool θΦ. The high pressure chamber 0η is provided so as to communicate with the compression stroke of the compression chamber (B) through the pressure guiding hole θr, and the low pressure chamber (2) is connected to the front bearing chamber (3) through the pressure guiding hole (7)'.
4F) and the suction chamber (c). In addition, approximately θ value is interposed in the low pressure chamber, and the spool is normally biased toward the high pressure chamber 07 to block the oil supply passage. .

From the oil supply passage 0→, there are multiple oil supply passages (5) from a position closer to the compression chamber (B) than the control valve mechanism (C).
0F) (50R) are branched and extended, one oil supply passage (5oF) is provided facing the front bearing chamber (34F), and the other oil supply passage (50F) is provided so as to face the front bearing chamber (34F).
R) is provided facing the rear bearing chamber (34R).

FIGS. 1O and 11 are drawings showing a third embodiment, that is, an embodiment for an IJ-type compressor similar to the above embodiment, in which the control valve mechanism is (c)' is provided. In the open control valve mechanism A, a valve seat (51) formed in a tapered shape in the supply passage θ→
), the valve seat (51) has its throttle direction aligned with the compression chamber (
A ball valve (52) is provided in the direction (a large diameter part is formed on the reservoir side and a small diameter part is formed on the compression chamber (b) side), and a ball valve (52) is installed in the large diameter part. Enclosed freely. Further, a spool (53) is provided in the opening control valve mechanism θ' in correspondence with the valve seat (51) so as to be movable forward and backward. More specifically, a projecting piece (53) is extended from the spool (53), and its tip is provided so as to face the inside of the valve seat (51).The spool (2) has a high pressure chamber 0η and a high pressure chamber 0η at both ends. Low pressure chambers (c) are provided facing each other.More specifically, protrusions (c) are provided.
5: A low pressure chamber is provided on the side where g is extended, and the low pressure chamber θ is connected to the front bearing chamber (34
F) and the suction chamber (to). Further, the high pressure chamber θ is provided so as to communicate with the compression stroke of the compression chamber (b) via the pressure guiding hole θ.

Next, its effect will be explained. In the first embodiment shown in FIGS. 1 to 4, when the compressor is stopped, each part inside the compressor, namely the suction chamber (9), the compression chamber (6)
, the discharge chamber 01), and the separation chamber 0→ are in a state where their respective pressures are balanced. Also, in the control valve mechanism Qυ, the pressures in the high pressure chamber (C) and low pressure chamber (C) are in a balanced state, and the spool gradient is urged toward the high pressure chamber (C) via the spring (C). Oil supply passage (1)
is in a state of occlusion.

Then, when the compressor is stopped as shown in the figure, the rotor (5) and vane (8) are rotated by rotating the drive shaft (4) by connecting an electromagnetic clutch (not shown). The effect of sucking the refrigerant gas in the suction chamber (9) into the compression chamber (6) through the suction hole OQ is obtained through the rotational action of . The refrigerant gas sucked into the compression chamber (6) in this manner is gradually compressed while being sent from the suction side to the discharge side within the compression chamber (6). Then, the refrigerant gas pressure-fed to the discharge hole (a) position is discharged through the discharge hole 02 and the discharge chamber 01.
), and is fed into the heating chamber 04) through the through hole 00.

Oil is separated from the refrigerant gas sent into the separation chamber 04), and the oil is stored in the reservoir 0, while the refrigerant gas flows through the discharge pipe from the discharge port 1 to the condenser (not shown). It is sent out in one direction. Since such a compression effect is obtained, a pressure difference is generated in the compression chamber (6) between the suction stroke and the compression stroke, but a high pressure chamber (HA) is generated in the control valve mechanism Q. ) communicates with the compression stroke of the compression chamber (6) through the pressure guiding hole (c)', and the low pressure chamber (c) communicates with the suction stroke of the compression chamber (6) through the pressure guiding hole (c)'. Due to the communication, the pressure difference that occurs between the suction stroke and the compression stroke in the compression chamber (6) is reduced by the spring (
When the pressure in C) exceeds the setting value, the spool (A) overcomes the biasing pressure of the spring (C) and is pushed toward the low pressure chamber (C), opening the oil supply passageway. . By opening the oil supply passage (a),
The oil stored in the reservoir θ of the separation chamber 04) is pushed up through the oil supply passage (1) through the pressure within the separation chamber 04) and is supplied to the vane groove (7). By supplying oil to the vane groove (7) in this way, back pressure is applied to each vane (8), and each vane (8) is moved into the compression chamber (6). A pushing action is obtained, and a lubrication action and a sealing action are obtained between each vane groove (7) and the vane (8).

On the other hand, when the compressor operation is stopped, the compression chamber (
6) The pressure inside the rotor (5) and vane (8)...
(3F) (3R) (3F) (3R) As a result of leakage to the suction chamber (9) side through the gap formed, each part (suction stroke and compression stroke) in the compression chamber (6) is under suction pressure. The pressure is the same as that of

Since each part in the compression chamber (6) is brought to the same pressure state as the suction pressure in this way, the high pressure chamber (1) and the low pressure chamber (c) in the control valve mechanism 0]) are brought to the same pressure state. That is, the spool (A) is biased toward the high pressure chamber by the spring (C), and a state is obtained in which the oil supply passageway is closed. When the oil supply passage (e) is blocked, the supply of oil to the vane groove (7) is stopped when the compressor is stopped, and the oil supply to the vane groove (7) is stopped. Oversupply of oil can be prevented. That is, it is possible to prevent excess oil from accumulating in the compression chamber (6), thereby preventing the occurrence of liquid compression at the time of restart.

In the second embodiment shown in FIGS. 5 to 9, when the compressor is stopped, the suction chamber (c) and the compression chamber (b)
, the discharge chamber) are in the same pressure state, so that the high pressure chamber o71 and the low pressure chamber (c) in the control valve mechanism (c)' are in the same pressure state. That is, the spool (T) is biased toward the high pressure chamber t4 by the spring θ, and is in a state of closing the oil supply passage.

As mentioned above, when the compressor is stopped, the electromagnetic flannel
male rotor (36A) through the connection operation of
By driving the female rotor (3a B), the refrigerant gas in the suction chamber (9) is sucked into the compression chamber (b) through the meshing rotation of the two-end rotors (36A) and (36B), and the refrigerant gas is compressed. This provides an effect of forcefully feeding the inside of the chamber toward the discharge chamber (G), that is, an effect of compressing the refrigerant gas. The refrigerant gas thus forced into the compression chamber (B) to the terminal position is sent into the discharge chamber (C) through the discharge hole (3). The refrigerant gas sent into the discharge chamber (c) is
The oil is separated in c), and the oil is stored in the pool θ■
While the refrigerant gas is stored in the discharge pipe, the refrigerant gas is sent out toward a condenser (not shown).

In the control valve mechanism θQ', the high pressure chamber θ is the pressure guiding hole 0.
By being in communication with the compression chamber (b) through 7y, the pressure spring G in the vicinity of the discharge hole 00 of the compression chamber (b)
When the set pressure of phase I is exceeded, the spool head overcomes the urging pressure of θ and is pressed toward the low pressure chamber (c), thereby opening the oil supply passage. When the oil supply passage θ→ is opened, the oil stored in the reservoir θ of the discharge chamber (G) is pushed up inside the oil supply passage θ→ by the pressure in the discharge chamber (A) and compressed. Supplied into the chamber (b). and compression chamber (a)
The oil supplied inside the tank is connected to both ports (36A) (36
Between the inner wall surfaces of B) and the compression chamber (B) and between both ports (3a
A) Lubrication and sealing action at the meshing part (36B) can be obtained.

In addition, a part of the oil pushed up inside the oil supply passage ■ branches from the same oil supply passage θ → to the oil supply passage (5
0F) (Front Bear 1
The bearing is fed into the J tank chamber (34F) and the rear bearing chamber (34R) and has the effect of lubricating the bearing parts (35F) (35R).

On the other hand, when the compressor operation is stopped, the compression chamber (
6) By returning the internal pressure to the same pressure state as the suction pressure, the pressures of the high pressure chamber 071 and the low pressure chamber 0→ are balanced in the control valve mechanism 0 clause. In other words, the spool 00 is pressed toward the high pressure chamber 0 by the urging pressure of θ, so that a state is obtained in which the oil supply passage 04 is closed.

In the third embodiment shown in FIGS. 10 and 11, during operation of the compressor, the pressure difference generated between the spool (5 is the high pressure chamber 17) and the low pressure chamber 0 in the control valve mechanism 00' causes the low pressure chamber ( In the state of being pressed in the direction (C), the ball valve (5 →
By pressing in the direction away from 5 strokes, a state is obtained in which the oil supply passage θ→ is communicated. In addition, when the operation is stopped, the pressure in the high pressure chamber θη and the low pressure chamber (c) is balanced at the same pressure as the suction pressure, and the high pressure chamber θη and the low pressure chamber (c) can freely slide in any direction. On the other hand, since the discharge pressure remains in the discharge chamber (to), a pressure difference will occur between the discharge chamber (to) and the high pressure chamber (0 to low pressure chamber). However, due to this pressure difference, the ball valve 0→ is pressed in a direction in which it comes into close contact with the valve seat (5]), and a state is obtained in which the oil supply passage θ→ is closed.

Effect The present invention is constructed as described above, and by supplying the oil separated from the refrigerant gas compressed in the compression chamber to the sliding portion of the compression chamber, In a compressor that is installed to obtain lubrication and sealing effects, a control valve mechanism for opening and closing the oil supply passage connecting the oil reservoir and the compression chamber is installed to open and close the oil supply passage, and when the compressor is operating, the oil supply passage connects the oil reservoir and the compression chamber. Opening the oil supply passage through the differential pressure that occurs between the compression stroke and the suction chamber, or between the suction stroke of the compression chamber (as long as there is a differential pressure within the compressor, it may also be at the beginning and end of the compression stroke). This provides the effect of supplying oil to the compression chamber, and when the compressor is not operating, the oil supply passage is blocked by the biasing pressure of the spring or the pressure and force of the discharge chamber (separation chamber). By providing an effect of blocking the supply of oil to the compression chamber, it has become possible to prevent excessive supply of oil to the compression chamber. In other words, it has become possible to effectively prevent liquid compression that would otherwise occur due to oil being supplied to the compression chamber in the stopped state and the oil remaining in the compression chamber.

Further, in the present invention, the oil supply passage is opened by utilizing the differential pressure generated between the compression stroke of the compression chamber and the suction stroke of the suction chamber or compression chamber during motion, so that the compressor It has become possible to obtain a state in which the oil supply passage is reliably opened in any operating state (for example, a high-speed rotation state, a low-speed rotation state), and to improve its reliability.

Furthermore, in the control valve mechanism, the pressures in the high pressure chamber and the low pressure chamber can be set arbitrarily, increasing the flexibility, and in addition, the control valve mechanism has a simple structure with fewer parts. This has made it possible to easily integrate it into a compressor.

[Brief explanation of the drawing]

1 to 4 are drawings showing the first embodiment, in which FIG. 1 is a cross-sectional view taken along line A-B-C in FIG. 2, and FIG. 2 is a cross-sectional view taken along line D-D in FIG. Figure 3 is a sectional view taken along line E-E in Figure 1, and Figure 4 is a sectional view taken along line E-E in Figure 4, showing the same operating state.
FIG. 5 to 9 are drawings showing the second embodiment, in which FIG. 5 is a sectional view taken along line FE in FIG. 6, FIG. 6 is a sectional view taken along line GG in FIG. FIG. 7 is a sectional view taken along the line H--H in FIG. 5, and FIGS. 8 and 9 are enlarged sectional views showing the operating state of the control valve mechanism. 10 and 1] are drawings showing the third embodiment, and are enlarged sectional views showing the operating state of the control valve mechanism portion. Further, FIG. 12 is a graph showing pressure changes in the conventional structure. (]) Housing, 0 → Front housing 1. (LF
t) Rear housing, (2) cylinder block, (
3F) Front side plate, OR) Rear side plate, (4) Drive shaft, (5) Rotor, (6) Compression chamber,
(7) Vane groove, (7)' back pressure chamber, (8) vane, (9
) Suction chamber, θ0 suction hole, (ITJ discharge chamber, 0 function discharge hole,
o3 discharge valve, Q:1' IJ retainer, 04) separation chamber,
00 hole, OG filter, θ reservoir, α Enoki oil supply groove,
00 pressure groove, (a) oil supply passage, oI) control valve mechanism, (a) spool, (c) high pressure chamber, (b)' pressure guide hole, (
C) Low pressure chamber, (Foundation)' Pressure guiding hole, (C) Spring, (E) Pressure guiding path, O1 → Front housing, (3), 9 Rear housing, I3 Cylinder block, 63 → Front side plate, 03 →Rear side plate, 6419 front bearing chamber, ◎40 rear bearing chamber, o5→■
5 → bearing N, 65 → male rotor, 06 → female rotor, (b) II M chamber, (c) suction chamber, (to)' suction port, zero discharge chamber, CII' discharge port, (c) discharge hole , @
discharge valve, (4-1f retainer-1 (6) filter,
03 Reservoir part, ■Oil supply passage, 2) Control valve mechanism, θΦ spool, hi high pressure chamber, 07) 2 Pressure guiding hole, 2) Low pressure chamber, 2) Pressure guiding hole, θ spring, ( 50 → (50 → oil supply passage, Φη valve seat, (5 → ball valve, (5 east spool, (5 → 'projection piece.

Claims (1)

[Claims] (1) In a compressor in which an oil separation chamber is formed on the discharge side of the compression chamber, and an oil reservoir formed at the bottom of the oil separation chamber is communicated with the compression chamber by an oil supply passage, the oil supply passage intersects with the oil supply passage. An on-off valve is provided so as to be able to move forward and backward, and at both ends of the on-off valve, a high pressure chamber communicating with the compression stroke of the compression chamber and a low pressure chamber communicating with the suction chamber or the suction stroke of the compression chamber are provided facing each other. The valve is a mechanism for preventing oversupply of lubricating oil in a compressor, which is provided so that when the compressor is stopped, it is pressed toward the high pressure chamber and closes the oil supply passage.