JPS59208196A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To prevent occurrance of the phenomenon that scrolls are disengaged from each other due to retard of lubrication by restricting the quantity of sucked air when a compressor starts or the pressure on the discharging side is over a rated value and releasing the restriction thereof when the pressure on the discharging side is below the rated value. CONSTITUTION:Before a compressor starts, a capacity regulation valve 41 is placed under such condition that a suction valve 53 is closed by the force of a spring 54 and a check valve 65 is also closed by the force of a weak spring 66. When a motor is started in said condition, a compression chamber 7 produces a vacuum therein by revolution of a turning scroll 4. Resultantly, while the pressure in the compression chamber 7 is reduced to a negative pressure, the pressure in a crankcase 11 remains at the atmospheric pressure. Therefore, the inner pressure of the crankcase 11 acts on the back face of the turning scroll 4 as a back pressure to press it, whereby preventing the turning scroll 4 from disengagement from a fixed scroll 6.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a scroll compressor suitable for use, for example, in compressing air or a refrigerant (hereinafter referred to as air).

In general, there are two types of scroll compressors known: oil-free compressors and oil-filled or oil-cooled compressors. While supplying oil, cooling, lubricating, and sealing each part,
The air sucked in from the suction port is compressed in the compression chamber, and this compressed air is discharged together with oil into the oil separation tank. The clean air from which oil has been removed in the nuclear oil separation tank is supplied to the air tank and pneumatic equipment. I'm trying to do it.

For this reason, the scroll compressor of the prior art has a casing with a bearing on the negative side and a cylindrical portion on the reservoir end, and a casing that is rotatably supported by the bearing of the casing and whose tip portion is located within the cylindrical portion. A rotating shaft that serves as a crank, an orbiting scroll that is rotatably supported by the crank of the rotating shaft, and a compression chamber that is fixed to the cylindrical side of the casing and rotates while overlapping the orbiting scroll. a fixed scroll forming a compressor, a discharge port provided at a central position of the fixed scroll for discharging air compressed in the compression chamber, and a discharge port discharging the compressed air and oil from the discharge port. An oil separation tank is connected to the discharge port to remove oil from the mixture.

To compress the air, the air sucked in from the suction port is sealed inside the airtight space 9 formed between the orbiting scroll and the fixed scroll as a pressure first δ chamber. The compression chamber is reduced to compress the air, and this compressed air is discharged from the discharge port into the oil tank, while the oil in the nuclear oil separation tank is fixed to the drive shaft, the bearing part of the orbiting scroll, and the orbiting scroll. By supplying the liquid to the end plate sliding surface of the scroll and the compression chambers formed by the scrolls, these parts are cooled, lubricated, and sealed.

By the way, in the prior art described above, when supplying oil in the oil separation tank to each of the aforementioned parts,
Sufficient oil supply can be performed after the pressure inside the oil separation tank has increased. However, since the pressure within the oil separation tank has not increased when the compressor is started, a refueling delay occurs. As a result, especially if there is a delay in refueling the sliding surface of the end plate between the fixed scroll and the orbiting scroll, the sealing performance of the curve between the fixed scroll and the orbiting scroll will be impaired and a separation phenomenon will occur. There is a problem in that each compression space is in communication and the pressure can rise at any time.

Therefore, in order to solve the above problem, the prior art provides a separate oil pump and a motor for driving the ponder, and drives the oil pump in line at the same time as or before starting the compressor to drive the fixed scroll. Oil was supplied to the sliding surface of the end plate of the orbiting scroll to prevent the above-mentioned release phenomenon from occurring.

However, the conventional technology does not require a separate oil pump or motor, and has the disadvantage of having a complicated piping system and high cost.

Another method is to make the oil piping for supplying oil to the sliding surface of the head plate large in diameter, and configure it so that oil can be supplied quickly even if there is a slight pressure increase in the oil separation tank. can also be considered.

However, with this method, a large amount of oil is not supplied during rated operation, and when the axial clearance between the fixed scroll and the orbiting scroll is large, the orbiting scroll may become unstable due to hydraulic pressure. 91 to make a turn
New problems arise, such as abnormal wear on the 297th part and early damage to the bearing.

The present invention was developed in view of the drawbacks and problems of the prior art described above, and prevents the occurrence of separation between the scrolls due to a delay in lubricating the sliding surface of the head plate at the time of startup, thereby ensuring compression operation at the time of startup. The object of the present invention is to provide a scroll compressor that can be used for various purposes.

% of the configuration adopted by the present invention in order to achieve the above object
The characteristic is that the suction port restricts the intake air amount at startup, and after startup, when the pressure in the discharge port side space reaches a predetermined pressure that is lower than the rated pressure, the restriction on the intake air amount from the suction port is released. In addition, when the pressure in the space on the discharge port side reaches the rated pressure, a capacity regulating valve is provided which again limits the amount of air taken in from the suction port.

With this configuration, the amount of intake air is limited when p1 is started, so the pressure in the crank chamber is higher than the pressure in the compression chamber, and the pressing force acting on the orbiting scroll prevents the phenomenon of the orbiting scroll coming loose. I can do it. Further, during steady compression operation after startup, the restriction on intake H can be canceled to prevent intake resistance. Furthermore, to the rated pressure? By restricting the amount of intake air when this happens, it is possible to prevent oil from blowing out from the intake port, and in the case of a continuous operation system, it is possible to prevent overloading. Taking as an example a case where a compressor of a type in which a main body and an oil separation tank are assembled integrally is used, FIG. 1, which will be explained together with the embodiment shown in the drawings, shows a first actual example of the present invention. That is, in the figure, 1 is a casing, and the casing 1 is formed from a bearing part IA and a large diameter cylindrical part IB. Reference numeral 2 denotes a drive S shaft rotatably supported by the bearing part IA via bearings 3A and 3B, one end of the drive shaft 2 protrudes outside the casing l and is connected to a motor (not shown), and the other end is connected to a motor (not shown). protrudes into the cylindrical portion IB to form a crank 2A. The axis o2 of the crank 2A is eccentric with respect to the axis O1 of the drive shaft 2 by a distance δ.

Reference numeral 4 denotes an orbiting scroll rotatably supported by the crank 2A of the drive jliθ information 12 via a bearing 5, and the orbiting scroll 4 is provided on the same line as the 1111 line o2 of the crank 2A. On the lower surface side of the end plate portion 4 of the stock scroll 4, there is formed a wrap portion 4B having an involute or a curved shape in which the in is close to a lute.
Reference numeral 6 denotes a fixed scroll solidly mounted on the opening side of the cylindrical portion IB of the casing 1, and the fixed scroll 6 is connected to the drive shaft 2.
It is set so that it is on the same @ line as the axis o1 of .

A wrap portion 6B having a curve close to a lute or involute is formed on the end surface side of the end plate portion 6 of the fixed scroll 6, and the wrap portion 6B forms a predetermined angle with the wrap portion 4B of the orbiting scroll 4. The wrap portions 4B and 6B are arranged so as to fit flush against each other, and the wrap portions 4B and 6B are in sliding contact with each other to form a plurality of compression chambers 7 which are airtight spaces.

Reference numeral 8 denotes a suction port formed on the side surface of the fixed scroll 6. One side of the suction port 8 is connected to a capacity adjustment valve, which will be described later, via an intake pipe 9, and the other side of the suction port 8 is It opens into the compression chamber 7 located on the outermost side, and is designed to suck in external air while the orbiting scroll 4 rotates. on the other hand,
1O is a discharge port provided at approximately the center of the fixed scroll 6. From the discharge port 10, air that is continuously compressed in the compression chamber 7 while the orbiting scroll 4 rotates is sent into an oil separation tank to be described later. It is designed to be discharged together with oil.

II is a crank chamber consisting of a sealed space formed between the casing 1 and the back of the orbiting scroll 7. One or two back pressure introduction holes 12 are formed in the end plate 7A of No. 7. In addition, since a pressure higher than the pressure at the suction port 3 and lower than the discharge pressure at the discharge port 4 is introduced into the crank chamber 11, the back pressure introduction hole 12 is connected to the suction port 3.
The crank chamber 11 opens into a compression chamber 9 located at an intermediate location between the and the discharge port 4, and during compression operation, the pressure inside the crank chamber 11 becomes equal to the pressure in the compression chamber 9 located at the intermediate location, thereby applying a pressing force to the orbiting scroll 7. It's brown.

Reference numeral 13 denotes an Oldham joint as a self-slip prevention mechanism provided in the crank chamber 11. When the Oldham joint 13 rotates the drive shaft 5 and rotates the orbiting scroll 7, the orbiting scroll 7 is moved along the axis 01 of the drive 4115. 14 is an oil hW tank consisting of a cylindrical body with a bottom, and the opening side of the oil separation tank 14 is connected to the bottom of the end plate 6A of the fixed scroll 6. is fixed to. And oil separation tank 14
is divided into an oil separation chamber 14A and an oil reservoir chamber 14B by a seal plate 15 provided at an intermediate position, and the oil separation chamber 14A and oil reservoir chamber 14B are separated by a plurality of ventilation holes formed in the seal plate 15. It is connected by 16. Further, a cylindrical oil separation element 17 is provided in the oil separation chamber 14A, and the oil separation element 17 separates oil in the compressed air supplied into the cylinder through the vent hole 16. In addition, a predetermined amount of oil 18 is stored in the oil reservoir chamber 14B.

19 is a discharge pipe which leads the regular air discharged from the discharge port 11 together with oil to the oil reservoir chamber 14B. The other end of the shell passage 1 is connected to the oil reservoir chamber 1 through the seal plate 15.
It opens at the upper position of 4B. In the figure, 20 is oil sump chamber 1
4B is a buckle plate disposed on the upper part of the seal plate 15 in the vicinity of the seal plate 15 and in parallel with the seal plate 15, so that the oil scattered from the oil surface by the baffle plate 20 directly flows into the oil separation element 17 from the vent hole 16. is prevented. 21 is oil content j11
A drain outlet opening in the bottom of the tank 14. A drain cock 22 is provided in the outlet 21, and by manually opening the drain cock 22, drain and waste oil can be discharged.
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On the other hand, 23 is an air outlet opened on the side wall of the oil n1 [chamber 14A] of the oil separation tank 14, and the outlet 23 is connected to one end of the discharge pipe 24 or connected to the outlet, and the other end is connected to a gust tank or an air tool (Fig. (not shown) is connected at nine. The discharge pipe 24
A pressure switch 25 is provided in the middle, branching off from this, and the pressure switch 25 is configured to close when the pressure collar in the discharge piping 24, that is, the pressure in the oil HTB tank 14 reaches a predetermined rated pressure. has been done. Further, 26 is a pilot pipe whose one end is branched from the discharge pipe 24, and the other end of the pilot pipe 26 is connected to a capacity adjustment valve, which will be described later, and the valve is opened when the pressure switch 25 is closed. A solenoid valve 27 is provided. In the figure, 28 is a manual valve provided in the discharge pipe 24.

Further, reference numeral 29 denotes an oil outlet which is opened on the side wall of the oil reservoir chamber 14B of the oil separation tank 14 and located below the oil level of the oil 18. is connected. The other end of the oil pipe 30 is connected to an oil filler port 33 and an annular groove 34 formed in the cylindrical portion IB of the casing 1.
, the sliding surfaces of the orbiting scroll 4 and the fixed scroll 6 are supplied with oil via the oil passage 35 of the fixed scroll 6, and the oil piping 3
The other end of the oil pipe 32 is connected to a capacity adjustment valve to be described later to supply pyropressure pressure, and the other end of the oil pipe 32 is connected to a fixed scroll 6.
The compression chamber 7 is connected to the compression chamber 7 through an oil supply port 36 and an oil passage 37 formed in the
Refuel inside. On the other hand, 38 is an oil outlet opening in the side wall of the oil separation chamber 14A of the oil separation tank 14 in the vicinity of the seal plate 15; 39 is an oil pipe whose one end is connected to the oil outlet 38; The other end is adapted to supply oil to the bearings 3A, 3B, 5, etc. through an oil supply port 40 formed in the bearing portion IA of the casing 1.

Next, reference numeral 41 denotes a closed valve type capacity adjustment valve used in this embodiment, and the capacity adjustment valve 41 includes a bottomed cylindrical upper cover 42 and a plate-shaped valve seat member 43 whose upper and lower surfaces serve as valve seats. and a lower cover 44 having a cylindrical shape with a bottom and a protrusion 44A formed at the lower part, and the upper cover 42, valve seat member 43, and lower cover 44 are integrally fixed by bolts 45. , and an end cover 46 is provided on the lower surface side of the protrusion 44A.
is fixedly installed.

Here, an inflow chamber 47 is formed by the upper cover 42 and the valve seat member 43, and the lower cover 44 and the valve seat member 4
3 forms an outflow chamber 48, and the inflow chamber 47 and outflow chamber 48 communicate with each other via a valve passage 49 formed in the valve seat member 43. An inlet 50 is formed in the upper cover 42, and the inlet 50 is inserted into the atmosphere through a filter 51, while an outlet 52 is formed in the lower cover 44, and the outlet 52 is as described above. It is connected to the other end of the intake pipe 9. Therefore, the air sucked in from the filter 51 flows through the inlet 50. Inflow chamber 47, valve passage 49, outflow chamber 48,
Air can be supplied from the intake pipe 9 to the suction port 8 via the outlet 52 in sequence.

Reference numeral 53 denotes an intake valve disposed inside the inflow chamber 47.The intake valve 53 is in contact with the valve seat member 43 by a spring 54 stretched between it and the upper cover 42, so as to always close the valve passage 49. energized.

55 is a large diameter cylinder formed in the protrusion 44A of the lower cover 44, and 56 is a small diameter cylinder formed in the end cover 46. The cylinders 55 and 56 are formed coaxially with each other and communicate with each other. 57 is a piston consisting of a large diameter portion 57A located in the large diameter cylinder 55 and a small diameter portion 57B located in the small diameter cylinder 56, and the piston 57 is integrated with the above-mentioned intake valve 53 via the valve shaft 58. are connected to each other. Therefore, in the non-operating state, the piston 57 is brought into the illustrated state by the spring force of the spring 54, and the large diameter portion 57A
is located at an intermediate position of the large-diameter cylinder 55 and forms a pressure chamber 59, and the small-diameter portion 57B is also located at an intermediate position of the small-diameter cylinder 56 and forms a pressure chamber 60. Reference numeral 61 denotes a pilot pressure introduction port formed in the lower cover 44. The pilot pressure introduction port 61 is connected to the other end of the aforementioned pilot pipe 26, and when the solenoid valve 27 is opened, compressed air from the pilot pipe 26 is supplied. The air can be introduced into the pressure chamber 59 through an air passage 62 formed in the lower cover. On the other hand, 63 is an oil introduction port formed in the lower cover 46, and the kernel oil introduction port 63 is connected to the other end of the aforementioned oil pipe 31 so that it can be introduced into the n1 oil separation chamber 60. Reference numeral 64 denotes a communication hole that communicates the pressure chamber 59 and the outflow chamber 48. The communication hole 64 is formed to have a smaller diameter than the air passage 62, and is used to release residual pressure in the pressure chamber 59 when the intake valve 53 is opened. It is a hole. In the figure, reference numeral 65 denotes a check valve for preventing oil from blowing out disposed in the outflow chamber 48. The check valve 65 is slidably inserted into the valve shaft 58, and the check valve 65 and the lower cover 4
4, the weak spring 66 is always biased in the valve closing direction, thereby closing the valve passage 49.

Furthermore, 67 is an auxiliary tank provided in a branch pipe 68 branched from the intake pipe 9, and the auxiliary tank 67 uses the air in the nuclear auxiliary tank 67 for compression at the time of startup to increase the amount of intake air at the time of startup. It has a function to compensate for the deficiency. The auxiliary tank 67 also serves as a resonance type muffler, and exhibits a muffling effect due to resonance during steady compression operation.

The present embodiment is constructed as described above, and its operation will now be described.

First, before starting, the intake valve 53 of the capacity adjusting valve 41 is closed by the spring force of the spring 54, and the check valve 65 is also closed by the spring force of the weak spring 66.

When the motor is started in this state, its rotation will be caused by the drive shaft 2.
, is transmitted to the orbiting scroll 4 via the bearing 5, and the orbiting scroll 4 performs a circular motion relative to the fixed scroll 6 while being guided by the Oldham joint 13. As a result, while the volume of the compression chamber 7 gradually decreases, the compressed air pressurized within the compression chamber 7 is discharged from the discharge port 10 through the discharge pipe 19 into the oil reservoir chamber 14B of the oil separation tank 14. be done.

However, since the intake valve 53 of the capacity adjustment valve 41 is closed, the air in the intake pipe 9, the outflow chamber 48, etc. cannot be used as compressed air by suctioning the air, and the orbiting scroll 4 The inside of the compression chamber 7 becomes in a vacuum state as the engine rotates.

As a result, the pressure inside the compression chamber 7 becomes negative, whereas the inside of the crank chamber 11 is maintained at atmospheric pressure (actually, the compartments communicate through the back pressure introduction hole 13). , the inside of the crank chamber 11 also becomes slightly negative pressure), the crank chamber 11
The internal pressure acts as back pressure on the back side of the orbiting scroll 4 and presses the orbiting scroll 4, thereby preventing the occurrence of a separation phenomenon in which the orbiting scroll 4 separates from the fixed scroll 6, and causing a pressure increase at the time of startup. It is possible to prevent the occurrence of a situation in which the information is lost.

On the other hand, after 1 start, the pressure inside the oil separation tank 14 increases slightly. 18 supplies oil to the sliding surfaces of the orbiting scroll 4 and the fixed scroll 6 through an oil outlet 29, an oil pipe 30, an oil supply port 33, and an annular groove 34, and performs lubrication and sealing between them. In addition, the oil from the outlet 29 is transferred to the oil pipe 32 and the oil filler port 3.
6. The oil is supplied into the compression chamber 7 through the oil passage 37, and performs lubrication and sealing between the lug portions 4B and 6B. In this way, it is possible to prevent the occurrence of a separation phenomenon due to a delay in refueling, and also to prevent the occurrence of abnormal noise even if there is an axial clearance between the lug portions 4B and 6B.

In addition, by providing an auxiliary tank 67 in the middle of the intake pipe 9, the oil separation tank 1 can compensate for the lack of space at the time of startup.
It is possible to hasten the rise in pressure within 4.

Next, as described above, when the pressure inside the oil separation tank 14 rises slightly, the oil 18 inside the oil separation tank 14 flows through the outlet 29 and the oil pipe 31 into the oil inlet 63 and into the pressure chamber 6o of the capacity adjustment valve 41. be guided within.

As a result, the oil in the pressure chamber 6o is transferred to the small diameter portion 5 of the piston 57.
7B, the piston 57 is lifted upward in the figure along with the valve shaft 58 and the intake valve 53 against the spring force of the spring 54, and the intake valve 53 is moved from the valve seat part 43 to the cabin, and the steady state is maintained. Shift to compression operation.

At this time, the air in the pressure chamber 59 flows through the communication hole 64 into the outflow chamber 4.
8, the piston 57 can be quickly displaced.

When the intake valve 53 opens as described above, the rotation y,
The air sucked through the filter 51 along with the &1L5NC of the filter 4 flows through the inlet 50, the inlet chamber 47, and the valve passage 49.
The air is sucked into the compression chamber 7 from the suction port 8 through the outflow chamber 48, the outflow port 52, and the intake pipe 9, and is gradually pressurized in the compression chamber 7. After being raised to a predetermined pressure, it is discharged. The oil is discharged from the outlet 10 through the discharge pipe 19 into the oil reservoir chamber 14B of the oil separation tank 14.

Further, the compressed air in the oil reservoir chamber 14B is guided into the cylinder of the oil separation element 17 through the vent hole 16, and while passing through the element 17, the oil that has become a mist is removed.
The air that has become essential oil is supplied from the air outlet 23 to an air tank or the like via a discharge pipe 24. Note that during the above-mentioned steady compression operation, the check valve 65 is displaced downward in the figure against the weak spring 66 due to the differential pressure between the inflow chamber 47 and the outflow chamber 48), which becomes a hindrance to intake. Never.

On the other hand, during steady compression operation, the inside of the oil separation tongue 14 has the same pressure as the discharge pressure, so the oil inside this is released from the oil outlet 29.
The oil is supplied to the sliding surfaces of the orbiting scroll 4 and the fixed scroll 6 through the oil piping 30, the oil supply port 33, the oil passage 34, and the oil passage 35, and performs lubrication and sealing between the orbiting scroll 4 and the fixed scroll 6. Further, the oil from the oil outlet 29 is transferred to the oil pipe 32 and the oil filler port 36.
, is supplied into the compression chamber 7 via the oil passage 37 to perform lubrication, sealing, and cooling between the n1 lug portions 4B and 6B. on the other hand,
The oil separated by the oil separation element 17 is transferred from the oil outlet 38 to the bearing 3A via the oil pipe 39 and the oil filler port 4o.
3B, 5, Oldham joint 13, etc., are refueled. and,
The oil supplied to these parts is discharged from the discharge port 1 together with the compressed air.
0 is discharged toward the oil separation tank 14, and smooth compression operation is performed.

Furthermore, when the inside of the discharge pipe 24 reaches a predetermined rated pressure,
The pressure switch 25 closes, the solenoid valve 27 opens, and the motor stops driving. As a result, the discharge pipe 24
The compressed air inside is sent from the pilot pipe 26 to the pressure chamber 59 of the pressure adjustment valve 41 via the pilot inlet 61. As a result, compressed air acts on the piston 57, displacing the core piston 57 downward in the figure together with the valve 411158 and the intake valve 53 against the pressure spring 54 in the pressure chamber 60.
The intake valve 53 is seated on the valve seat member 43. As a result, the supply of air from the capacity adjustment valve 41 to the suction port 8 is stopped, and at the same time, the compression operation is stopped by stopping the motor. At this time, if the closing operation of the intake valve 53 is delayed, the oil in the compression chamber 7 may flow back into the outflow chamber 48 . Therefore, the check valve 65 is provided, and when the intake valve 53 starts its closing operation, the check valve 65 is immediately closed by the weak spring 66, thereby preventing the oil from spouting out from the inlet port 50. Note that this check valve 65 is provided as needed and is not necessarily required.

Thus, while the capacity adjustment valve 41 is closed, the compressor is in a stopped state. When the pressure inside the air tank decreases as the amount of air used increases and the pressure inside the discharge pipe 25 reaches the lower limit pressure, a pressure switch (not shown) closes and the % magnetic valve 2
7 Fully open the valve and restart the motor. As a result, the supply of compressed air into the pressure car chamber 59 is stopped, and the system is not limited to the so-called automatic restart system, in which the motor is stopped when the air pressure is reached and the motor is driven again when restarted, in the same way as described above. , it is also possible to adopt a non-negative direction operation system in which the motor is operated continuously. That is, by using a pressure switch that closes the pressure switch 25 at the upper limit pressure, which is the rated pressure, and opens it at a predetermined lower limit pressure, the solenoid valve 27 opens at the rated pressure, and during this time, the motor continues to drive completely. It is also possible to close the system by setting the system to a no-load operating state, and then closing the electromagnetic valve 27 when the lower limit pressure is reached to return to a loaded operating state.

Next, FIG. 2 shows a second embodiment of the present invention, in which the same components as those of the first embodiment described above are given the same reference numerals, and the explanation thereof will be omitted.

However, 70 in the figure is the suction throttle valve type sludge MA used in this embodiment! With I valve adjustment, the capacity W,! The valve regulator 70 comprises a spade-shaped cylinder portion U'71 having a protruding portion 71A, a valve seat member 72, and a lower cylinder member 73 having a protruding portion 73A. It has been cured completely.

Here, an inflow lower 4 is formed in the upper cylinder member 71, an inflow chamber 75 is formed inside, and a protruding portion 71A.
A small-diameter cylinder 76 is formed in the inflow chamber 7 , and the inflow lower 4 communicates with the atmosphere through the filter 51 .
A bulge 77 is formed on the opening side of 5. On the other hand, hυ
A valve passage 78 is formed in the valve seat member 72, and a lower valve seat 79 and a lower valve seat 80 are also formed. 8
1 is formed, and a valve chamber 82 is formed between it and the upper cylinder member 71. Further, an outflow chamber 83 communicating with the valve chamber 82 is formed in the lower cylinder member.
3 is connected to the other end of the aforementioned intake pipe 9 via an outlet 84, and a large diameter cylinder 85 is formed in the protrusion 73A.

Therefore, the air sucked from the filter 51 flows through the inflow lower 4,
Air can be supplied from the intake pipe 9 to the intake port 8 via the inlet chamber 75, valve chamber 82, valve passage 78, outlet chamber 83, and outlet 84 in this order.

86 is an intake valve disposed within the valve chamber 82;
is a valve portion 86A that approaches and separates from the valve seat 77 and the lower valve seat 79, respectively.
, a protrusion 86B that protrudes into the inflow chamber 75 and is pushed by a small-diameter piston that will be described later, and a protrusion 86C that protrudes into the valve passage 78 and is pushed and pushed by a large-diameter piston that will be described later. 86 is bored with a small passage 87 in the orifice 3 that constantly communicates between the inflow chamber 75 and the outflow chamber 84.

A small diameter piston 88 is slidably inserted into the small diameter cylinder 76, and a pressure chamber 89 is formed between the small diameter piston 88 and the small diameter cylinder 76, and the pressure chamber 89 is formed in the protrusion 71A. It communicates with the oil inlet 90. The oil inlet 90 is connected to the other end of the oil pipe 31, and by introducing oil in the oil separation tank 14 through the core oil pipe 31, the small diameter piston 88 is displaced downward in the figure, and the protrusion 86B It has the ability to open the intake valve 86 by moving PP.

Further, reference numeral 91 denotes a check valve for preventing oil from blowing out, which also serves as a stop valve and is disposed in the outflow chamber 83 and is seated on and off the lower valve seat 80.
2 shows a large-diameter piston that is slidably inserted into the large-diameter cylinder 85, and the check valve 91 and the large-diameter piston 92 are connected to the desilt 2A protruding from the large-diameter piston 92 by a nut 9.
It is solid-rotted integrally through 3. And check valve 9
A spring 94 is tensioned between 1 and the intake valve 86, and normally urges the intake valve 86 to sit on the valve seat 77, while also forcing the check valve 91 to leave the lower valve seat 80. . Further, a pressure chamber 95 is formed between the large-diameter piston 92 and the large-diameter cylinder 85, and the pressure chamber 95 communicates with a pilot pressure introduction port 96 formed in the protrusion 73A. The pilot pipe is connected to the other end of the pilot pipe 26, and when the solenoid valve 27 is opened, compressed air from the pilot pipe 26 can be introduced into the pressure chamber 95. Reference numeral 97 is a communication hole that communicates the pressure chamber 95 and the outflow chamber 83, and the communication hole 97 serves as a residual pressure release hole for releasing the residual pressure in the pressure chamber 95 when the check valve 91 is opened. In the figure, reference numeral 98 indicates a spring that is stretched between the check valve 9 and the lower cylinder member 73. Here, the intake valve 86 and the check valve 91 are configured to have almost the same stroke, and in the illustrated state, the lower end of the protruding portion 86C of the intake valve 86 and the billet 92
The distance between the tip of A and the stroke is the same length as the stroke or longer than the stroke, and when the intake valve 86 is seated on the lower valve seat 79, the protrusion 86C is closed.
92A, and in this state, when the check valve 91 is seated on the lower valve seat 80, the port 92A pushes the protrusion 86C to seat the intake valve 86 on the valve seat 77. , or configured to be close to the valve seat 77. Note that in this embodiment, the auxiliary tank 67 shown in the first embodiment is not provided.

Although #ir/', # is constructed as described above, its operation will be described next.

First, before starting, the intake valve 86 of the intake valve 86 is seated on the valve seat 77 due to the spring force of the spring 94 and is closed, and the check valve 91 is also closed due to the spring force of the spring 94.
Seated from 0.

In this state, when the motor is started, the compressed air pressurized in the compression chamber 7 is transferred to the oil sheath tank 1, as in the first embodiment.
4 is discharged into the oil reservoir chamber 141).

However, in the 'n regulator valve 70, the intake valve 86 is closed 1, and the inflow chamber 75 and the outflow chamber 83 are connected to each other by 5!1 through only the small-diameter crest passage 87, but only 2. Therefore, the air in the intake pipe 9, the outflow chamber 48, etc., and the small amount of air flowing in from the throttle passage 87 are used as compressed air by suction. Accordingly, the inside of the compression chamber 7 becomes a vacuum state.

As a result, as in the first embodiment, the pressure inside the compression chamber 7 becomes negative, whereas the inside of the crank chamber 11 is maintained at atmospheric pressure, so that the pressure inside the crank chamber 11 acts as a back pressure. Acting on the back side of the orbiting scroll 4, the orbiting scroll 4
Press the orbiting scroll 4 against the fixed scroll 6.
It is possible to prevent the occurrence of the free 1lilf phenomenon in which the fuel is released, and to prevent the occurrence of a situation in which the pressure does not increase at the time of startup.

On the other hand, since the internal pressure of the oil separation tank 14 increases slightly after startup, the pressure difference between the internal pressure of the oil separation tank 14 and the pressure in the compression chamber 7 causes the oil 18I in the oil separation tank 14 to rise.
i. The oil is supplied to the sliding surfaces of the Mu rotating scroll 4 and the fixed scroll 6 and into the compression chamber 7 through the oil pipes 30 and 32, respectively, and provides lubrication between the sliding surfaces and between the lap portions 4B and 6B. Perform a seal. In this way, it is possible to prevent the occurrence of a separation phenomenon due to a delay in refueling, and also to prevent the occurrence of abnormal noise even when there is a gap in one direction between the lap parts 4B and 6B.

Next, as described above, when the pressure inside the oil separation tank 14 increases slightly, the oil 18 inside the oil II tank 14 flows through the outlet 29.
From the oil inlet 90 via the oil pipe 31 to the capacity-based regulating valve 7
0 into the pressure chamber 89.

As a result, the oil in the pressure chamber 89 causes the small diameter piston 88 and the intake valve 86 to separate from the valve seat 77, and the operation shifts to steady compression operation.

When the intake valve 86 opens as described above, the air sucked in from the filter 51 as the orbiting scroll 4 rotates through the inflow lower 4, the inflow chamber 75, the communication port 81, and the valve actuator 1i.
i 78, the air is sucked into the compression chamber 7 from the suction port 8 via the outflow chamber 83, the outflow port 84, and the intake pipe 9, and is gradually pressurized in the compression chamber 7 to a predetermined pressure n1. Discharge port i
o to the oil sump chamber 1 of the oil separation tank 14 via the discharge pipe 19
Discharge 7'L into 4B. Further, the compressed air in the oil reservoir chamber 14B is guided into the cylinder of the oil separation element 17 through the vent hole 16, and while passing through the element 17, the oil in the form of mist is removed and the air becomes clean. Air is supplied to an air tank or the like from the air rush outlet 23 via the discharge pipe 24.

Furthermore, when the inside of the discharge pipe 24 reaches a predetermined rated pressure,
The pressure switch 25 closes, the solenoid valve 27 opens, and the motor stops driving. As a result, the discharge pipe 24
The pressure M air inside is led from the pilot pipe 26 to the pressure chamber 95 via the pilot pressure introduction port 96. As a result,
Compressed air acts on the large-diameter piston 92, displacing the large-diameter piston 92 upward in the figure against the internal pressure spring 94 of the pressure chamber 89, and causing the check valve 91 to sit on the lower valve seat 80. .

At the same time, the tip of the bolt 92A of the large-diameter piston 92 pushes the protrusion 86C of the intake valve 86 upward in the figure, causing the intake valve 86 to sit on the valve seat 77Vc.

This L stops the supply of air from the capacity 14 & valve 7o to the suction port 8, and at the same time stops the compression operation by stopping the motor. At this time, if the closing operation of the intake valve 86 is delayed, the oil in the compression chamber 7 will flow backward into the b1 discharge chamber 75. Look at this 1ζ check valve 91,
At the start of the closing operation of the intake valve 86, the reverse valve 91 is immediately closed by the weak 1 spring 98, thereby preventing oil from flowing out from the b1-filled lower 4. Note that this check valve 91 may be provided as necessary, but is not necessarily required.

Therefore, when the check valve 91 is not provided, when the rated pressure is applied, the large-diameter piston 92 and the intake valve 86 are displaced upward, and the intake valve 86 is pushed and seated against the valve seat 77, thereby controlling the intake air. It may be stopped or terminated.

In this way, the compressor is in an unoperated state while each lT1 regulating valve 70 is closed. When the pressure inside the air tank decreases as the amount of air used increases and the pressure inside the discharge pipe 25 approaches the lower limit pressure, a pressure switch that does not display automatically opens the solenoid valve 27 and starts the motor. do. As a result, the supply of compressed air into the pressure chamber 95 is stopped, and the compressed air in the output chamber 95 is supplied to the outflow chamber 8 from the continuous JIh hole 97.
3, the check valve 91 and the large diameter piston 92 are connected to the spring 9.
The spring force of 4 returns it to the state shown in the figure, and it can be restarted in the same manner as described above.

In each of the above-described embodiments, the oil separation tank 14 was described as being attached integrally to the fixed scroll 6, but the oil separation tank 14 and the tank 14 may be constructed separately and communicated with each other through a discharge pipe. Also, when the internal pressure of the oil separation tank 14 increases slightly during startup, the oil in the kernel oil separation tank 14 is transferred to each oil inlet 63.
90, compressed air in the oil separation tank 14 may be introduced instead of introducing oil. Conversely, when the rated pressure is reached, i + Ilot piping 26
Discharge pipe 24 to pilot pressure inlet 61.96 via
Although it has been described that compressed air is introduced midway, the compressed air or oil 18 in the oil separation tank 14 may also be introduced as pyropressure, in short, the compressed air or oil pressure in the discharge side space is used as a pilot pressure. Any pressure that closes the intake valves 53 and 86 may be used. Furthermore, in the case of the second embodiment, are the small-diameter piston 88, the intake valve 86, and the large-diameter piston 92 separate? Although it has been described that it is formed of FB 4m, it is of course possible to have a structure in which three members are connected and fixed together as in the first embodiment.

Furthermore, the compressor is not limited to an oil-filled type compressor, and may be an oil-free type compressor.

The scroll type compression 11t according to the present invention is as described in detail above, and can prevent the phenomenon of the orbiting scroll coming loose at the time of start-up, as well as prevent delay in refueling, so that effective compression operation can be performed immediately at the time of start-up. be able to. Also,
Even if the gap between the wrap portions of the orbiting scroll and the fixed scroll is large, there is no problem, so the machining accuracy can be reduced, and the cost can be reduced accordingly.

[Brief explanation of the drawing]

FIG. 1 is an overall configuration diagram showing the first embodiment of the present invention, and FIG.
The figure is also an overall configuration diagram showing a second embodiment of the present invention. l...Casing, 2...Drive shaft, 4...Orbiting scroll, 6...Fixed scroll, 7...Compression chamber,
8... Suction port, 9... Intake pipe, lO... Discharge port, 11... Ri18... Oil, 19... Discharge pipe, 2
4...Discharge piping, 25...Pressure switch, 26...
... 9 pilot piping, 27... solenoid valve, 30.31.
32...Oil piping, 41 River capacity adjustment valve, 42...Upper cover, 43...Valve seat member, 44...Lower cut-14
6... End cover, 47... Inflow chamber, 48...
Outflow chamber, 50... Inflow port, 52... Outflow chamber, 53.
...Intake valve, 54...Spring, 55.56...Cylinder, 57...Piston, 59.60...Pressure chamber, 6
5... Check valve, 67... Auxiliary tank, 7o... Capacity adjustment valve, 71... Upper cylinder member, 72... Valve seat member, 73... Lower cylinder member, 74...・Inlet,
75...Inflow chamber, 76...Small diameter cylinder, 77...
... Valve seat, 79... Upper valve seat, 80... Lower valve seat, 81
...Communication port, 82...Valve chamber, 83...Outflow chamber, 8
4...Outlet port, 85...Large diameter cylinder, 86...
Intake valve, 87... Throttle passage, 88... Small diameter piston, 89.95... Pressure chamber, 91... Check valve, 92...
...Large diameter piston, 94...spring.

Claims (5)

[Claims] (1) While the orbiting scroll rotates while sliding in contact with the fixed scroll, the air sucked in from the suction port is compressed,
In a scroll compressor configured to discharge the compressed air from a discharge port, the suction port side is provided with a predetermined pressure that restricts the intake of air at startup, and after startup, the pressure in the space on the discharge port side is lower than the rated pressure. A capacity adjustment valve is provided that releases the restriction on the intake air amount from the suction port when the pressure reaches the pressure, and limits the intake air amount from the suction port again when the pressure in the discharge port side space reaches the rated pressure. Scroll-type compression featuring (2) The scroll type compression described in item (1), which is the required range of %g'fiis in the capacity adjustment valve-1, a closing valve that closes between the air inlet and the suction port when restricting the intake air amount. Machine. (3) A scroll compressor according to claim 0, wherein an auxiliary tank is provided between the closing valve and the suction port. (4) The capacity regulating valve is a suction throttle valve that communicates between the atmospheric inflow port and the suction port via a throttle passage when limiting the amount of intake air (the scroll according to claim 0). type compressor. (5) The scroll compressor according to claim (1), wherein the discharge port side space is the pressure of oil or air in the oil separator tank or the pressure in the discharge pipe.