JP5229304B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor, and relates to a reduction in oil content in a gas discharged from the compressor.

  Except in special cases, mechanical means are used to compress the gas. For this reason, oil is used to ensure the lubricity and sealing performance of each part in the mechanical means, but this oil is often mixed into the gas. However, in most applications of compressed gas, the oil in the gas is often prohibited or avoided. For example, in the case of the refrigerant gas used in the refrigeration cycle, the oil contained in the refrigeration cycle deteriorates the performance in the heat exchanging unit, and therefore the compressor of the refrigeration cycle needs to be devised to reduce the amount of oil discharged together with the gas as much as possible. .

  Conventionally, as shown in the scroll compressor of Japanese Patent Laid-Open No. 6-346884, a metal plate and a thin plate with a large number of holes are provided inside the sealed container of the discharge pipe, and the compressed gas is passed through the thin plate. The oil was separated.

JP-A-6-346884

  However, since it has a structure in which a high-speed rotating body such as a rotor of a motor is arranged in the flow path of the compressed gas, the compressed gas containing oil collides with the high-speed rotating body, and at that time, individual oil droplets are torn and a plurality of As a result of the separation into small oil droplets, there is a problem that the amount of oil adhering to a metal net or a thin plate having a large number of holes is reduced, and the amount of oil discharged from the compressor cannot be reduced. The reason will be described below.

The oil droplet has a gravity force proportional to the mass, and a viscous force approximately proportional to the product of the relative velocity with the surrounding gas and the surface area of the oil droplet. However, the gravitational force is negligible because it is usually smaller than the viscous force. The viscous force is expressed as follows.
(Viscous force) ≒ A x (surface area of oil droplet) x (relative velocity with surrounding gas) (1)
A is a proportionality constant. Here, the value of A is very large. This means that if the oil droplet has a slight relative velocity with respect to the gas, a large viscous force acts, so that the oil droplet moves almost on the gas flow. However, where the gas flow rate changes abruptly, such as inside a metal net or a thin plate with many holes, due to the inertia of the oil droplets, it does not ride on the gas flow and deviates from it. The action of trying to continue works. At this time, from the viewpoint of moving with the flow of gas, this action can be regarded as an inertial force. Since this inertia force is proportional to the mass which is the inertia of the oil droplet, it is expressed by the following equation.
(Inertia force) = B x (mass of oil droplet) x (acceleration of gas) (2)
By the way, oil droplets are almost spherical due to surface tension.
(Mass of oil droplets) ∝ (Diameter of oil droplets) ³ (3)
(Oil drop surface area) ∝ (Oil drop diameter) ² (4)
The following relational expression holds. Therefore, substituting the relational expressions (3) and (4) into (1) and (2) yields the following.
(Viscosity) ∝ A x (Diameter of oil drop) ² x (Relative velocity with surrounding gas) (5)
(Inertial force) ∝ B x (diameter of oil droplet) ³ x (gas acceleration) (6)
As shown in (6), an inertial force acts on the oil droplets. Dividing both sides of (5) and (6) gives the following formula.
(Inertial force) / (Viscosity force) ∝ (Diameter of oil droplet) × (B × Acceleration of gas) / (A × Relative velocity with surrounding gas) (7)

  Since the term including the relative velocity with the surrounding gas does not change greatly because A is large as described above, it is almost independent of the size of the oil droplet. Further, since the acceleration of the gas is determined by external conditions such as the shape of the gas flow path and the gas velocity, this is also almost independent of the size of the oil droplet. Therefore, it can be seen from (7) that the inertial force approaches or increases with respect to the viscous force as the diameter of the oil droplet increases. This means that when the oil droplets become large, the gas flow changes abruptly, and it is easy to come off from the gas flow. In other words, where the flow changes in a complicated manner, such as inside a mesh or a porous body, if the oil droplets become large, the oil droplets will deviate from the flow of the gas and will be easily adsorbed by contacting the mesh or porous body. This shows that the oil content of the oil is reduced. That is, conversely, the smaller the oil particle size, the lower the effect of reducing the oil content by the net or porous body.

  Therefore, in order to adsorb a large amount of oil with a small particle size, the change of the gas flow flowing therethrough is made sharper by making the mesh of the metal mesh finer or making many holes opened in the thin plate smaller. Although means can be considered, there arises a problem that the flow path resistance of the gas is increased by these means and the performance is lowered.

  In another scroll compressor shown in the above publication, a metal net or a thin plate with a large number of holes is provided so as to cover the compression operation port, and oil contained in the compressed gas is separated while passing therethrough. It had the composition to do. However, the operating conditions in which a large amount of refrigerant gas is dissolved in the oil and the surface tension of the oil is reduced, and the gas dissolved in the oil contained therein due to the sudden pressure reduction of the compressed gas at the compression operation port explosively occur. Under operating conditions such as vaporizing overcompression conditions, similar to the above example, the oil particle size in the compressed gas becomes small, and thus there is a similar problem.

An object of the present invention is to provide a compressor capable of reducing over-compression and improving performance .

The compressor according to the present invention is engaged with a fixed scroll member including an end plate and a scroll wrap standing on the end plate, and an orbiting scroll member engaged with the fixed scroll member. Between these scroll members, there is a compression chamber formed by the revolving motion of the orbiting scroll member without rotating, and a fixed back chamber that penetrates the end plate of the fixed scroll member and serves as the compression chamber and discharge pressure. In a scroll-type compressor comprising: a bypass hole to be connected; and a bypass valve that controls communication of the bypass hole and communicates the compression chamber and the fixed back chamber when the pressure of the compression chamber is higher than a discharge pressure. On the fixed tooth bottom side that is the compression chamber side opening of the bypass hole, along the scroll wrap of the fixed scroll member And providing a notch only in the direction.

According to the present invention, the re-expansion due to the high-pressure gas remaining in the hole is suppressed as much as possible, and the period of communication with the compression chamber of the high-pressure side bypass valve 23 is expanded to the high-pressure side, so that overcompression can be further reduced and performance is improved. Can

The longitudinal cross-sectional view of a 1st Example. The top view from the non-scroll wrap side of the fixed scroll member of a 1st Example. The top view from the scroll wrap side of the fixed scroll member of a 1st Example. The top view of the retainer of a 1st Example. Explanatory drawing of the compression process of a 1st Example. The longitudinal cross-sectional view of the bypass valve vicinity of a 1st Example (enlarged view of the R section in FIG. 1). The longitudinal cross-sectional view of the differential pressure control valve vicinity of a 1st Example (enlarged view of the P section in FIG. 1). The longitudinal cross-sectional view of the rotation side surface area vicinity of the differential pressure control valve of a 1st Example (enlarged view of the Q section in FIG. 7). The longitudinal cross-sectional view of the oil storage chamber vicinity of a 1st Example (enlarged view of the S section in FIG. 1). The perspective view of the oil droplet removal part of a 1st Example. The top view from the motor chamber side of the bearing support plate of a 1st Example. The top view from the motor chamber side of the bearing support plate of a 2nd Example. The top view from the motor chamber side of the bearing support plate of a 3rd Example. The longitudinal cross-sectional view of the oil storage chamber vicinity of a 4th Example (enlarged view of the S section in FIG. 1). The longitudinal cross-sectional view of the oil storage chamber vicinity of a 5th Example (enlarged view of the S section in FIG. 1). The assembly perspective view of the gas cover of a 5th Example. The top view from the oil storage chamber side of the gas cover of a 5th Example. The longitudinal cross-sectional view of the oil storage chamber vicinity of a 6th Example (enlarged view of the S section in FIG. 1). The top view from the motor chamber side of the bearing support plate of a 6th Example. The longitudinal cross-sectional view of the oil storage chamber vicinity of a 7th Example (enlarged view of the S section in FIG. 1). The longitudinal cross-sectional view of the oil storage chamber vicinity of an 8th Example (enlarged view of the S section in FIG. 1). The assembly perspective view of the gas cover of a 9th Example. The top view from the oil storage chamber side of the gas cover of a 9th Example. The perspective view of the oil droplet removal part of a 9th Example. The perspective view of the oil-drop removal part of a 10th Example. The longitudinal cross-sectional view of the oil storage chamber vicinity of an 11th Example (enlarged view of the S section in FIG. 1). The assembly perspective view of the oil trap plate of the 12th Example. The oil trap plate attachment perspective view of the twelfth embodiment. The longitudinal cross-sectional view of the attachment part vicinity of the oil trap plate of 12th Example. The perspective view of the oil trap plate of 13th Example. The perspective view of the oil trap plate of a 14th Example. The top view from the scroll wrap side of the fixed scroll member of 15th Example. The top view of the center vicinity from the scroll wrap side of the fixed scroll member of the 16th Example. The longitudinal cross-sectional view of the bypass hole of the 16th Example. The top view of the center vicinity from the scroll wrap side of the fixed scroll member of the 17th Example. The longitudinal cross-sectional view of the bypass hole of the 17th Example. The top view of the center vicinity from the scroll wrap side of the fixed scroll member of the 18th Example. The longitudinal cross-sectional view of the pressure difference control valve vicinity of a 19th Example (enlarged view of the P section in FIG. 1).

Before describing the embodiment, the operation of the present invention will be described.
First, the operation of the first means for achieving the above object will be described. When a gas containing oil is passed through the stored oil, it is necessary to blow the gas into the lower portion of the stored oil due to the difference in specific gravity between the gas and the liquid. The blown gas rises as bubbles in the stored oil. Since the entire area around the bubbles is oil, the probability that the oil droplets in the bubbles come into contact with the surrounding oil is very high. Furthermore, the rise of the bubbles in the stored oil is very small compared to the gas flow rate elsewhere in the compressor due to the viscosity of the oil, so that the oil droplets in the bubbles contact the surrounding oil. The time that can be taken is long, and the probability that the oil droplets in the bubbles come into contact with the surrounding oil becomes higher. The oil droplets in contact with the surrounding oil act to reduce the surface area by the surface tension of the oil. As a result, the small oil droplets are sucked into the oil around the bubbles. That is, when a gas containing oil is passed through the stored oil, the oil content of the gas coming out of the oil is reduced. This oil content reduction effect is not dependent on the size of the oil droplets in the bubbles, so it was difficult to remove not only large oil droplets but also nets and porous bodies raised in the prior art. Oil droplets having a small particle diameter can also be effectively removed. By the way, depending on the operating conditions, when the gas bubbles reach the oil level of the stored oil, the bubbles may be crushed and new oil droplets may be generated. However, since the rising speed of the bubbles is very slow, the oil droplets generated at this time are quite large. For this reason, the gas coming out of the stored oil contains only almost large oil droplets, but if this gas passes next through the porous body, large oil droplets have a high probability for the reasons described above. Can be removed. As a result, gas with a significantly reduced oil content can be discharged from the compressor.

Next, the operation of the second means for achieving the above object will be described. If the oil trap plate is placed so as to obstruct the gas flow path coming out from the compression operation port, the gas flow is suddenly bent there, but the oil contained in the gas has a large inertia, so this oil trap plate It adheres and the content of oil droplets in the gas is reduced. However, if this oil trap plate is too close to the compression operation port, the flow path cross-sectional area is reduced and the flow path resistance is increased, resulting in performance degradation. That is,
(Area of compression operation port) ≦ (Cross sectional area of gas flow path after exiting compression operation port) (8)
Is required. The gas flow after exiting the compression operation port is considered to be bent at right angles by this oil trap plate, and the cross-sectional area of the gas flow path after exiting the compression operation port is compressed to the circumference of the compression operation port. It can be regarded as the area multiplied by the distance from the compression operation port to the oil trap plate on the outer surface of the operation part, that is, the side surface area of the columnar solid figure with the height from the compression operation port to the oil trap plate. it can. Usually, the compression operation port has a circular shape or a shape close thereto, so that the situation hardly changes even if the compression operation port is a circle having the same cross-sectional area. Therefore, D the equivalent diameter previously defined, and the distance from the compression operation port to the oil trap plate and H, (area of the compression operation ^{opening) = π × D 2/4} (9)
(Cross sectional area of gas flow path after coming out of compression operation port) = π × D × H (10)
Therefore, the condition of (8) is
^{π × D 2/4 ≦ π} × D × H (11)
It becomes. This is organized as follows.
H ≧ D / 4 (12)

On the other hand, if H becomes too large, the rate at which the gas collides with the oil trap plate is reduced, so that the oil droplet removal rate in the gas is lowered. From the examination so far, it has been found that the oil drop removal rate is drastically reduced when D is 2 times or more, so the following relational expression is obtained.
H ≦ 2 × D (13)
From (12) and (13), if the oil trap plate is disposed at a position that is a distance of 0.25 from the equivalent diameter of the compression operation port by a distance of 2 times, the performance deterioration due to the channel resistance does not occur. The oil droplet removal rate in the gas is also increased.

  Scroll compression that presses the orbiting scroll member against the fixed scroll member by applying a pressure that is higher than the suction pressure by a substantially constant value (hereinafter referred to as an excessive suction pressure value) to the space on the anti-compression chamber side of the orbiting scroll member. A first embodiment implemented in the machine will be described with reference to FIGS. 1 is a longitudinal sectional view of the compressor, FIG. 2 is a plan view of the fixed scroll member from the non-scroll wrap side, FIG. 3 is a plan view of the fixed scroll member from the scroll wrap side, and FIG. 4 is a plan view of the retainer. 5 is an explanatory view of the compression stroke, FIG. 6 is a longitudinal sectional view in the vicinity of the bypass valve (enlarged view of R portion in FIG. 1), and FIG. 7 is a longitudinal sectional view in the vicinity of the differential pressure control valve (enlarged view of P portion in FIG. 1). 8 is a longitudinal sectional view of the differential pressure control valve in the vicinity of the back pressure chamber (enlarged view of portion Q in FIG. 7), and FIG. 9 is a longitudinal sectional view of the vicinity of the oil storage chamber (enlarged view of S portion in FIG. 1). FIG. 10 is a perspective view of the oil droplet removing unit, and FIG. 11 is a plan view from the motor chamber side of the bearing support plate. In this example, the compressor has a diameter of about 10 mm to 1000 mm.

  First, the structure will be described.

  The orbiting scroll member 3 is provided with a bearing holding portion 3s in which a scroll wrap 3b having an involute or an algebraic spiral or the like as a basic line is erected on an end plate 3a, and an orbiting bearing 3w is inserted on the back thereof, and orbiting Oldham grooves 3g and 3h. Provide.

The fixed scroll member 2 has a scroll wrap 2b erected on the end plate 2a, and as shown in FIG. 3, a non-turning reference surface 2u that is substantially flush with the scroll wrap tooth tip surface is provided on its outer periphery, and a peripheral groove 2c is provided there. Form. And four bypass holes 2e are provided in a tooth base. The reason why the four bypass holes 2e are provided here is to always open the bypass holes 2e in all the compression chambers 6 to be formed as shown in FIG. A bypass valve plate 23x (FIG. 2), which is a lead valve plate, and a retainer 23a for limiting the degree of opening of the valve plate 23x are fixed with a bypass screw 23h so as to cover the bypass hole 2e (FIGS. 4 and 6). Further, a compression operation port 2d is opened near the center. Further, a suction dig 2q (FIG. 3) is provided on the outer edge side of the tooth bottom surface, and a suction hole 2v for inserting the suction pipe 54 from the back is provided therein. The suction pipe 54 is inserted into the suction hole 2v. At that time, the valve body 24a and the check valve spring 24c are inserted to form the suction side check valve 24. Furthermore, a plurality of flow grooves 2 r for flowing gas and oil are provided on the outer periphery of the fixed scroll member 2. And one of them passes the motor wire 19n. A back-side conduction path 2β and a valve hole 2f (FIG. 7) are opened in the peripheral groove 2c to provide a valve seal surface or a valve seal line 2j. A suction-side conduction path 2α is provided to connect the side surface of the valve hole 2f and the communication groove 2δ communicating with the suction chamber 60. As shown in FIG. 7, a plate-like valve body 100a and a differential pressure valve spring 100c are inserted into the valve hole 2f, and the valve cap 100f is inserted into the valve hole with one end of the differential pressure valve spring 100c inserted into a spring positioning projection 100h. The differential pressure control valve 100 is formed by press-fitting into the valve cap insertion portion 2k having a diameter larger than 2f. At this time, the differential pressure valve spring 100c is compressed and presses the valve body 100a against the valve seal surface 2j. Since this pressing force determines the excessive suction pressure value, the depth of the valve hole 2f, the depth of the cap insertion part 2k, the thickness of the valve body 100a, the spring constant of the differential pressure valve spring 100c, Natural length must be managed accurately. In particular, it is necessary to finish the end portion of the differential pressure valve spring 100c to a surface substantially perpendicular to the central axis of the spring. Otherwise, buckling occurs when the spring 100c is compressed, the excessive suction pressure value becomes abnormally small, and the orbiting scroll member 3 is detached from the fixed scroll member 2 and normal operation is impossible. There is also a method in which the outer diameter of the valve cap 100f is made smaller than the diameter of the valve cap insertion portion 2k, and the valve cap 100f is expanded and stopped when the pressing force becomes a normal value. As the pressing force at this time, a method is adopted in which a rod is inserted into the back surface side conduction path 2β, one end is attached to the valve body 100a, and the force received by the rod is detected.
In the case of this method, there is no need to accurately manage the dimensions of the respective parts and the values of the spring constants, so that there is an effect that the mass productivity is improved. When these two methods are completed, the outer periphery of the valve cap 100f and the inner periphery of the valve cap insertion portion 2k must be completely sealed (the opposite side of the differential pressure valve spring 100C is the discharge space). Because this spring is higher than the pressure in the space). Bonding or welding may be performed to complete this seal. Here, a tapered shape in which the diameter of the tip is smaller than the root of the spring positioning protrusion 100h may be used. In this case, since the end portion of the differential pressure valve spring 100c is fixed only at the root of the spring positioning projection 100h, the movable portion of the spring does not come into contact with the positioning projection 100h, and the natural length of the spring is the natural length of the spring alone. It is secured as long. Therefore, there is a specific effect that an error from the set value of the excessive suction pressure value can be reduced.

  The frame 4 is provided with a fixed mounting surface 4b for mounting the fixed scroll member 2 on the outer peripheral portion, and a swivel pinching surface 4d on the inner side thereof, and one or a plurality of pinching surface grooves 4α are provided on the pinching surface 4d. It is done. Further on the inner side, frame Oldham grooves 4e and 4f (both not shown) are provided in order to place the Oldham ring 5 between the frame 4 and the orbiting scroll member 3. A shaft seal 4a and a main bearing 4m are provided at the center, and a shaft thrust surface 4c for receiving the shaft is provided on the scroll side. An oil holding space 4n is opened between the shaft seal 4a and the main bearing 4m. A plurality of flow grooves 4h serving as gas and oil flow paths are provided on the outer peripheral surface. And one of them passes the motor wire 19n. Further, a frame oil ring 44 is provided on the outer peripheral portion opposite to the fixed mounting surface 4b.

  The Oldham ring 5 is provided with frame protrusions 5a and 5b (both not shown) on one surface, and swivel protrusions 5c and 5d on the other surface.

As shown in FIG. 1, the shaft 12 is provided with a shaft oil supply hole 12a, a main bearing oil supply hole 12b, a shaft seal oil supply hole 12c, and a sub-bearing oil supply hole 12i. Further, there is a balance holding portion 12h having an enlarged diameter at the upper portion thereof, and a shaft balance 49 is press-fitted there.
Further, an eccentric portion 12f is provided.

  The rotor 15 incorporates a non-magnetized permanent magnet 15b in a laminated steel plate 15a and is provided with rotor balances 15c and 15p at both ends.

  The stator 16 is provided with a plurality of stator grooves 16c serving as a flow path for compressive gas and oil on the outer peripheral portion of the laminated steel plate 16a, and a coil through hole 16v is opened therein. The coil 16w passes through here, and the auxiliary bearing side coil end portion 16x and the main bearing side coil end portion 16y, which are the folded portions of the coil, are arranged on both sides of the stator 16. Further, a stator hole 16m penetrating from the coil through hole 16v to the outer peripheral portion is opened inside the laminated steel plate 16b. This is because if the stator hole 16m is provided on the inner side of the coil through hole 16v, the magnetic flux density between the rotor 15 and the stator 16 is greatly reduced, and the motor efficiency is reduced.

These components are assembled as follows. First, the shaft 12 into which the shaft balance 49 is press-fitted, bonded or shrink-fitted is inserted into the main bearing 4a of the frame 4, and the rotor 15 is press-fitted or shrink-fitted. Further, the Oldham ring 5 is mounted on the frame 4 by inserting frame protrusions 5a and 5b (both not shown) of the Oldham ring 5 into the frame Oldham grooves 4f and 4e. Further, the orbiting scroll member 3 is swung while inserting the orbiting protrusions 5c and 5d of the Oldham ring 5 into the orbiting Oldham grooves 3g and 3h, and inserting the eccentric portion 12f of the shaft 12 into the orbiting bearing 3w. It is mounted on the sandwiching surface 4d. The fixed scroll member 2 is engaged with the orbiting scroll member 3, and the fixed scroll member 2 is attached to the frame 4 by a wrap fixing screw 53 at a position where the rotational torque becomes minimum or below a certain reference value while rotating the shaft 12. To fix. According to this method, although it does not greatly deviate from the optimum position, it is difficult to fix it at the optimum position with high accuracy. At this time, the thickness of the end plate 3a of the orbiting scroll member 3 is set to be about 5 to 20 μm smaller than the distance between the orbiting surface 4d and the non-orbiting reference surface 2u, and the orbiting scroll member 3 and the fixed scroll member are arranged. 2 defines the maximum separation distance in the axial direction. Therefore, the fixed scroll member 2 can be attached to the frame 4 with a higher accuracy by using the following method. As shown in FIGS. 2 and 3, two positioning holes 2p with high positional accuracy and dimensional accuracy are formed in the outer peripheral portion of the fixed scroll member 2, and a high-precision positioning hole (not shown) is similarly formed at the corresponding frame position. ). A positioning pin is press-fitted into the hole on the frame side in a state protruding from the fixed mounting surface 4b. The positioning hole 2p is inserted into the positioning pin, and the fixed scroll member 2 is attached to the frame 4 with high accuracy. Since this is an assembling method depending on the processing accuracy of each component, there is a risk that the assembly accuracy may be lowered if the component is not processed with high accuracy. Therefore, this method is effective only when the parts can be kept with high accuracy. On the contrary, the assembly method described above can be said to be a method with high mass productivity because it can ensure a certain level of assembly accuracy even when the component accuracy is not so high. At this time, a back surface excessive suction pressure region 99 is formed on the back surface of the orbiting scroll member 3. Next, the cylindrical casing in which the bearing 16 is welded or press-fitted in advance with the stator 16 being shrink-fitted, press-fitted or bonded, and having a central hole 18c at the center and a lower flow passage hole 18a at the bottom and welded with an oil ring. In 31, the above-described assembly portion is inserted, and tack welding is performed on the side surface of the frame 4 or the fixed scroll member 2. Here, as shown in FIG. 11, the height of the highest point of the lower flow passage opening 18a is lower than the lowest point of the central hole into which the rotor of the stator 16 is inserted (the inner diameter height of the stator in the figure). Set. Moreover, you may adhere | attach instead of tack welding. At this time, since the assembly portion by welding and the cylindrical casing 31 are not deformed, the performance is improved. Thus, a motor 19 is formed by the rotor 15 and the stator 16, and a motor chamber 62 is formed between the bearing support plate 18 and the frame 4. Next, the bearing housing 70 is incorporated so that one end of the shaft 12 coming out of the central hole 18 c of the bearing support plate 18 is inserted into a cylindrical hole of a spherical bearing 72 mounted on the bearing housing 70, and the shaft 12 The position of the bearing housing 70 is adjusted while detecting the rotational torque, and the bearing housing 70 is spot welded to the bearing support plate 18 at a position where the rotational torque is minimized or below a certain reference value. Then, an oil filler cap 90 welded to the bent oil supply pipe 71 is inserted into the bearing housing 70 and then spot welded to the bearing housing 70 with a seal 73 interposed therebetween.
Here, the surface roughness accuracy of the sealing surface may be increased and the pressing force of the sealing surface may be increased so that the sealing is performed without sandwiching the seal 73. Moreover, you may adhere | attach. These eliminate the need for a seal and reduce the number of parts. Thereafter, a magnet 89 is provided near the tip of the oil supply pipe 71. On the other hand, a plurality of wire meshes 45a are laminated by the lamination holding part 45b to form an oil droplet removing part 45 that becomes a porous body, and this is fixed to the bottom casing 21 by the attaching part 45f. A discharge pipe 55 is welded to the upper portion of the bottom casing 21. Then, the bottom casing 21 is welded to the cylindrical casing 31 to form an oil storage chamber 80. At this time, the bottom casing 21 is inserted into the cylindrical casing 31 to a position where there is no gap between the oil droplet removing portion 45 and the bearing support plate 18. Next, the upper casing 20 in which the hermetic terminal 22 and the suction pipe attachment pipe 37 are welded to the cylindrical casing 31 is welded by attaching the motor wire 19n to the inner terminal of the hermetic terminal 22, and the suction pipe. 54 is inserted into the suction pipe attachment pipe 37 and the gap is brazed to form the fixed back chamber 61. In this state, a current is passed through the stator 16 to magnetize the permanent magnet 15b in the rotor 15 to form a motor 19. Then add the oil. In the lower part of the frame 4 and the fixed scroll member 2 partitioning the fixed back chamber 61 and the motor chamber 62, the flow grooves 4 h and 2 r exist, and the motor chamber 62 and the oil storage chamber 80. Since the lower circulation port 18a exists in the lower part, the storage oil 69 is accumulated in the lower part of the fixed back chamber 61, the motor chamber 62, and the oil storage chamber 80a. Therefore, these three chambers have the role of oil storage chambers.

  Next, the operation will be described. First, the operation immediately after starting the compressor will be described.

By starting the rotation of the motor 19, the shaft 12 rotates and the orbiting scroll member 3 starts orbiting motion. Here, the turning radius of the orbiting scroll member 3 is set to be smaller than the size determined geometrically from the scroll wrap shape. This is because there is always a processing error in the shape of the scroll wraps 2b and 3b. If the setting is not made small, the side surface of the lap will come into pressure contact, increasing the friction loss and the progress of wear. This is because galling may cause adhesion, or the lap may be destroyed, resulting in inoperability. Here, since the Oldham ring 5 is provided, rotation of the orbiting scroll member 3 is prevented. By this operation, the gas in the suction chamber 60 formed in the outer peripheral portion of the area where the two scroll wraps 2b and 3b mesh with each other is substantially confined and compressed in the compression chamber 6 formed between the scroll members, and the compression operation is performed. It begins to be discharged into the fixed back chamber 61 from the mouth 2d. By the way, as shown in FIG. 7, the thickness of the end plate 3a of the orbiting scroll member 3 is made to be smaller by about 5 to 70 μm than the distance between the orbiting surface 4d and the non-orbiting reference surface 2u, and the orbiting scroll member. 3 and the maximum separation distance in the axial direction of the fixed scroll member 2 are defined. For this reason, immediately after the compressor is started, the orbiting scroll member 3 is separated from the fixed scroll member 2 by the separating force by the gas in the compression chamber 6 and moves to the frame 4 side by the distance described above. Therefore, the anti-wrap side of the end plate 3a and the turning sandwiching surface 4d slide, and a gap corresponding to the maximum separation distance is formed between the end of the end plate 3a and the non-turning reference surface 2u. At the same time, the gap between the tip of the wrap and the bottom of the wrap is about the same, so the internal leakage is large and high-efficiency operation is not possible. By increasing the pressure to the maximum allowable value, internal leakage can be suppressed, and the suction pressure can be sufficiently reduced or the discharge pressure can be sufficiently increased. The gas discharged from the compression operation port 2d to the fixed back chamber 61 passes through the fixed scroll member 2 and the flow grooves 2r and 4h on the outer periphery of the frame 4, and the motor 19 and the frame 4 in the motor chamber 62. Also flows into the space between. The gas further reaches the bearing support plate 18 side of the motor chamber 62 through the stator groove 16 c and the gap between the rotor 15 and the stator 16. Since the compressed gas that has spread so far loses its destination, it begins to accumulate and the pressure rises. This pressure increase pushes the stored oil 69 accumulated in the lower part of the motor chamber 62 and the fixed back chamber 61 downward. As a result, the stored oil 69 flows into the oil storage chamber 80 through the lower flow path port 18a and raises the oil level on the oil storage chamber side. When the oil level of the motor chamber 62 reaches the height of the highest point of the lower flow path port 18a, the lower flow path port 18a becomes a flow path and gas flows from the motor chamber 62 into the oil storage chamber 80. At this time, the gas is blown out from below the storage oil 69 collected in the oil storage chamber and rises in the form of bubbles. Here, since the height of the highest point of the lower flow passage opening 18a is set lower than the lowest point of the central hole into which the rotor of the stator 16 is inserted, the oil level of the motor chamber 62 is the rotor. Therefore, the rotor 15 that rotates the stored oil 69 at high speed does not form fine oil droplets, and the oil content of the gas can be reduced. By the way, if the set height of the lower flow passage opening 18a is determined so that the height of the oil surface on the motor chamber 62 side is not covered by the rotor 15, the oil flow is generated by the flow of gas generated by the rotation of the rotor. Oil droplets are generated from the surface, and the content of oil droplets in the gas does not decrease much. Therefore, the oil level on the motor chamber 62 side is preferably lowered to a position where the gas flow generated by the rotation of the rotor is reduced to about half of the rotor surface speed. As described above, since a large amount of stored oil can be stored inside the small compressor without the oil level of the motor chamber 62 being applied to the rotor 15, the possibility of running out of oil is low and the reliability is high. There is an effect peculiar to the present embodiment that the horizontal compressor can be realized in a small size. The gas that has risen to the surface of the storage oil 69 in the oil storage chamber 80 passes through the oil droplet removing portion 45 made of a porous material, and is then discharged from the discharge port formed by the discharge pipe 55 to the outside of the compressor. The The pressure in the back excessive suction pressure region 99 immediately after the start of the compressor is close to the suction pressure due to the gap between the sandwiching surface groove 4α of the frame 4 and the lap side of the end plate 3a and the non-rotating reference surface 2u as described above. It is pressure. The oil in the oil storage chamber 80 enters the oil supply cap 90 from the oil supply pipe 71 due to a differential pressure between the oil pressure in the back excessive suction pressure region 99 and the oil storage chamber 80 which is substantially close to the discharge pressure. The spherical force is supplied to the spherical bearing portion of the spherical bearing 72 by centrifugal force. Furthermore, since the cross-sectional area is large, it enters the shaft oil supply hole 12a having almost no flow resistance, and a part of the bearing is provided on the center hole side of the spherical bearing 72 through the auxiliary bearing oil supply hole 12i by applying centrifugal force. Similarly, the other part is supplied to the shaft seal 4a through the shaft seal oil supply hole 12c when centrifugal force is applied in the same manner, and the other part is supplied to the main bearing oil supply hole 12b by centrifugal force. After passing through the main bearing 4m, the remainder reaches the center of the rear surface of the orbiting scroll member 3 and then is supplied to the orbiting bearing 3w by the same differential pressure and centrifugal force as described above. As a result, a rear discharge pressure region 95 to which discharge pressure is applied is formed at the center of the rear surface of the orbiting scroll member 3. The oil supplied to the main bearing 4m and the slewing bearing 3w rises in temperature due to friction there, and then enters the back oversuction pressure region 99. At this time, since the average oil pressure in the bearing portion is higher than the pressure in the back surface oversuction pressure region 99 and closer to the pressure on the oil storage chamber 80 side, the oil is blown out to the back surface oversuction pressure region 99. As a result, the temperature rise due to the friction of the bearing portion and the rapid drop in pressure lower the solubility of the gas component of the oil, and the gas component dissolved in the oil vaporizes all at once. Since the heat of vaporization is taken away from the surroundings at this time, there is a specific effect that the reliability of the main bearing 4m and the slewing bearing 3w is improved in order to keep the temperature level in the vicinity low. Further, since the gas component is vaporized, the oil becomes fine oil droplets, so that the oil easily moves along the gas flow.
As will be described later, since the gas is directed to the orbiting scroll member 3 side, the oil also flows in that direction. Since the Oldham ring 5 is in the middle of the path from the main bearing 4 m and the orbiting bearing 3 w to the orbiting scroll member 3, oil droplets are reliably supplied to the sliding portion of the Oldham ring 5. Therefore, there is also a specific effect that the reliability of the Oldham ring sliding portion is improved. As a result, the amount of gas flowing into the back surface excessive suction pressure region 99 increases rapidly immediately after the compressor is started. As shown in FIG. 7, this gas flows into the suction chamber 60 together with oil through the sandwiching surface groove 4α and the gap between the end plate 3a and the non-turning reference surface 2u. And the oil in this flowed into the compression chamber 6 having a slight gap in the axial direction, and improved the sealing performance therefor, thereby reducing the internal leakage of the compression chamber and promoting the increase of the discharge pressure. Then, the gas exits to the fixed back chamber 61 from the compression operation port 2d together with the gas. In addition, since the gap between the lap side of the end plate 3a and the non-rotating reference surface 2u is small and the amount of oil in the flowing fluid is large and partially forms a seal portion, the gas flowing into the back oversuction pressure region 99 and The amount of gas flowing out and the amount of oil are small compared to the amount of oil, and the pressure in the back oversuction pressure region 99 rises rapidly. As a result, with the contribution of the pressure increase in the back surface discharge pressure region 95 accompanying the increase in the discharge pressure, the attraction force that is the force for pressing the orbiting scroll member 3 against the fixed scroll member 2 increases rapidly. The magnitude of the attracting force becomes equal to or greater than the magnitude of the separating force almost immediately after startup or in a very short time, and the orbiting scroll member 3 is pressed against the fixed scroll member 2. As a result, since the gap between the tooth tip and the tooth bottom of the scroll wrap is reduced, the sealing property of the compression chamber 6 is improved, the amount of internal leakage of gas during compression is reduced, and compared with immediately after startup. The performance is dramatically improved and the system is shifted to the normal operating state. By the way, if a surface film having a conformability that can be scraped when pressed against the surface of the scroll members 2 and 3 that form a sealing surface when the compression chamber 6 is formed, the scroll members 2 and 3 are pressed. Since the gap between the tooth tip and the tooth bottom of the scroll wrap is almost eliminated at the time, the sealing performance of the compression chamber 6 is further improved, and the amount of internal leakage of gas during compression is further reduced, compared with immediately after startup. The performance will be further improved and it will shift to the normal operating state. Even if this conformable film is provided only on one scroll member, it is effective.

  Next, an operation during normal operation in which the orbiting scroll member 3 is pressed against the fixed scroll member 2 will be described.

Except that all the gas and oil that flowed into the back oversuction pressure region 99 do not flow directly into the suction chamber 60, this is the same as immediately after the start of the compressor. Therefore, only this part is mainly shown in FIGS. It explains using. The gas and oil that have flowed into the back excessive suction pressure region 99 pass through the sandwiching surface groove 4α and the gap between the anti-wrap surface of the end plate 3a and the swivel clamping surface 4d, and the side surface of the end plate 3a and the frame 4 Enter the swivel side surface area 67 which is the space between. A part of them flows into the suction chamber 60 while lubricating both sliding surfaces of the lap side of the end plate 3a and the non-turning reference surface 2u. Since the flow resistance between the swivel side surface area 67 and the back surface oversuction pressure region 99 is small, the pressure in the swivel side surface region 67 is substantially equal to the pressure in the back surface oversuction pressure region 99. As can be seen from FIG. 8, since the peripheral groove 2c always communicates with the turning side surface region 67, the pressure in the peripheral groove 2c becomes the pressure of the back surface excessive suction pressure region 99, and the back side conduction path 2β The pressure in the back oversuction pressure region 99 is applied to the frame-side surface of the valve body 100a of the differential pressure control valve 100 via. Since the space on the opposite surface side of the valve body 100a communicates with the suction chamber 60 which is the suction pressure by the suction side conduction path 2α, the pressure in the back surface excessive suction pressure region 99 is more than the difference from the suction pressure. When it becomes higher than the excessive suction pressure value that is a constant value corresponding to the pressing force of the pressure valve spring 100c, the valve body 100a moves toward the differential pressure valve spring 100c. As a result, the back side conduction path 2β, the valve body 100c, and the valve seal surface other than the gas and oil in the swivel side surface region 67 that have flowed into the suction chamber 60 via the sliding surface. Alternatively, the gas flows into the suction chamber 60 through the clearance of the valve seal line 2j, the side surface of the valve body 100c, the valve hole 2f, and the suction side conduction path 2α. Then, it is mixed with the gas in the compression chamber 6 to improve the sealing performance of the compression chamber 6 and is transferred to the center of the wrap and discharged from the compression operation port 2d. As a result, the compressed gas discharged from the compression operation port 2d contains the entire amount of oil supplied to the bearing. In this way, the pressure in the back excessive suction pressure region 99 is controlled to a pressure that is higher than the suction pressure by a certain value corresponding to the pressing force of the differential pressure valve spring 100c.
That is, the pressure in the excessive suction pressure region 99 is roughly controlled as follows.

Let A (super suction pressure value) be a certain constant,
(Pressure in the back side over suction pressure region 99) ≈ (suction pressure + A)
As a result, the orbiting scroll member 3 is pressed against the fixed scroll member 2 in the entire required operating range, and the biasing force obtained by subtracting the pulling force from the pulling force is reduced in a wide range of operating conditions, thereby reducing the sliding loss. There is an effect that a high-performance compressor can be realized. By the way, the gas passing through the back side super suction pressure region 99 is a flow that is short-circuited from the discharge system to the intermediate pressure chamber 68 in the middle of compression in the compressor, and is similar to the internal leakage in the scroll wrap as a result. Therefore, it is necessary to reduce as much as possible. Here, since there is a bearing gap which is a throttle channel of the discharge back-to-back flow path 102, the flow rate is very small, and the performance of the compressor does not deteriorate.

  Here, since the gas discharged from the compression operation port 2d includes all the oil supplied to the slewing bearing 3w and the main bearing 4m as described above, for example, the discharge pressure and the back over-suction pressure region 99 As the pressure difference increases, the amount of oil in the compressed gas that exits from the compression operation port 2d increases. Further, the smaller the rotational speed of the orbiting scroll member 3 is, the smaller the amount of compressed gas per unit time is. However, since the bearing oil supply amount is the same, the oil content of the gas coming out of the compression operation port 2d is reduced. Increase. Next, this gas enters the motor chamber 62 through the flow grooves 2r and 4h. At this time, due to the frame oil ring 44 and the main bearing side coil end portion 16y, the main flow does not go to the rotor 15 side, but flows through the stator groove 16c and the stator hole 16m. Due to this flow, the main flow of the gas that has passed through the laminated steel plate 16a of the stator 16 does not go to the rotor 15 side by the auxiliary bearing side coil end portion 16x, but escapes toward the bearing support plate 18. And although it goes to the said lower flow path opening 18a below, this flow does not approach the said rotor 15 by the said oil ring 46. FIG. Since gas passes through the stator 16, the coil 16 w and the laminated steel plate 16 a of the stator that are at a high temperature can be cooled, so that there is a specific effect that motor efficiency is improved. Here, when passing through and near the porous body such as the coil end portions 16x and 16y of the stator 16, the oil collides with the coil end portion due to the inertia of the oil droplets and adheres to the coil end portion. There is a specific effect that it becomes a solid and falls into the storage oil 69 in the lower part or flows through the stationary part and the oil content is reduced. In addition, since the main flow of gas does not approach the rotor 15 rotating at high speed by the coil end portions 16x and 16y and the oil ring 46, there are very few oil droplets in contact with the rotor 15 and fine oil droplets are formed. Since it hardly occurs, there is a specific effect that oil separation efficiency from gas by a porous body such as a coil end portion is improved. Although the oil content of the gas reaching the lower flow path port 18a is considerably reduced by the means described above, the gas is blown from the lower flow path port 18a through the lower part of the stored oil 69 in the oil storage chamber 80. This has the effect of further reducing the oil content. The blown gas rises as bubbles in the storage oil 69. Since the entire area around the bubbles is oil, the probability that the oil droplets in the bubbles come into contact with the surrounding oil is very high. Furthermore, the rise of the bubbles in the storage oil 69 is very small compared to the gas flow rate at other points in the compressor due to the viscosity of the oil, so that the oil droplets in the bubbles are separated from the surrounding oil. The contact time is long, and the probability that the oil droplets in the bubbles come into contact with the surrounding oil becomes higher. The oil droplets in contact with the surrounding oil act to reduce the surface area by the surface tension of the oil. As a result, the small oil droplets are sucked into the oil around the bubbles. Such an effect brings about the above-mentioned effect. This oil content reduction effect does not depend on the size of the oil droplets in the bubbles, so it is also possible to effectively remove oil droplets having a small particle diameter, which were difficult to remove with the porous material raised in the prior art. . However, when the gas bubbles reach the oil level of the stored oil 69, the bubbles are crushed and new oil droplets are generated. However, since the rising speed of the bubbles is very slow, the oil droplets generated at this time are quite large. For this reason, only large oil droplets are contained in the gas coming out of the stored oil. However, since this gas passes through the oil droplet removing section 45 which is a porous body, for the reasons described above, large oil droplets are generated. Can be removed with high probability. As a result, there is an effect that the gas whose oil content is significantly reduced can be discharged from the compressor. The end plate 2a of the fixed scroll member 2 is provided with four bypass holes 2e. The bypass valve plate 23x is positioned so that the valve portion is positioned so as to cover the bypass valve seal surface 2λ of each of the bypass holes 2e, and fixed by the bypass screw 23h together with the retainer 23a, thereby forming the bypass valve 23. As a result, these bypass valves 23 are opened when the pressure in the compression chamber 6 becomes higher than the pressure in the fixed back chamber 61 which is a part of the discharge system. Since the pressure in the fixed back chamber 61 is a discharge pressure, the bypass valve has an effect of communicating the compression chamber 6 and the discharge system when the pressure in the compression chamber 6 is higher than the discharge pressure. Actually, the opening timing of the bypass valve 23 is slightly shifted due to the pressure distribution on the bypass valve seal surface 2λ and the surface tension of the oil there. In this manner, as the attraction force adding means for the orbiting scroll member 3, the over suction pressure region 99 is provided on the orbiting back surface, and the bypass valve 23 is provided. Therefore, the over suction pressure value can be set small, and a wide operating range is provided. The urging force can be set small. As a result, there is a specific effect that the total heat insulation efficiency and reliability can be increased in a wide operating range. By the way, as shown in FIG. 5, since the four bypass holes 2e are provided so as to always connect the compression chamber 6 and the fixed back chamber 61, the pressure is extremely high no matter what timing the liquid compression occurs. The fluid is discharged to the fixed back chamber 61 by opening the bypass valve before the fluid reaches the fixed rear chamber 61. As a result, there is a unique effect that the risk of damage to the lap can be avoided and the reliability can be improved. In addition, since overcompression can be suppressed even when the pump operation is extremely close to a low pressure ratio, there is an effect that the overall heat insulation efficiency can be increased in a wide operating condition range on the low pressure ratio side.

  Here, at the time of starting the compressor, if an operator is provided with a system for performing an operation of restricting both or one of the piping system connected to the suction pipe 54 and the piping system connected to the discharge pipe 55, A reduction in suction pressure or an increase in discharge pressure can be realized more reliably. As a result, there is an effect that it is possible to shift to a normal operation of pressing the orbiting scroll member 3 against the fixed scroll member 2 in a shorter time.

  Next, a description will be given based on the second embodiment. Since it is the same as that of the first embodiment except that the position of the highest point of the lower flow passage opening 18a of the bearing support plate 18 is set at the center, the description of the structure, operation, and effects of other portions is omitted. In the first embodiment, since the upper side of the lower flow path port 18a is horizontal, the position where the gas may blow out into the stored oil 69 is the entire upper side. For this reason, when bubbles start to form at a plurality of locations close to the upper side of the lower flow path port 18a, the bubbles are combined in the bubble growth process. Let us consider a case where the timing of this coalescence is such that each bubble alone is barely detachable from the upper side of the lower flow path port 18a. The size of the bubbles formed by combining at this time becomes a size that cannot be formed by bubbles that are grown independently without being combined. If the bubbles are large, the ratio of the surface area to the volume of the bubbles is small, so the probability that the oil droplets in the bubbles are in contact with the surrounding oil is low. Further, the rising of the bubbles in the stored oil 69 is promoted by a force obtained by subtracting gravity from the buoyancy of the bubbles, and is suppressed by the viscous force of the oil. The former force is roughly proportional to the volume of the bubble and the latter force is roughly proportional to the surface area of the bubble. When the bubbles are large, the ratio of the surface area to the volume of the bubbles is reduced, so that the rising speed of the bubbles is increased and the time during which the oil droplets in the bubbles can come into contact with the surrounding oil is shortened. From the above two points, when the bubbles are large, the effect of reducing the oil content is reduced. On the other hand, in the present embodiment, the place where bubbles can be generated is determined at one place in the center of the upper side of the lower flow passage opening 18a, and thus the problem of the first embodiment is eliminated. As a result, there is an effect that the gas in which the content of oil in the discharge gas is further greatly reduced can be discharged from the compressor. Further, in the first embodiment, as shown in FIGS. 9 and 10, the oil droplet removing unit 45 has a porous body only at the central portion, so that the mounting posture of the compressor is the cylindrical shaft of the compressor. When the oil is rotated to the center, bubbles rise at the location off the center of the stored oil 69 and oil droplets are generated at the oil surface portion outside the center, so that these oil droplets are removed without passing through the porous body. There is a high possibility of passing through the portion 45 and reaching the discharge port. On the other hand, in this embodiment, since the bubbles rise near the center of the stored oil 69, the problem of the first embodiment is eliminated. As a result, there is an effect that the gas whose oil content is significantly reduced can be discharged from the compressor.

  Next, a third embodiment will be described based on a plan view from the motor chamber side of the bearing support plate of FIG. Except for the upper side of the lower flow passage opening 18a of the bearing support plate 18 having a sawtooth shape, it is the same as in the first embodiment, and the description of the structure, operation, and effects of the other parts is omitted.

In the present embodiment, bubbles are formed at a sawtooth-like peak on the upper side of the lower flow path opening 18a. As a result, coalescence of bubbles, which is a problem in the first embodiment, is not generated, and there is an effect that the gas in which the content of oil in the discharge gas is further reduced can be discharged from the compressor. However, if the period interval of the saw teeth is made smaller than the diameter of the bubbles that can grow on the upper side of the lower flow path opening 18a, coalescence occurs, so the saw teeth must be formed at least at an interval larger than that. In addition, when the bubbles rise in the storage oil 69, they are influenced by the flow of the storage oil 69 and do not rise straight. Therefore, the period interval of the sawtooth is larger than the diameter of the bubbles that can grow on the upper side of the lower flow passage opening 18a. Also, it is better to increase the width of the left and right sway due to the flow of the stored oil 69.
Further, since the crests on both sides are taken, air bubbles rise near the center of the stored oil 69 and oil droplets are generated at the oil surface near the center. Therefore, most of the oil droplets are porous bodies of the oil droplet removing unit 45. Pass through. As a result, there is an effect that the gas whose oil content is significantly reduced can be discharged from the compressor.

  Next, a fourth embodiment will be described based on a longitudinal sectional view in the vicinity of the oil storage chamber in FIG. 14 (enlarged view of the S part in FIG. 1). Since it is the same as that of the said 1st thru | or 3rd Example except having made the oil droplet removal part 45 incline, description of the structure of another part, operation | movement, and an effect is abbreviate | omitted.

  In the case of the first embodiment in which the oil droplet removing portion 45 is not inclined, for example, the oil droplets adhering to the wire mesh 45a are accumulated to some extent and united, and a part thereof extends to the laminated holding portion 45b. Then, the oil adsorbed on it collects again and coalesces. A part of the oil spreads to the bottom casing 21 and returns to the stored oil 69 by gravity. As described above, since the time of adhering to the oil droplet removing unit 45 is long, the oil droplet once captured may return to the gas again due to the flow of the gas passing therethrough. In the present embodiment, since the oil droplet removing portion 45 is inclined, the oil droplets captured by the wire mesh 45a quickly flow toward the bottom casing 21 due to gravity and travel along the attachment portion of the oil droplet removing portion 45. Then, it flows down to the surface of the bottom casing 21. Therefore, since the oil droplets once captured do not return to the gas again as described above, there is an effect that the gas whose oil content is greatly reduced can be discharged from the compressor. In the present embodiment, the oil droplet removing portion 45 is inclined toward the bottom casing 21 side, but may be inclined toward the bearing support plate 18 side. At this time, the oil droplet removing portion 45 may be fixed to the bearing support plate 18.

  Next, a vertical sectional view of the vicinity of the oil storage chamber of FIG. 15 (enlarged view of the S portion in FIG. 1), an assembly perspective view of the gas cover of FIG. 16, and an oil storage chamber side of the gas cover of FIG. This will be described based on the plan view. Since it is the same as that of the 1st thru | or 4th Example except having provided the gas cover 88 which attached the oil-drop removal part 45 to the bearing support plate 18, description of the structure of another part, operation | movement, and an effect is abbreviate | omitted.

  The gas cover 88 fixes the oil droplet removing portion 45 inside the annular cover 88d and then brazes, bonds or welds the base plate 88c to form a gas vent passage 88a therein. At this time, a central collar 88g and an outer peripheral claw 88f are provided in order to determine a fixing place. As a result, since the gas flow path of the oil storage chamber 69 becomes the gas vent passage 88a in the gas cover 88, the risk of gas bubbles entering the oil supply pipe 71 is very low. As a result, when the gas stored in the motor chamber passes through the gas vent passage 88a from the lower circulation port 18a, it then passes through the oil droplet removing section 45 and reaches the discharge pipe 55. By this route, as described in the above embodiment, there is an effect that the gas in which the content of oil in the discharge gas is greatly reduced can be discharged from the compressor. In this embodiment, the oil droplet removing unit 45 is set horizontally, but if it is inclined, the same effect as in the fourth embodiment can be obtained. Here, the direction of the gas flowing into the oil storage chamber 80 is directed toward the discharge pipe 55 after colliding with the side surface of the bottom casing 21 because the passage opening 88b is opened on the side surface of the gas cover. As a result, there is a specific effect that the content of oil droplets in the gas is further reduced due to the collision with the bottom casing 21.

  Next, a sixth embodiment will be described based on a longitudinal sectional view in the vicinity of the oil storage chamber in FIG. 18 (enlarged view of the S portion in FIG. 1) and a plan view from the motor chamber side of the bearing support plate in FIG. Since it is the same as that of the said 4th Example except having provided the upper flow path opening 18b in the upper part of the bearing support plate 18, description of the structure of another part, operation | movement, and an effect is abbreviate | omitted.

  The upper flow path port 18b forms a flow path from the motor chamber 62 to the gas area of the oil storage chamber 80. At this time, the flow path resistance of the upper flow path port 18b is slightly added, the pressure of the oil storage chamber 80 is slightly lower than the pressure of the motor chamber 62, and oil is stored in the oil storage chamber 80 by this pressure difference. To do. As a result, during operation at a very large flow rate, if the upper flow passage port 18b is not provided, the oil droplet removal unit 45 cannot capture the oil bubbles when the bubbles in the oil come to the oil surface and collapse. In this example, the amount of gas that passes through the oil is small, so the generation of oil droplets due to foaming on the oil surface is greatly reduced, and the oil content in the discharge gas is greatly reduced. There is an effect that discharged gas can be discharged from the compressor. Here, as shown in FIG. 18, the upper flow path port 18b may be two or three instead of one at the center.

  Next, a seventh embodiment will be described based on a longitudinal sectional view in the vicinity of the oil storage chamber of FIG. 20 (enlarged view of S part in FIG. 1). Since it is the same as that of the said 5th Example except having provided the upper flow path opening 18b in the upper part of the bearing support plate 18, description of the structure of another part, operation | movement, and an effect is abbreviate | omitted. The upper flow path port 18b forms a flow path from the motor chamber 62 to the gas area of the oil storage chamber 80. At this time, the flow path resistance of the upper flow path port 18b is slightly added, the pressure of the oil storage chamber 80 is slightly lower than the pressure of the motor chamber 62, and oil is stored in the oil storage chamber 80 by this pressure difference. To do. As a result, during operation at a very large flow rate, if the upper flow passage port 18b is not provided, the oil droplet removal unit 45 cannot capture the oil bubbles when the bubbles in the oil come to the oil surface and collapse. In this example, the amount of gas that passes through the oil is small, so the generation of oil droplets due to foaming on the oil surface is greatly reduced, and the oil content in the discharge gas is greatly reduced. There is an effect that discharged gas can be discharged from the compressor.

  Next, an eighth embodiment will be described based on a longitudinal sectional view in the vicinity of the oil storage chamber of FIG. 21 (enlarged view of the S part in FIG. 1). Since the upper flow path port 18b of the bearing support plate 18 is provided in the gas cover 88 except for the short-circuit opening 88e provided at the corresponding position of the base plate 88c, the other parts are the same. The description of the structure, operation, and effect is omitted. Since the upper flow path opening 18b is opened inside the gas cover, the gas passing therethrough collides with the annular cover 88d. Accordingly, the gas undergoes a large speed change, and a large inertial force acts on the oil droplets contained therein, so that the oil adheres to the inner wall of the annular cover 88d. As a result, the gas that has passed through the upper flow path port 18b from which the oil droplets have not been removed is removed here, so that the gas having a significantly reduced oil content can be discharged from the compressor. There is. Further, an embodiment in which a wall surface porous body 88k, which is a porous body, is provided at a location where gas collides with the annular cover 88d is also conceivable. In this case, the attached oil is difficult to re-separate, the oil droplet capturing rate is improved, and the oil content in the gas is further reduced.

  Next, a ninth embodiment will be described with reference to an assembly perspective view of the gas cover in FIG. 22, a plan view of the gas cover from the oil storage chamber side in FIG. 23, and a perspective view of the oil droplet removing portion in FIG. A portion where the gas that has passed through the upper flow passage port 18b collides with the annular cover 88d becomes an inclined portion 88h, and the oil droplet removal portion 45 is moved to a position where the gas flow rises substantially vertically in the gas vent passage 88a. Since it is the same as that of the eighth embodiment except that it is provided and the structure of the oil droplet removing unit 45 is changed, the description of the structure, operation, and effects of other parts is omitted.

  When there is no inclined part, since the driving force for the oil attached near the center of the collision part to move is only gravity, it is very small and the oil droplets remain almost attached. Therefore, there is a risk that oil adhering to the subsequent gas collision may be re-separated. In this embodiment, the collision gas flow itself has the action of pushing the attached oil downward, so that the oil attached to the annular cover 88d does not re-separate into the gas, and the oil contained in the discharge gas is contained. There is an effect that the gas whose rate is greatly reduced can be discharged from the compressor. Further, since the gas flows almost in the center of the oil droplet removing unit 45, the gas does not flow through the gap around the oil droplet removing unit 45, and the oil content can be greatly reduced. In addition, since the oil drop removing portion was divided at two locations, the wire mesh 45a became smaller and the risk of dropping the wire forming it from the end increased, but in order to avoid this, the mesh presser 45c was used, The presser claws 45d are fixedly disposed on the laminated holding portion 45b. As a result, there is an effect that a compressor with improved reliability can be provided. Moreover, you may install a porous body in the channel | path opening part 88b. Thereby, there is an effect that the gas whose oil content is further reduced can be discharged from the compressor.

  Next, a tenth embodiment will be described based on the perspective view of the oil droplet removing unit in FIG. Since the oil droplet removing portion 45 is the same as the ninth embodiment except that a large number of small holes 45e are provided instead of laminating a wire mesh, the description of the structure, operation, and effects of other portions is omitted. Since the structure is simple, there is an effect that the processing cost can be reduced.

  Next, an eleventh embodiment will be described based on a longitudinal sectional view in the vicinity of the oil storage chamber of FIG. 26 (enlarged view of the S portion in FIG. 1). The gas that has passed through the upper flow path port 18b is the same as that of the sixth embodiment except that the oil droplet removing unit 45 is inclined so as to pass through the oil droplet removing unit 45. Description of operation and effect is omitted.

  The oil droplet removing unit 45 serves to remove oil droplets generated on the oil surface by bubbles rising in the stored oil 69 and to remove oil droplets in the gas that has passed through the upper flow path port 18b. Since it serves also, the gas which reduced the content rate of oil significantly can be implement | achieved by simple structure.

  Next, the twelfth embodiment will be described based on the assembly perspective view of the oil trap plate in FIG. 27, the perspective view of the oil trap plate in FIG. 28, and the longitudinal sectional view in the vicinity of the oil trap plate mounting portion in FIG. To do. Since the oil trap plate 47 is the same as that of the first to eleventh embodiments except that the oil trap plate 47 is disposed on the retainer 23a, description of the structure, operation, and effects of other parts is omitted. A plurality of meshes 47b are stacked and inserted into the mesh insertion portion 47e of the oil plate holder 47a, and the oil trap plate 47 is formed by bending the meshing ring 47c on the top and bending and fixing the retaining claws 47d. As shown in FIG. 28, the oil trap plate 47 is fixed to the upper portion of the retainer 23a by a two-stage bolt 23m and a bypass nut 23n. As a result, a gas containing a large amount of oil exiting from the compression operation port 2d collides with the oil trap plate 47. As described above, the oil adheres to the laminated net 47b due to its inertia. Therefore, there is an effect that the gas whose oil content is greatly reduced can be discharged from the compressor. Here, the distance H between the oil trap plate 47 and the compression operation port 2d is set within a range of 0.25 to 2 times the diameter D of the compression operation port 2d. As a result, there is an effect that the flow path resistance does not increase and the oil droplet removal rate in the gas is high. Here, in order to set this H, the thickness of the nut portion of the two-stage bolt 23m and the thickness of the retainer 23a are used. As a result, there is an effect that a jig or a separate part for securing H becomes unnecessary and the cost is reduced. Furthermore, when performing a leak check of the bypass valve 23, it is necessary to fix only the bypass valve plate 23x and the retainer 23a. In this case, only the two-stage bolts 23m can fix them, This has the effect of increasing mass productivity. Here, when the fineness of the mesh 47b is made fine on the side close to the bottom and the side close to the surface is made rough, the oil removal rate from the gas can be improved.

  Next, a thirteenth embodiment will be described based on the perspective view of the oil trap plate of FIG. The structure is the same as that of the twelfth embodiment except that the uneven portion 47g is provided instead of the net lamination, and the description of the structure, operation, and effects of other portions is omitted. Since the unevenness portion 47g increases the amount of oil attached, the oil removal rate from the gas can be improved.

  Next, a fourteenth embodiment will be described based on the perspective view of the oil trap plate of FIG. Since this embodiment is the same as the twelfth embodiment except that the net stack is not provided, the description of the structure, operation, and effects of other parts is omitted. Since the gas collides with the plate, the oil in the plate collides violently and adheres to the plate due to its inertia, so that the content of oil in the gas can be reduced. Since this has a very simple structure, there is an effect that a low-cost compressor can be realized.

  Next, a fifteenth embodiment will be described based on a plan view from the scroll wrap side of the fixed scroll member of FIG. Since the second differential pressure control valve 200 is provided in addition to the differential pressure control valve 100, the configuration is the same as that of the first to fourteenth embodiments. Is omitted. When the amount of oil or gas flowing through the differential pressure control valve 100 is large, there is an effect that it is possible to prevent the differential pressure set value from deviating. The differential pressure setting value of the second differential pressure control valve 200 may be larger than the setting value of the differential pressure control valve 100. In this case, it is possible to serve as a safety valve for escaping an abnormal increase in pressure when a large amount of gas or oil flows into the rear over-suction pressure region 99 at the time of start-up or a sudden change in the operating state. As a result, there is an effect that a highly reliable compressor can be provided.

  Next, a sixteenth embodiment will be described based on a plan view of the vicinity of the center from the scroll wrap side of the fixed scroll member of FIG. 33 and a longitudinal sectional view of the bypass hole of FIG. Except for providing a notch toward the center in the direction along the scroll wrap 2b on the tooth bottom side of the pair of bypass holes 2e on the high pressure side, it is the same as in the first to twelfth embodiments. The description of the structure, operation, and effect is omitted. Since the re-expansion due to the high-pressure gas remaining in the hole is suppressed as much as possible and the period of communication with the compression chamber of the high-pressure side bypass valve 23 is expanded to the high-pressure side, over-compression can be further reduced and the performance is improved.

  Next, a seventeenth embodiment will be described based on a plan view of the vicinity of the center of the fixed scroll member from the scroll wrap side in FIG. 35 and a longitudinal sectional view of the bypass hole in FIG. Except for providing a notch outwardly in the direction along the scroll wrap 2b on the tooth bottom side of the pair of bypass holes 2e on the high-pressure side, the structure and operation of other parts are the same as the thirteenth embodiment. The description of the effect is omitted. Since the period of communication with the compression chamber of the high-pressure side bypass valve 23 is expanded from the low-pressure side to the high-pressure side while suppressing re-expansion due to the high-pressure gas remaining in the hole as much as possible, the over-compression at a low pressure ratio can be further reduced. There is an effect of improving.

  Next, an eighteenth embodiment will be described based on a plan view of the vicinity of the center from the scroll wrap side of the fixed scroll member of FIG. Since it is the same as the fourteenth embodiment except that a notch is provided in the center and outward in the direction along the scroll wrap 2b on the tooth bottom side of the pair of bypass holes 2e on the low pressure side, The description of the structure, operation, and effect is omitted. The pair of bypass holes 2e on the low-pressure side also has a role of suppressing overcompression, but the main role is to avoid liquid compression. Since the period during which the low pressure side bypass valve 23 communicates with the compression chamber has expanded from the low pressure side to the high pressure side, liquid compression can be avoided more reliably and the reliability can be improved.

  Finally, the nineteenth embodiment will be described with reference to a longitudinal sectional view in the vicinity of the differential pressure control valve shown in FIG. 38 (enlarged view of portion P in FIG. 1). Since it is the same as the first to fifteenth embodiments except that the differential pressure valve spring 100c having a long natural length and the insertion valve cap 100j into which it can be inserted are provided, the description of the structure, operation, and effects of other parts is omitted. Thereby, since the spring constant can be set small, the differential pressure can be set without increasing the dimensional accuracy of each part, which has the effect of improving mass productivity. Here, the differential pressure valve spring 100c is a helical spring, but may be a bamboo shoot spring. In this case, since it is difficult to buckle, there is an effect that the differential pressure value can be set with higher accuracy.

  2 ... fixed scroll member (non-orbiting scroll member), 2e ... bypass hole, 3 ... orbiting scroll member, 4 ... frame, 5 ... Oldham ring, 6 ... compression chamber, 12 ... shaft, 19 ... motor, 44 ... Frame oil ring, 45 ... Oil drop removal section, 46 ... Oil ring, 47 ... Oil trap plate, 47 m ... Two-stage bolt, 60 ... Suction chamber, 61 ... Fixed back chamber, 62 ... Motor chamber, 69 ... Oil stored, 95 ... back discharge pressure region, 96 ... discharge chamber, 99 ... back oversuction pressure region, 100 ... differential pressure control valve.

Claims (4)

A fixed scroll member comprising an end plate and a scroll wrap standing on the end plate;
An orbiting scroll member comprising an end plate and a scroll wrap standing on the end plate, and meshed with the fixed scroll member;
A compression chamber formed by the revolving motion of the orbiting scroll member without rotating between the meshed scroll members;
A bypass hole that penetrates the end plate of the fixed scroll member and connects the compression chamber and a fixed back chamber serving as a discharge pressure;
A bypass valve that controls communication of the bypass hole and communicates the compression chamber and the fixed back chamber when the pressure of the compression chamber is higher than a discharge pressure;
In the scroll type compressor consisting of
A compressor having a notch provided only in a direction along the scroll wrap of the fixed scroll member on a fixed tooth bottom side that is an opening of the bypass hole on the compression chamber side. In claim 1,
Of the bypass holes, only the bypass hole provided on the high-pressure side is provided with the notch. In claim 2,
A compressor characterized in that the notch is provided only on the center-facing side. In any one of Claims 1 thru | or 3,
The compressor is characterized in that the shape of the notch is a shape whose depth decreases as the distance from the bypass hole increases.

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