JPH11247786A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the quantity of the oil flowed into a refrigerating cycle by forming a path by way of the oil in an oil reservoir portion, in a path from a compressing operational portion to a discharge port as an outlet to the outside of a compressor. SOLUTION: When a motor 19 is rotated and a revolving scroll member 3 is revolved through a shaft 12, the gas in a suction chamber 60 formed on an outer peripheral part of an area where both scroll laps 2b, 3b are engaged, is confined in a compression chamber 6 formed between both scroll members 2, 3 to be compressed, and then discharged into a fixed back chamber 61. The oil 69 stored at a lower part of a motor chamber 62 and the fixed back chamber 61 is pressed downward by the increase of the pressure of the compressed gas, to be flowed into an oil storing chamber 80 through a lower passage port 18a, and the oil face at the oil storing chamber 80 side is risen. The gas risen to the surface of the stored oil 69 in the oil, storing chamber 80 is passed through an oil-drops removing portion formed by a porous body, and then discharged to the outside of the compressor from a discharge port formed by a discharge pipe 55.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor and, more particularly, to a reduction in oil content in gas discharged from the compressor.

[0002]

2. Description of the Related Art Except in special cases, mechanical means are used to compress a gas. For this reason, oil is used to ensure the lubricity and sealability of each part in mechanical means, but this oil often mixes with the gas. However, in most applications of compressed gas, oil in the gas is often prohibited or avoided. For example, in the case of a refrigerant gas used in a refrigeration cycle, the oil contained therein deteriorates the performance of the heat exchange unit, so that the compressor of the refrigeration cycle needs to be contrived to minimize the amount of oil discharged together with the gas. .

Conventionally, as shown in a scroll compressor disclosed in Japanese Patent Application Laid-Open No. 6-348883, a metal net or a thin plate having a large number of holes is provided inside a closed vessel of a discharge pipe.
It had a configuration in which oil in the compressed gas was separated while passing therethrough.

[0004]

However, because of the structure in which a high-speed rotating body such as a motor rotor is arranged in the flow path of the compressed gas, the compressed gas containing oil collides with the high-speed rotating body. Oil droplets are torn and separated into multiple small oil droplets, resulting in less oil adhering to a metal net or a thin plate with many holes, making it impossible to reduce the amount of oil discharged from the compressor There was a problem. The reason will be described below.

[0005] An oil droplet has a gravitational force proportional to the mass and a viscous force approximately proportional to the product of the relative velocity with respect to the surrounding gas and the surface area of the oil droplet. However, gravitational force is small in normal cases compared to viscous force, and is ignored. The expression of the viscous force is as follows.

(Viscous force) ≒ A × (surface area of oil droplet) × (relative velocity with surrounding gas) (1) A is a proportional constant. Here, the value of A is very large. This means that if the oil droplet has any relative velocity with respect to the gas, a large viscous force acts, so that the oil droplet moves almost on the flow of the gas. However, in places where the gas flow speed changes rapidly, such as inside a metal net or a thin plate with many holes, the inertia of the oil droplets shifts from the original speed without riding the gas flow. The action that tries to continue works. At this time, from the viewpoint of moving with the flow of gas, this action can be regarded as inertial force. Since this inertial force is proportional to the mass, which is the inertia of the oil droplet, it is expressed by the following equation.

(Inertial force) = B × (mass of oil droplet) × (acceleration of gas) (2) Since the oil droplet has a substantially spherical shape due to surface tension, (mass of oil droplet) ∝ (oil) (Drop diameter) ³ (3) (Surface area of oil drop) ∝ (Diameter of oil drop) ² (4) Therefore, when the relational expressions of (3) and (4) are substituted into (1) and (2), the following is obtained.

(Viscous force) ∝A × (Diameter of oil droplet) ² × (Relative speed with surrounding gas) (5) (Inertial force) ∝B × (Diameter of oil droplet) ³ × (Acceleration of gas) (6) As shown in (6), an inertial force acts on the oil droplet.
By dividing both sides of (5) and (6), the following equation is obtained.

(Inertial force) / (Viscous force) ∝ (Diameter of oil droplet) × (B × Gas acceleration) / (A × Relative velocity with surrounding gas) (7) Relative velocity with surrounding gas The containing term, as described above,
Since A is large and does not change much, it is almost independent of the size of the oil droplet. In addition, since the acceleration of the gas is determined by external conditions such as the shape of the gas flow path and the velocity of the gas,
This is also almost independent of the size of the oil droplet. Therefore,
(7) shows that as the diameter of the oil droplet increases, the inertial force approaches or increases with respect to the viscous force. This means that when the oil droplets become large, the gas flow tends to change suddenly where the gas flow suddenly changes. In other words, where the flow changes in a complicated manner, such as inside a net or porous body, the oil droplets become larger,
The oil droplets deviate from the gas flow and come into contact with the net or the porous body to be easily adsorbed, indicating that the oil content in the gas is reduced. In other words, conversely, the smaller the oil particle size, the lower the oil content reduction effect of the net or porous body.

Therefore, in order to adsorb a large amount of oil having a small particle diameter, the mesh of the metal mesh is made fine or the number of holes formed in the thin plate is made small to further change the gas flow flowing therethrough. Means for increasing the temperature are conceivable, but a problem arises in that the flow path resistance of the gas is increased by these means and the performance is reduced.

Further, in another scroll compressor disclosed in the above publication, a metal net or a thin plate having a large number of holes is provided so as to cover the compression operation port, and the compressed gas is contained in the compressed gas while passing therethrough. It had a configuration to separate oil. However, under the operating conditions where a large amount of refrigerant gas is dissolved in the oil and the surface tension of the oil is reduced, or when the compressed gas in the compression operation port is rapidly reduced in pressure, the gas dissolved in the oil contained therein explosively explodes. Under the operating condition such as the over-compression condition in which the gas evaporates, the particle size of the oil in the compressed gas becomes small similarly to the above-described example, and thus the same problem occurs.

An object of the present invention is to provide a compressor that reduces the amount of oil flowing into a refrigeration cycle.

[0013]

SUMMARY OF THE INVENTION The object of the present invention is to provide a compressor having a compression operation section provided in an airtight container for compressing a gas introduced from the outside and an oil reservoir provided in the container. This is achieved by providing a path from the compression operation section to a discharge port which is an outlet of the gas to the outside of the compressor, the path passing through the oil in the oil reservoir. Also, a path may be provided after the oil reservoir in the oil through the porous body.

The above object is also provided with a compression operation section provided in the closed container for compressing a gas introduced from the outside, and an oil reservoir provided in the closed container, wherein the gas from the compression operation section is provided. Is discharged into the closed container, and the gas from the compressing portion is discharged from the compressing portion into the closed container through a distance of 0.25 to 2 times the equivalent diameter of the compressing port. This is achieved by disposing the oil trap plate at a remote position. here,
The above-mentioned equivalent diameter is the diameter of a circle having the same area as the cross-sectional area of the compression operation port.

[0015] The above object is also provided with a compression mechanism section and an electric motor section for driving the compression mechanism section in a closed container, and the refrigerant discharged from the compression mechanism section is externally discharged from a discharge port through the closed container. In the compressor discharged to the motor, a discharge pipe is provided on the opposite side of the compression mechanism with respect to the electric motor, an auxiliary bearing provided between the electric motor and the discharge pipe, and an auxiliary bearing provided on the auxiliary bearing. This can be achieved by providing a support plate having holes, and a shielding plate between the support plate and the discharge port.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Before describing the embodiments, 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 passing a gas containing oil through the storage oil, it is necessary to blow the gas into the lower part of the storage oil due to a difference in specific gravity between the gas and the liquid. The blown gas rises as bubbles in the storage oil. Since the entire area around the bubbles is oil, the probability of the oil droplets in the bubbles coming into contact with the surrounding oil is very high. Further, the rise of bubbles in the stored oil is very small compared to the gas flow velocity in other parts of the compressor due to the viscosity of the oil, so that the oil droplets in the bubbles come into contact with the surrounding oil. The time that can be done is long,
The probability of the oil droplets in the bubbles coming into contact with the surrounding oil is higher. The oil droplets in contact with the surrounding oil have the effect of reducing 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 an oil-containing gas is passed through the storage oil, the oil content of the gas coming out of the oil decreases. Since this oil content reduction action does not depend on the size of oil droplets in bubbles, it was difficult to remove not only oil droplets having a large particle diameter but also nets and porous bodies raised in the prior art. Oil droplets having a small particle size can also be effectively removed.
By the way, depending on the operating conditions, when the gas bubbles reach the oil level of the storage oil, the gas 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 almost only large oil droplets. If this gas is made to pass through the porous body next, the large oil droplets have a high probability for the above-mentioned reason. Can be removed. As a result, the gas whose oil content is significantly reduced 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 arranged so as to obstruct the flow path of the gas coming out of the compression operation port, the gas flow is sharply bent there, but the oil contained in the gas has a large inertia, so this oil trap plate It adheres and reduces the content of oil droplets in the gas. However, when the oil trap plate is too close to the compression operation port, the cross-sectional area of the flow passage is reduced and the flow passage resistance is increased, so that the performance is reduced. That is, (area of the compression operation port) ≦ (cross-sectional area of the gas flow path after exiting the compression operation port) (8) is required. The gas flow after exiting the compression port is
The oil trap plate is considered to be bent at a right angle, and the cross-sectional area of the gas flow path after exiting from the compression operation port is changed to the circumference of the compression operation port by the oil trap from the compression operation port on the outer surface of the compression operation section. Area multiplied by the distance to the plate,
That is, it can be regarded as the area of the side surface of the columnar three-dimensional figure having the height up to the oil trap plate having the compression operation port as the bottom surface. Usually, since the compression operation port has a circular shape or a shape close thereto, the situation hardly changes even if the compression operation port is a circle having the same sectional area. Thus, out of the equivalent diameter previously defined from D, the and the distance from the compression operation port until the oil trap plate and H, (area of the compression operation ^{opening) = π × D 2/4} (9) ( compression operation port than the flow path cross-sectional area) = π × D × H ( 10) of the gas after the condition (8) is a ^{π × D 2/4 ≦ π} × D × H (11). This can be summarized as follows.

H ≧ D / 4 (12) On the other hand, if H is too large, the speed at which the gas collides with the oil trap plate decreases, and the rate of removing oil droplets from the gas decreases. From the previous studies, it has been found that when the value of D is twice or more, the oil droplet removal rate sharply decreases.

H ≦ 2 × D (13) From (12) and (13), if the oil trap plate is disposed at a position which is twice as long as 0.25 of the equivalent diameter of the compression operation port, In addition, the performance does not decrease due to the flow path resistance, and the removal rate of oil droplets in the gas increases.

According to the present invention, the orbiting scroll member is fixed to the fixed scroll member by applying a pressure higher than the suction pressure to the space of the orbiting scroll member on the side opposite to the compression chamber by a substantially higher value than the suction pressure. A first embodiment of the present invention applied to a pressing scroll compressor 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 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 near the bypass valve (an enlarged view of a portion R in FIG. 1), and FIG. 7 is a longitudinal sectional view near the differential pressure control valve (an enlarged view of a portion P in FIG. 1). 8 is a longitudinal sectional view of the differential pressure control valve in the vicinity of the back pressure chamber (an enlarged view of a portion Q in FIG. 7), FIG. 9 is a longitudinal sectional view of the vicinity of the oil storage chamber (an enlarged view of the S portion in FIG. 1), FIG. 10 is a perspective view of the oil droplet removing unit, and FIG. 11 is a plan view of the bearing support plate from the motor chamber side. In this example,
The diameter of the compressor is about 10 mm to 1000 mm.

First, the structure will be described. The orbiting scroll member 3 is provided with a scroll wrap 3b standing upright on an end plate 3a having an involute or an algebraic screw thread as a basic line, and a bearing holding portion 3s having a swivel bearing 3w inserted on the back thereof, and orbital Oldham grooves 3g and 3h. Is provided.

The fixed scroll member 2 has a scroll wrap 2b erected on a mirror plate 2a and a non-turn reference surface 2u which is substantially flush with the scroll wrap tooth tip surface as shown in FIG. The groove 2c is formed. And
Four bypass holes 2e are provided in the tooth bottom. Here, the reason why four bypass holes 2e are provided is as shown in FIG.
This is because the bypass holes 2e are always opened in all the compression chambers 6 to be formed. A bypass valve plate 23x (FIG. 2), which is a reed valve plate, and a retainer 23a for limiting the degree of opening of the valve plate 23x are fixed by 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 digging 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 surface is provided therein. The suction pipe 54 is inserted into the suction hole 2v. At this time, the valve element 24a and the check valve spring 24c are inserted.
The suction side check valve 24 is formed. Further, a plurality of flow grooves 2 for flowing gas and oil around the outer periphery of the fixed scroll member 2.
r is provided. One of them has a motor wire 19
Pass n. A back side conduction path 2β and a valve hole 2 are formed in the peripheral groove 2c.
Open f (FIG. 7) and provide a valve seal surface or valve seal line 2j. Then, a suction-side conduction path 2α is provided to connect a side surface of the valve hole 2f and a communication groove 2δ communicating with the suction chamber 60. FIG.
As shown in FIG. 2, a plate-shaped valve body 100a and a differential pressure valve spring 100c are inserted into the valve hole 2f, and the valve cap 100f is removed from the valve hole 2f with one end of the differential pressure valve spring 100c inserted into a spring positioning projection 100h. Is press-fitted into the valve cap insertion portion 2k having a large diameter to form the differential pressure control valve 100. 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 an over-suction pressure value, the depth of the valve hole 2f and the cap insertion portion 2k which are dimensions for determining the over-suction pressure value are determined.
And the thickness of the valve body 100a and the differential pressure valve spring 10
The spring constant and natural length of 0c must be managed with high precision. In particular, it is necessary to finish the end of the differential pressure valve spring 100c on a plane substantially perpendicular to the center 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 separates from the fixed scroll member 2 and normal operation becomes impossible. In addition, the valve cap 100
f is smaller than the diameter of the valve cap insertion portion 2k, and the valve cap 10
There is also a method of expanding and stopping 0f. The pressing force at this time is
A rod is inserted into the back-side conductive path 2β and the valve body 100a
To one end and detect the force applied to the rod. In the case of this method, there is no need to precisely control the dimensions and the values of the spring constants of the above-described respective parts, so that there is an effect that the mass productivity is improved. In both of these two methods, upon completion of assembly, the space between 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). And this spring is higher than the pressure in a certain space). Adhesion or welding may be performed to complete the seal. Here, the spring positioning protrusion 100h may have a tapered shape in which the diameter at the tip is smaller than the root. In this case, since the end of the differential pressure valve spring 100c is fixed only at the base of the spring positioning projection 100h, the movable portion of the spring is fixed to the positioning projection 100h.
And the natural length of the spring is maintained as it is when the spring is alone. Therefore, there is a unique effect that an error from the set value of the excessive suction pressure value can be suppressed.

The frame 4 has a fixed mounting surface 4b for mounting the fixed scroll member 2 on an outer peripheral portion thereof, and a revolving insertion surface 4d provided inside the fixed mounting surface 4b.
Is provided with one or a plurality of pinching surface grooves 4α. Further inside, in order to arrange the Oldham ring 5 between the frame 4 and the orbiting scroll member 3, frame Oldham grooves 4e, 4f (both not shown) are provided.
Further, a shaft seal 4a and a main bearing 4m are provided in 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. One of them passes through 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 projections 5a and 5b (both not shown) on one surface and revolving projections 5c and 5d on the other surface.

As shown in FIG. 1, the shaft 12 has a shaft oil supply hole 12a, a main bearing oil supply hole 12b, a shaft seal oil supply hole 12c, and an auxiliary bearing oil supply hole 12i. In addition, a balance holding part 1 having an enlarged diameter is provided on the upper part thereof.
The shaft balance 49 is press-fitted therein. Further, an eccentric portion 12f is provided.

The rotor 15 has an unmagnetized permanent magnet 15b built in a laminated steel plate 15a, and a rotor balance 15 at both ends.
c, 15p are provided.

The stator 16 has a plurality of stator grooves 16c serving as flow paths for compressible gas and oil on the outer peripheral portion of the laminated steel plate 16a.
And a coil through hole 16v is opened inside. Here, the coil 16w passes therethrough, and the sub-bearing-side coil end portion 16x and the main bearing-side coil end portion 1 which are the folded portions of the coil are provided.
6y 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 in the laminated steel plate 16b. This is because if the stator hole 16m is provided inside 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 on 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 inserted into the frame Oldham grooves 4f and 4e.
Frame projections 5a, 5b (both not shown) are inserted and mounted on the frame 4. Further, the revolving scroll member 3 is inserted into the revolving Oldham grooves 3g, 3h with the revolving protrusions 5c, 5d of the Oldham ring 5,
The eccentric portion 12f of the shaft 12 is inserted into the slewing bearing 3w while being mounted on the slewing surface 4d. The fixed scroll member 2 is engaged with the orbiting scroll member 3, and the fixed scroll member 2 is fixed to the frame 4 by the wrap fixing screw 53 at a position where the rotating torque is minimized or becomes a certain reference value or less while rotating the shaft 12. Is fixed. According to this method, it does not deviate greatly from the optimum position, but it is difficult to fix it to 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 smaller than the distance between the orbiting insertion surface 4d and the non-orbiting reference surface 2u by about 5 to 20 μm, and the orbiting scroll member 3 and the fixed scroll member are set. 2 defines the maximum separation distance in the axial direction. Therefore, the fixed scroll member 2 can be attached to the frame 4 with higher accuracy by using the following method. As shown in FIGS.
Positioning hole 2p with high positional accuracy and dimensional accuracy
And two similarly high-precision positioning holes (not shown) are provided at the corresponding frame positions. A positioning pin is press-fitted into the hole on the frame side while protruding toward the fixed mounting surface 4b. The positioning holes 2p are inserted into the positioning pins, 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 reduced if the component is not processed with high accuracy. Therefore, this is an effective method only when components can be maintained with high accuracy. Conversely, the assembly method described earlier
Even when the component accuracy is not so high, a method of high mass productivity can be said because a certain level of assembly accuracy can be ensured. At this time, a back surface excessive suction pressure region 99 is formed on the back surface of the orbiting scroll member 3. Next, a cylindrical casing in which the stator 16 is previously shrink-fitted or press-fitted or adhered, and a bearing support plate 18 having a central hole 18c at the center and a lower flow passage hole 18a at the lower portion and having an oil ring welded thereto is welded or press-fitted. At 31, the above assembly 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 passage opening 18a is lower than the lowest point of the central hole (the inner diameter height of the stator in the figure) of the stator 16 into which the rotor is inserted. Set. Further, bonding may be performed instead of tack welding. At this time, the assembly part by welding and the cylindrical casing 3
Since the deformation of No. 1 is eliminated, the performance is improved. This allows
A motor 19 is provided 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 assembled so that one end of the shaft 12 protruding from the central hole 18c of the bearing support plate 18 is inserted into a cylindrical hole of the spherical bearing 72 mounted on the bearing housing 70. The position of the bearing housing 70 is adjusted while detecting the rotation torque, and the bearing housing 70 is spot-welded to the bearing support plate 18 at a position where the rotation torque is minimized or becomes equal to or less than a reference value. Then, after inserting the oil supply cap 90 to which the bent oil supply pipe 71 is welded into the bearing housing 70, spot welding is performed on the bearing housing 70 with the 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. Thus, no seal is required, and the number of parts is reduced. Thereafter, a magnet 89 is provided near the tip of the oil supply pipe 71. On the other hand, a plurality of wire nets 45a are laminated by the lamination holding part 45b to form the oil droplet removing part 45 which becomes a porous body, and this is fixed to the bottom casing 21 by the mounting part 45f. A discharge pipe 55 is welded to an 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 drop removing unit 45 and the bearing support plate 18. Next, the upper casing 20 in which the hermetic terminal 22 and the suction pipe mounting pipe 37 are welded to the upper part of the cylindrical casing 31 is welded by attaching the motor wire 19n to the inner side terminal of the hermetic terminal 22, and welding the suction pipe. 54 is inserted into the suction pipe attachment pipe 37 and the gap is brazed to form a fixed rear chamber 61. In this state, the stator 16
And a permanent magnet 15b inside the rotor 15 is magnetized to form a motor 19. Then add the oil.
In the lower part of the frame 4 and the fixed scroll member 2 that partition between the fixed rear chamber 61 and the motor chamber 62,
The existence of the flow grooves 4h and 2r and the lower flow port 18 in the lower portion of the motor chamber 62 and the oil storage chamber 80
Due to the presence of a, the storage oil 69 accumulates in the lower part of the fixed rear chamber 61, the motor chamber 62, and the oil storage chamber 80a. Therefore, these three chambers have a role of an oil storage room.

Next, the operation will be described. First, the operation immediately after starting the compressor will be described. ◆ By starting rotation of the motor 19, the shaft 12 rotates and the orbiting scroll member 3 starts to orbit. Here, the turning radius of the orbiting scroll member 3 is set to be smaller than a size geometrically determined from the scroll wrap shape. This is because the shape of the scroll wraps 2b and 3b always has a processing error, and if not set small, the side surfaces of the wrap will come into pressure contact with each other, increasing friction loss and advancing wear, and in the worst case, the side surfaces will be pressed. This is because galling may cause adhesion or the wrap may be broken, resulting in inoperability. Here, the existence of the Oldham ring 5 prevents the orbiting scroll member 3 from rotating. By this operation, the gas in the suction chamber 60 formed on the outer peripheral portion of the region 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 two scroll members, and the compression operation is performed. Discharge starts from the mouth 2d into the fixed rear chamber 61. By the way, as shown in FIG. 7, the thickness of the end plate 3a of the orbiting scroll member 3 is set to be smaller than the interval between the orbital insertion surface 4d and the non-orbiting reference surface 2u by about 5 to 70 μm. 3 defines the maximum separation distance between the fixed scroll member 2 and the fixed scroll member 2 in the axial direction. For this reason, immediately after the start of the compressor, the orbiting scroll member 3 is connected to the compression chamber 6.
It is separated from the fixed scroll member 2 by the separating force by the gas inside, and moves to the frame 4 by the distance described above. Therefore, the opposite lap side of the end plate 3a slides on the turning sandwiching surface 4d, and a gap is formed between the lap side of the end plate 3a and the non-turn reference surface 2u by the maximum separation distance described above. At the same time, the gap between the tip of the lap and the root of the lap becomes almost the same, so that internal leakage is large and high-efficiency operation cannot be performed. However, if the maximum separation distance is about 5 to 70 μm, the motor rotation speed is increased immediately after startup. By increasing the pressure to about the maximum allowable value, internal leakage can be suppressed, and the suction pressure or the discharge pressure can be sufficiently increased. The gas discharged from the compression operation port 2d to the fixed rear chamber 61 is supplied to the fixed scroll member 2 and the frame 4
Flows into the space between the motor 19 and the frame 4 in the motor chamber 62 through the flow grooves 2r and 4h on the outer circumference of the motor chamber 62. The gas further flows into the stator groove 16c.
Or through the gap between the rotor 15 and the stator 16 to reach the bearing support plate 18 side of the motor chamber 62. The compressed gas that has spread so far loses its place to go, and starts to accumulate and the pressure increases. This pressure increase is caused by the motor chamber 62 and the fixed rear chamber 61.
Press the storage oil 69 accumulated in the lower part of the lower side of the lower side. As a result, the storage oil 69 flows into the oil storage chamber 80 through the lower passage opening 18a, and raises the oil level on the oil storage chamber side.
And, the oil level of the motor chamber 62 is
When it reaches the height of the highest point a, 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 as a bubble in the inside. Here, since the height of the highest point of the lower passage opening 18a is set lower than the lowest point of the central hole where the rotor of the stator 16 is inserted, the oil level of the motor chamber 62 is 15, the rotor 15 which rotates the stored oil 69 at high speed does not stir and forms fine oil droplets, so that the oil content of the gas can be reduced. By the way, if the set height of the lower passage opening 18a is determined so that the height of the oil level on the motor chamber 62 side is not so high that the rotor 15 can be barely bound, the oil flow due to the rotation of the rotor Oil droplets are generated from the surface, and the content of oil droplets in the gas does not decrease so much. Therefore, it is preferable that the oil level on the motor chamber 62 side is lowered to at least 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 in 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 this embodiment that a 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 unit 45 formed of a porous body, and is then discharged from the discharge port formed by the discharge pipe 55 to the outside of the compressor. You. Immediately after the compressor is started, the pressure in the rear excessive suction pressure region 99 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-swirl reference surface 2u as described above. Pressure. The oil in the oil storage chamber 80 enters the oil supply cap 90 from the oil supply pipe 71 due to a pressure difference between the pressure in the rear excessive suction pressure area 99 and the oil storage chamber 80 which is almost the same as the discharge pressure, where capillary action and the like occur. It is supplied to the spherical bearing portion of the spherical bearing 72 by centrifugal force.
Further, the bearing enters the shaft oil supply hole 12a, which has almost no flow path resistance because of its large cross-sectional area, and a part of the bearing is located on the center hole side of the spherical bearing 72 through the auxiliary bearing oil supply hole 12i when a centrifugal force is applied. And the other part is similarly subjected to centrifugal force to produce the shaft seal lubrication hole 12c.
And the other part is supplied to the main bearing 4m through the main bearing oil supply hole 12b by centrifugal force, and the remaining part reaches the center of the back surface of the orbiting scroll member 3. It is supplied to the slewing bearing 3w by the same differential pressure and centrifugal force as described above. As a result, a back discharge pressure region 95 for applying a discharge pressure is formed at the center of the back surface of the orbiting scroll member 3. The main bearing 4m and the slewing bearing 3
The oil supplied to w enters the rear over-suction pressure region 99 after the temperature rises due to the friction there. At this time, since the average pressure of the oil in the bearing portion is higher than the pressure in the rear over-suction pressure region 99 and closer to the pressure in the oil storage chamber 80, the oil is blown out to the back over-suction pressure region 99. As a result, the solubility of the gas component of the oil decreases due to the temperature rise and the sharp decrease in the pressure due to the friction of the bearing portion, and the gas component dissolved in the oil evaporates at a stretch. At this time, it takes away heat of vaporization from the surroundings,
The main bearing 4m
There is a specific effect that the reliability of the slewing bearing 3w is improved. Further, the vaporization of the gas component turns the oil into fine oil droplets, which makes it easy to move along with the flow of the gas. As will be described later, after this, the gas flows toward the orbiting scroll member 3, so that the oil also flows in that direction.
Since the Oldham ring 5 is located on the path from the main bearing 4m and the orbiting bearing 3w 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 rear over-suction pressure region 99 sharply increases immediately after the compressor is started. As shown in FIG. 7, this gas flows into the suction chamber 60 together with the oil through the sandwiching surface groove 4α and the gap between the lap side of the end plate 3a and the non-swirl reference surface 2u. Then, the oil therein flows into the compression chamber 6 having a slight gap in the axial direction, and has the effect of improving the sealing performance there, reducing the internal leakage of the compression chamber, and promoting the rise of the discharge pressure. Thereafter, the gas exits the fixed rear chamber 61 through the compression operation port 2d together with the gas. Also,
Since the gap between the lap side of the end plate 3a and the non-swirl reference surface 2u is small and the amount of oil in the flowing fluid is large and partially forms a seal portion, the amount of gas and oil flowing into the back excessive suction pressure area 99 In this case, the amount of gas and oil flowing out is small, and the pressure in the rear over-suction pressure region 99 sharply increases. As a result, together with the contribution of the pressure increase in the back discharge pressure region 95 due to the increase of the discharge pressure, the attraction force, which is the force pressing the orbiting scroll member 3 against the fixed scroll member 2, sharply increases. Almost immediately after the activation or in a very short time, the magnitude of the attracting force becomes greater than the magnitude of the separating force, and the orbiting scroll member 3 is pressed against the fixed scroll member 2. As a result, the gap between the tooth tip and the tooth bottom of the scroll wrap is reduced, so that the hermeticity of the compression chamber 6 is improved, and the amount of internal leakage of gas during compression is reduced. The performance is dramatically improved, and the vehicle shifts to the normal operating state. By the way, the scroll member 2, which becomes a sealing surface when forming the compression chamber 6,
When a surface film having conformability that can be scraped off when pressed and slid on the surface of No. 3 is formed, there is almost no gap between the tooth tip and the root of the scroll wrap when the scroll members 2 and 3 are pressed. The hermeticity of the compression chamber 6 is further improved, the amount of internal leakage of gas during compression is further reduced, the performance is dramatically improved compared to immediately after startup, and the operation shifts to a normal operation state. Even if this conformable film is provided on only one of the scroll members, it is effective.

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

Except that not all of the gas and oil flowing into the rear over-suction pressure region 99 do not directly flow into the suction chamber 60, the operation is the same as that immediately after the start of the compressor. This will be mainly described. The gas and oil flowing into the rear excessive suction pressure area 99 pass through the scissor surface groove 4α and the gap between the anti-lap surface of the end plate 3a and the swivel sandwiching surface 4d, and the side surface of the end plate 3a and the frame 4 Into the turning side area 67, which is the space between the two. Some of the suction chambers 60 lubricate the sliding surfaces of the lap side of the end plate 3a and the non-swirl reference surface 2u.
Flows into. Since the flow resistance between the turning side surface area 67 and the back excessive suction pressure area 99 is small, the pressure in the turning side area 67 is substantially equal to the pressure in the back excessive suction pressure area 99. As can be seen from FIG. 8, since the peripheral groove 2c always communicates with the turning side surface area 67, the peripheral groove 2c
c becomes the pressure in the back-side excessive suction pressure region 99 and passes through the back-side conduction path 2β to the differential pressure control valve 1.
The pressure of the back side excessive suction pressure region 99 is applied to the surface of the valve body 100a on the frame side of the valve body 100a. 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 rear excessive suction pressure area 99 is smaller than the suction pressure by the pressure difference. Pressure valve spring 1
When the pressure becomes higher than the excessive suction pressure value which is a constant value corresponding to the pressing force of 00c, the valve body 100a
Move to 0c side. As a result, except for the gas and oil in the revolving side surface area 67 that have flowed into the suction chamber 60 via the sliding surface, the back side conduction path 2β, the valve body 100c and the valve seal surface Alternatively, the gas flows into the suction chamber 60 sequentially through the gap between the valve seal wires 2j, the side surface of the valve body 100c, the valve hole 2f, and the suction-side conduction path 2α. Then, it is transferred to the center of the wrap while being mixed with the gas in the compression chamber 6 to improve the sealing property of the compression chamber 6, and is discharged from the compression operation port 2d. As a result, the compression operation port 2
The compressed gas discharged from d contains the entire amount of oil supplied to the bearing. In this way, the pressure in the back excessive suction pressure area 99 is higher than the suction pressure in the differential pressure valve spring 10.
The pressure is controlled to be higher by a fixed value corresponding to the pressing force of 0c. That is, the pressure in the excessive suction pressure region 99 is roughly controlled as follows.

Assuming that A (excess suction pressure value) is a certain constant, (pressure of the rear excess suction pressure region 99) ≒ (suction pressure + A) Thus, the orbiting scroll member 3 is fixed to the fixed scroll member 2 in the entire required operating range. And the urging force obtained by subtracting the attraction force from the attraction force in a wide range of operating conditions is reduced, so that a high-performance compressor with small sliding loss can be realized. By the way, the gas passing through the back over-suction pressure region 99 is a flow that short-circuits from the discharge system to the intermediate pressure chamber 68 in the middle of compression in the compressor. 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 channel 102, the flow rate is very small, and the performance of the compressor does not decrease.

Here, since the gas discharged from the compression operation port 2d contains all the oil supplied to the slewing bearing 3w and the main bearing 4m as described above, for example, the discharge pressure and the rear excessive suction pressure The greater the difference in pressure in the region 99, the greater the amount of oil in the compressed gas exiting from the compression operation port 2d. In addition, as the rotational speed of the orbiting scroll member 3 decreases, the amount of the compressed gas per unit time decreases, but the amount of oil supplied to the bearing is the same. 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. By this flow, the main flow of the gas that has passed through the laminated steel plate 16a of the stator 16 is changed to the sub-bearing side coil end portion 16x
As a result, it does not go to the rotor 15 side but goes out toward the bearing support plate 18. Then, the flow goes to the lower flow passage port 18 a below, but this flow does not approach the rotor 15 by the oil ring 46. By passing the gas through the stator 16, the coil 16w and the laminated steel plate 16a of the stator, which are at a high temperature, can be cooled, so that there is a specific effect that the 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, oil collides with the coil end portion due to the inertia of oil droplets and adheres to the coil end portion. Agglomerate and fall into the lower storage oil 69 or flow along a stationary part,
There is a specific effect that the oil content is reduced. Also,
Since the main flow of gas does not approach the rotor 15 rotating at high speed due to the coil end portions 16x and 16y and the oil ring 46, the number of oil droplets coming into contact with the rotor 15 is extremely small, and fine oil droplets are almost generated. Therefore, there is a specific effect that the efficiency of oil separation from gas by a porous body such as a coil end portion is improved. Although the oil content of the gas reaching the lower passage opening 18a has been considerably reduced by the means described above, the gas is blown from the lower passage opening 18a from below the storage oil 69 in the oil storage chamber 80. This has the effect of further reducing the oil content. This injected gas is stored oil 6
9 rises as bubbles. Since the entire area around the bubbles is oil, the probability of the oil droplets in the bubbles coming into contact with the surrounding oil is very high. Further, the rise of the bubbles in the storage oil 69 becomes very small compared to the gas flow velocity in other parts of 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 have the effect of reducing 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. The effect described above is obtained by such an operation. This oil content reduction effect does not depend on the size of the oil droplets in the air bubbles, and therefore, it is difficult to remove with the porous body raised in the prior art. . However, when the gas bubbles reach the oil surface of the storage 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, the gas coming out of the storage oil contains only large oil droplets. However, since this gas passes through the oil droplet removing unit 45 which is a porous body, large oil droplets are removed for the above-described reason. 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. Also,
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 comes to a position covering the bypass valve seal surface 2λ of each of the bypass holes 2e, and is fixed together with the retainer 23a with the bypass screw 23h to form 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 rear chamber 61 which is a part of the discharge system. Since the pressure of the fixed rear chamber 61 is the discharge pressure,
The bypass valve has an operation of communicating the compression chamber 6 with the discharge system when the pressure in the compression chamber 6 is higher than the discharge pressure. Actually, the timing at which the bypass valve 23 opens slightly shifts due to the pressure distribution on the bypass valve seal surface 2λ and the surface tension of the oil there.
In this way, the over-suction pressure region 99 is provided on the orbiting back surface and the bypass valve 23 is provided as the attraction force applying means for the orbiting scroll member 3, so that the over-suction pressure value can be set to a small value, and a wide operating range can be set. Can set the biasing force small. As a result, there is a specific effect that the total adiabatic efficiency and reliability can be increased in a wide operation 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 rear chamber 61, the pressure is extremely high regardless of the timing of the liquid compression. Before ascending, the bypass valve is opened and the fluid is discharged to the fixed rear chamber 61. As a result, there is a specific effect that the risk of damage to the wrap can be avoided and the reliability can be improved. In addition, overcompression can be suppressed even when the pump operation is extremely close to an extremely low pressure ratio, so that there is an effect that the overall adiabatic efficiency can be increased in a wide operating condition range on the low pressure ratio side.

At the time of starting the compressor, a system for performing an operation of restricting both or each of the piping system connected to the suction pipe 54 and the piping system connected to the discharge pipe 55 is provided to the operator or provided to the operator. By doing so, a reduction in suction pressure or an increase in discharge pressure can be realized more reliably. As a result, there is an effect that the normal operation of pressing the orbiting scroll member 3 against the fixed scroll member 2 can be shifted in a shorter time.

Next, a description will be given based on a second embodiment.
Except that the position of the highest point of the lower passage opening 18a of the bearing support plate 18 is set at the center, the structure is the same as that of the first embodiment, and the description of the structure, operation and effect of the other parts is omitted. In the first embodiment, since the upper side of the lower passage opening 18a is horizontal, the position where gas may blow out into the storage oil 69 is the entire upper side. For this reason, when bubbles start to form at a plurality of adjacent locations on the upper side of the lower flow path opening 18a, the bubbles coalesce during the bubble growth process.
It is assumed that the timing of the coalescence is such that the bubbles cannot be separated from the upper side of the lower flow passage opening 18a just by the bubbles alone. At this time, the size of the bubbles formed by merging becomes a size that cannot be formed by the bubbles formed by independent growth without merging. When the size of the bubbles is large, the ratio of the surface area to the volume of the bubbles is reduced, so that the probability of the oil droplets in the bubbles coming into contact with surrounding oil is reduced. Further, the rise of bubbles in the storage 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 decreases, so that the rising speed of the bubbles increases, and the time during which the oil droplets in the bubbles can come into contact with the surrounding oil decreases. 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 location where bubbles can be generated is determined at one location in the center of the upper side of the lower flow passage opening 18a, so that 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 reduced can be discharged from the compressor. In the first embodiment, the oil droplet removing unit 45 has a porous body only at the center as shown in FIGS. 9 and 10, so that the mounting posture of the compressor is the same as that of the cylindrical shaft of the compressor. When the oil is rotated to the center, bubbles rise at a position deviated from the center of the storage oil 69, and an oil droplet is generated at an oil surface portion deviated from the center. Therefore, the oil droplet does not pass through the porous body and is removed. There is a high possibility that it will pass by the part 45 and reach the discharge port. On the other hand, in the present embodiment, since the bubbles rise near the center of the storage oil 69, the problem of the first embodiment is eliminated. As a result, there is an effect that the gas whose oil content is further reduced can be discharged from the compressor.

Next, a third embodiment will be described with reference to a plan view of the bearing support plate shown in FIG. Except that the upper side of the lower passage opening 18a of the bearing support plate 18 is formed in a saw-tooth shape, the structure is similar to that of the first embodiment, and the description of the structure, operation, and effects of other parts is omitted.

In the present embodiment, air bubbles are formed at the upper part of the lower flow passage opening 18a where the serration is formed. As a result, coalescence of air bubbles, which is a problem in the first embodiment, does not occur, so that there is an effect that a gas in which the content of oil in the discharge gas is further reduced can be discharged from the compressor. But,
If the periodic interval of the saw teeth is set smaller than the diameter of the bubble that can grow on the upper side of the lower flow passage opening 18a, coalescence occurs. Therefore, the saw teeth must be formed at least longer intervals. In addition, when the bubbles rise in the storage oil 69, they do not rise straight because of the flow of the storage oil 69, so that the periodic interval of the sawtooth is lower than that of the lower flow path port 1.
8a is larger than the diameter of the bubble that can grow on the upper side of the storage oil 6a.
It is better to increase the left and right swing width by the flow of 9.
In addition, since the peaks on both sides are taken, bubbles rise near the center of the storage oil 69, and oil droplets are generated on the oil surface near the center. Pass through. As a result, there is an effect that the gas whose oil content is further reduced can be discharged from the compressor.

Next, a fourth embodiment will be described with reference to a longitudinal sectional view of the vicinity of the oil storage chamber in FIG. 14 (an enlarged view of a portion S in FIG. 1). Since the configuration is the same as that of the first to third embodiments except that the oil droplet removing unit 45 is inclined, the description of the structure, operation, and effects of other parts is omitted.

In the case of the first embodiment, for example, in which the oil droplet removing unit 45 has no inclination, the oil droplets adhering to the wire netting 45a accumulate to some extent and coalesce.
spread to b. Then, the oil adsorbed thereon accumulates again and coalesce, and a part of the oil spreads to the bottom casing 21 and returns to the storage oil 69 by gravity. As described above, since the time for which the oil droplets adhere to the oil droplet removing unit 45 is long, the oil droplets once captured may return to the gas again due to the flow of the gas passing therethrough. In this embodiment, since the oil droplet removing unit 45 is inclined, the oil droplets captured by the wire netting 45a are quickly moved by gravity to the bottom casing 2a.
It flows in one direction and flows down to the surface of the bottom casing 21 along the mounting portion of the oil droplet removing unit 45. Therefore, as described above, the oil droplets once captured do not return to the gas again, so that 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 section 45 is inclined toward the bottom casing 21 side.
It may be inclined to the bearing support plate 18 side. At this time, the oil droplet removing section 45 may be fixed to the bearing support plate 18.

Next, a fifth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion S in FIG. 1) near the oil storage chamber of FIG. 15, an assembled perspective view of the gas cover of FIG. 16, and an oil storage of the gas cover of FIG. Description will be given based on a plan view from the room side. Since it is the same as the first to fourth embodiments except that a gas cover 88 in which the oil droplet removing portion 45 is mounted on the bearing support plate 18 is provided, the description of the structure, operation, and effects of the other portions is omitted.

The gas cover 88 has the oil droplet removing portion 45 fixed inside the annular cover 88d, and is then brazed, adhered or welded to the base plate 88c to form a gas vent passage 88a inside. At this time, a central flange 88g and an outer peripheral nail 88f are provided to determine a fixing position. As a result, the flow path of the gas in the oil storage chamber 69 is the gas vent passage 88a in the gas cover 88, so that the risk of gas bubbles entering the oil supply pipe 71 is greatly reduced. As a result, when the gas stored in the motor chamber passes through the gas vent passage 88a from the lower flow port 18a, it then passes through the oil droplet removing unit 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 significantly reduced can be discharged from the compressor. In this embodiment, the oil droplet removing unit 45 is set to be horizontal.
If this is made oblique, 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 the oil droplets in the gas is further reduced by the collision with the bottom casing 21.

Next, a sixth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion S in FIG. 1) near the oil storage chamber of FIG. 18 and a plan view of the bearing support plate from the motor chamber side of FIG. explain. The fourth embodiment is the same as the fourth embodiment except that the upper flow passage port 18b is provided above the bearing support plate 18, and the description of the structure, operation, and effects of the other portions is omitted.

The upper passage opening 18b forms a passage from the motor chamber 62 to the gas area of the oil storage chamber 80. At this time, the pressure in the oil storage chamber 80 is slightly lower than the pressure in the motor chamber 62 by slightly applying the flow path resistance of the upper flow path port 18b, and the oil is stored in the oil storage chamber 80 by this pressure difference. I do. As a result, during operation at a very large flow rate, if there is no upper passage opening 18b, the bubbles in the oil when the bubbles in the oil come to the oil surface and are crushed become so vigorous that the oil droplet removal unit 45 cannot capture the oil. In this example, the amount of oil flowing out is small, but in this example, since the amount of gas passing through the oil is small, the generation of oil droplets due to bubbling on the oil surface is significantly reduced, and the oil content in the discharged gas is significantly reduced. There is an effect that the discharged gas can be discharged from the compressor. Here, as shown in FIG. 18, the number of the upper passage openings 18b is not limited to one at the center, but may be two or three.

Next, a seventh embodiment will be described with reference to a longitudinal sectional view of the vicinity of the oil storage chamber in FIG. 20 (an enlarged view of a portion S in FIG. 1). Since it is the same as the fifth embodiment except that the upper passage opening 18b is provided above the bearing support plate 18, the description of the structure, operation and effects of the other parts is omitted. The upper passage opening 18b forms a passage that passes from the motor chamber 62 to the gas area of the oil storage chamber 80. At this time, the pressure in the oil storage chamber 80 is slightly lower than the pressure in the motor chamber 62 by slightly applying the flow path resistance of the upper flow path port 18b, and the oil is stored in the oil storage chamber 80 by this pressure difference. I do. As a result, during operation at a very large flow rate, if the upper flow path port 18b is not provided, the bubbles in the oil when the bubbles in the oil come to the oil surface and are crushed become violent, and the oil droplet removing unit 4
In this example, the amount of oil passing through the oil is small, so that the generation of oil droplets due to foaming on the oil surface is greatly reduced, and the oil content in the discharged gas is low. This has the effect of allowing the gas to be discharged from the compressor with greatly reduced pressure.

Next, an eighth embodiment will be described with reference to a longitudinal sectional view near the oil storage chamber in FIG. 21 (an enlarged view of a portion S in FIG. 1). Since it is the same as the seventh embodiment except that a short-circuit opening 88e is provided at a position corresponding to the base plate 88c in order to provide the upper passage opening 18b of the bearing support plate 18 in the gas cover 88, the other parts The description of the structure, operation, and effects is omitted. Since the upper passage opening 18b is opened inside the gas cover, gas passing therethrough collides with the annular cover 88d. Therefore, the gas changes greatly in velocity, and a large inertial force acts on the oil droplets contained therein, and the oil adheres to the inner wall of the annular cover 88d. As a result, the upper passage opening 18b from which the oil droplets were not removed
Since the gas that has passed through is removed from the oil droplets here, there is an effect that the gas whose oil content is greatly reduced can be discharged from the compressor. Further, the gas is supplied to the annular cover 88d.
An embodiment is also conceivable in which a porous wall body 88k, which is a porous body, is provided at a location where it collides with the surface. In this case, there is a specific effect that the adhered oil is less likely to detach again, the trapping rate of oil droplets is improved, and the content of oil in the gas is further reduced.

Next, the ninth embodiment will be described with reference to the assembled perspective view of the gas cover in FIG. 22, the plan view of the gas cover from the oil storage chamber side in FIG. 23, and the perspective view of the oil droplet removing section in FIG. I do. The location where the gas that has passed through the upper passage opening 18b collides with the annular cover 88d becomes an inclined portion 88h, and the oil droplet removing 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 the eighth embodiment except that the arrangement and the structure of the oil droplet removing unit 45 are changed, the description of the structure, operation and effect of the other parts will be omitted.

In the case where there is no inclined portion, the driving force for moving the oil adhering near the center of the collision portion is only gravity, so that the driving force is very small, and the oil droplets remain almost adhered. Therefore, there is a danger that the oil adhering to the subsequent gas collision may be released again. In the present embodiment, the flow of the colliding gas itself has a function of flushing the adhering oil to the lower portion, so that the oil adhering to the annular cover 88d does not separate again into the gas, and the oil contained in the discharge gas contains the oil. There is an effect that the gas whose rate has been greatly reduced can be discharged from the compressor. Further, since the gas flows substantially at 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 droplet removing section is divided into two places, the wire mesh 45a becomes smaller, and the danger of the wire forming the wire dropping off from its end increases, but in order to avoid this, using the wire holder 45c, The holding part 45b is held by the holding claws 45d.
Fixedly arranged. As a result, there is an effect that a compressor with improved reliability can be provided. Further, a porous body may be provided in the passage opening 88b. As a result, there is an effect that the gas whose oil content is further greatly reduced can be discharged from the compressor.

Next, a tenth embodiment will be described with reference to a perspective view of an oil droplet removing unit shown in FIG. As the oil droplet removing unit 45,
Since it is the same as the ninth embodiment except that a number of small holes 45e are provided instead of laminating the wire mesh, the description of the structure, operation, and effects of the other parts 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 with reference to a longitudinal sectional view of the vicinity of the oil storage chamber in FIG. 26 (an enlarged view of a portion S in FIG. 1). Except that the gas that has passed through the upper flow path port 18b also inclines the oil droplet removing unit 45 so as to pass through the oil droplet removing unit 45, it is the same as the sixth embodiment, so the structure of the other parts and The description of the operation and the effect is omitted.

The oil droplet removing section 45 is provided with the storage oil 6
9 has a role of removing oil droplets generated on the oil surface due to bubbles rising in the inside and a role of removing oil droplets in the gas that has passed through the upper passage opening 18b. The reduced gas can be realized with a simple configuration.

Next, the twelfth embodiment is shown in an assembled perspective view of the oil trap plate of FIG. 27, a perspective view of the attachment of the oil trap plate of FIG. 28, and a longitudinal sectional view of the vicinity of the attachment portion of the oil trap plate of FIG. It will be described based on the following.
Since the oil trap plate 47 is the same as the first to eleventh embodiments except that the oil trap plate 47 is arranged so as to overlap the upper part of the retainer 23a, the description of the structure, operation, and effects of the 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 mesh holding ring 47c is placed on the upper portion, and the holding claws 47d are bent and fixed to form the oil trap plate 47. As shown in FIG. 28, the oil trap plate 47 is fixed to the upper portion of the retainer 23a by a two-step bolt 23m and a bypass nut 23n. As a result, the gas containing a large amount of oil coming out of the compression operation port 2d collides with the oil trap plate 47, and 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 oil trap plate 47 and the compression operation port 2d
Is set in the 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 removal rate of oil droplets in the gas is high.
Here, in order to set this H, the thickness of the nut portion of the two-step bolt 23m and the thickness of the retainer 23a are used. As a result, there is no need for a jig or another component for securing H, and there is an effect that the cost is reduced. Furthermore, when checking for leakage of the bypass valve 23, it is necessary to fix only the bypass valve plate 23x and the retainer 23a. In this case, since only the two-stage bolt 23m can fix them, This has the effect of increasing mass productivity. Here, if the mesh of the net 47b is made finer on the side near the bottom and rougher on the side near the surface, the removal rate of oil from the gas can be improved.

Next, a thirteenth embodiment will be described with reference to a perspective view of an oil trap plate shown in FIG. Since it is the same as the twelfth embodiment except that the uneven portion 47g is provided instead of the lamination of the net, the description of the structure, operation and effect of the other portions is omitted. Since the amount of oil adhesion increases due to the uneven portion 47g, the removal rate of oil from gas can be improved.

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

Next, a fifteenth embodiment will be described with reference to a plan view of the fixed scroll member from the scroll wrap side in FIG. Except that another 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. The differential pressure control valve 100
When the amount of oil or gas flowing through the air is large, there is an effect that the set value of the differential pressure can be prevented from shifting. Further, the set value of the differential pressure of the second differential pressure control valve 200 may be larger than the set value of the differential pressure control valve 100. In this case, at the time of start-up or a sudden change in the operating state, a role of a safety valve for releasing an abnormal increase in pressure there when a large amount of gas or oil flows into the rear excessive suction pressure region 99 can be provided. As a result, there is an effect that a highly reliable compressor can be provided.

Next, a sixteenth embodiment will be described with reference to a plan view near the center of the fixed scroll member from the scroll wrap side in FIG. 33 and a longitudinal sectional view of the bypass hole in FIG. Except that a cutout is provided on the tooth bottom side of the pair of high pressure side bypass holes 2e in the direction along the scroll wrap 2b toward the center, the same as in the first to twelfth embodiments, The description of the structure, operation, and effects 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 extended to the high-pressure side, overcompression can be further reduced and the performance is improved.

Next, a seventeenth embodiment will be described with reference to a plan view near 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 that a notch is provided outward in the direction along the scroll wrap 2b on the tooth bottom side of the pair of high pressure side bypass holes 2e, the structure and operation of the other parts are the same as in the thirteenth embodiment. The description of the effects 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 extended from the low-pressure side to the high-pressure side, overcompression at a low pressure ratio can be further reduced, and the performance can be further reduced. There is an effect of improving.

Next, an eighteenth embodiment will be described with reference to a plan view of the vicinity of the center of the fixed scroll member from the scroll wrap side in FIG. A pair of low pressure side bypass holes 2e
The fourteenth embodiment is the same as the fourteenth embodiment except that a notch is provided on the bottom side of the teeth in the direction along the scroll wrap 2b in the center and outward directions. Omitted. A pair of low pressure side bypass holes 2e
Has a role of suppressing excessive compression, but the main role is to avoid liquid compression. Since the period of communication with the compression chamber of the low-pressure side bypass valve 23 has been extended from the low-pressure side to the high-pressure side, liquid compression can be avoided more reliably and reliability is improved.

Finally, a nineteenth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion P in FIG. 1) near the differential pressure control valve in FIG. Except that a differential pressure valve spring 100c having a long natural length and an insertion valve cap 100j into which it can be inserted are the same as those of the first to fifteenth embodiments, the description of the structure, operation, and effects of the other parts will be omitted. As a result, the spring constant can be set small, and 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 100
Although c is a helical spring, it 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.

[0059]

According to the present invention, it is possible to provide a compressor having a low oil content of gas discharged outside the compressor.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment.

FIG. 2 is a plan view of the fixed scroll member of the first embodiment as viewed from the side opposite to the scroll wrap.

FIG. 3 is a plan view of the fixed scroll member according to the first embodiment as viewed from the scroll wrap side.

FIG. 4 is a plan view of the retainer of the first embodiment.

FIG. 5 is an explanatory diagram of a compression stroke according to the first embodiment.

FIG. 6 is a longitudinal sectional view of the vicinity of a bypass valve according to the first embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 7 is a vertical cross-sectional view of the vicinity of the differential pressure control valve according to the first embodiment (an enlarged view of a portion P in FIG. 1).

8 is a longitudinal sectional view (enlarged view of a Q portion in FIG. 7) of the vicinity of a turning side surface region of the differential pressure control valve according to the first embodiment;

FIG. 9 is a longitudinal sectional view of the vicinity of the oil storage chamber of the first embodiment (an enlarged view of a portion S in FIG. 1).

FIG. 10 is a perspective view of an oil droplet removing unit according to the first embodiment.

FIG. 11 is a plan view of the bearing support plate of the first embodiment as viewed from the motor chamber side.

FIG. 12 is a plan view of the bearing support plate of the second embodiment as viewed from the motor chamber side.

FIG. 13 is a plan view of the bearing support plate of the third embodiment as viewed from the motor chamber side.

FIG. 14 is a longitudinal sectional view of the vicinity of an oil storage chamber according to a fourth embodiment (FIG. 1);
FIG.

FIG. 15 is a longitudinal sectional view of the vicinity of an oil storage chamber according to a fifth embodiment (FIG. 1);
FIG.

FIG. 16 is an assembled perspective view of a gas cover according to a fifth embodiment.

FIG. 17 is a plan view of the gas cover of the fifth embodiment as viewed from the oil storage chamber side.

FIG. 18 is a longitudinal sectional view of the vicinity of an oil storage chamber according to a sixth embodiment (FIG. 1);
FIG.

FIG. 19 is a plan view of a bearing support plate according to a sixth embodiment as viewed from the motor chamber side.

FIG. 20 is a longitudinal sectional view of the vicinity of an oil storage chamber according to a seventh embodiment (FIG. 1);
FIG.

FIG. 21 is a longitudinal sectional view showing the vicinity of an oil storage chamber according to an eighth embodiment (FIG. 1);
FIG.

FIG. 22 is an assembled perspective view of a gas cover according to a ninth embodiment.

FIG. 23 is a plan view of the gas cover of the ninth embodiment as viewed from the oil storage chamber side.

FIG. 24 is a perspective view of an oil droplet removing unit according to a ninth embodiment.

FIG. 25 is a perspective view of an oil droplet removing unit according to a tenth embodiment.

FIG. 26 is a longitudinal sectional view of the vicinity of the oil storage chamber of the eleventh embodiment (an enlarged view of a portion S in FIG. 1).

FIG. 27 is an assembled perspective view of an oil trap plate according to a twelfth embodiment.

FIG. 28 is an attached perspective view of an oil trap plate according to a twelfth embodiment.

FIG. 29 is a longitudinal sectional view showing the vicinity of a mounting portion of an oil trap plate according to a twelfth embodiment.

FIG. 30 is a perspective view of an oil trap plate according to a thirteenth embodiment.

FIG. 31 is a perspective view of an oil trap plate according to a fourteenth embodiment.

FIG. 32 is a plan view of the fixed scroll member of the fifteenth embodiment as viewed from the scroll wrap side.

FIG. 33 is a plan view of the vicinity of the center of the fixed scroll member from the scroll wrap side in the sixteenth embodiment.

FIG. 34 is a longitudinal sectional view of a bypass hole according to a sixteenth embodiment.

FIG. 35 is a plan view of the vicinity of the center of the fixed scroll member from the scroll wrap side in the seventeenth embodiment.

FIG. 36 is a longitudinal sectional view of a bypass hole according to a seventeenth embodiment.

FIG. 37 is a plan view of the vicinity of the center of the fixed scroll member from the scroll wrap side in the eighteenth embodiment.

FIG. 38 is a vertical cross-sectional view of the vicinity of the differential pressure control valve according to a nineteenth embodiment (an enlarged view of a portion P in FIG. 1).

[Explanation of symbols]

2 ... fixed scroll member (non-orbiting scroll member), 2
e: bypass hole, 3 ... rotating scroll member, 4 ... frame, 5 ... Oldham ring, 6 ... compression chamber, 12 ... shaft, 19 ... motor, 44 ... frame oil ring, 45
... oil drop removing part, 46 ... oil ring, 47 ... oil trap plate, 47m ... two-stage bolt, 60 ... suction chamber, 6
1: fixed rear chamber, 62: motor chamber, 69: stored oil, 95
... rear discharge pressure area, 96 ... discharge chamber, 99 ... rear excessive suction pressure area, 100 ... differential pressure control valve.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazumi Tamura 800, Tomita, Odai-cho, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Inside the Hitachi, Ltd.Cooling Division Hitachi, Ltd.Cooling Division (72) Inventor Koichi Sekiguchi 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Inside (72) Inventor Atsushi Shimada 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi, Ltd. (72) Inventor Tetsuya Tadokoro 709, Tomita, Ohira-machi, Shimotsuga-gun, Tochigi 2 Inside Hitachi Tochigi Electronics Co., Ltd. (72) Takehiro Akizawa 800, Tomita, Odaira, Shimotsuga-gun, Tochigi Hitachi, Ltd. (72) Inventor Nobuo Abe Shimotsuga-gun, Tochigi 800, Tomita, Ohira-machi, Hitachi, Ltd.Cooling and Heating Division, Hitachi, Ltd.

Claims (4)

[Claims] 1. A compressor comprising: a compression operation section provided in an airtight container for compressing a gas introduced from outside; and an oil reservoir provided in the airtight container. A compressor having a path through the oil in the oil reservoir in a path leading to a discharge port which is an outlet to the outside of the compressor. 2. The compressor according to claim 1, further comprising a path passing through a porous body after a path passing through the oil reservoir. 3. A compressor provided in a closed container for compressing a gas introduced from the outside, and an oil reservoir provided in the closed container, wherein the gas from the compressing unit is sealed by the sealing unit. In the compressor which discharges into a container, the position which opposes the compression operation port which discharges the gas from the said compression operation part into the said closed container, and was away by the distance of 0.25 times the equivalent diameter of this compression operation port. A compressor with an oil trap plate arranged on the top. 4. A compression mechanism portion and an electric motor portion for driving the compression mechanism portion in the closed container, and the refrigerant discharged from the compression mechanism portion is discharged from the discharge port to the outside through the closed container. In the compressor, a discharge pipe is provided on the opposite side of the compression mechanism with respect to the electric motor unit, an auxiliary bearing provided between the electric motor unit and the discharge pipe, and a hole provided in the auxiliary bearing. A compressor having an opened support plate and a shielding plate between the support plate and the discharge port.