JPH11132164A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide high performance in the whole operation area by arranging a back face excessive intermediate pressure area to apply pressure slightly larger than intermediate pressure between suction pressure and delivery pressure to a turning back face being the anti-compression space side of an end plate of a scroll member. SOLUTION: An opposite surface side space of a valve element 100a leads to an intermediate pressure chamber 68 where a time average becomes intermediate pressure being pressure between suction pressure and delivery pressure by an intermediate side conducting passage 2α. Therefore, when pressure of a back face excessive intermediate pressure area 99 becomes higher than excessive intermediate pressure being a constant value correspondent to pressing force of a differential pressure regulating valve spring 100c in this intermediate pressure, the valve element 100a moves to the differential pressure regulating valve spring 100c side. As a result, among gas and oil in a turning side surface area 67, one except flowing in a suction chamber 60 through a slidingly movable surface flows in the intermediate pressure chamber 68 through a back face side conducting passage 2β, a clearance between the valve element 100a and a valve seal surface 2j, a side surface of the valve element 100a, a valve hole 2f and an intermediate side conducting passage 2α. As a result, volumetric efficiency is improved, and a small and large capacity compressor is obtained.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a structure for improving overall adiabatic efficiency and reliability in a wide operating range.

[0002]

2. Description of the Related Art A conventional scroll compressor is provided with a bypass valve for suppressing a pressure in a compression chamber from becoming higher than a discharge pressure as shown in a known example of FIG. There is provided a flow path for supplying a fluid from the fluid supply unit to the back surface of the orbiting scroll member and releasing the fluid to a suction system via a valve device including a valve body and a pressing spring. As a result, the pressure on the back of the orbit is controlled to a value larger than the pressure of the suction system by a substantially constant value in accordance with the strength of the pressing spring in the valve device. It could be set small in the range and high performance was realized (published by the 31st Air Conditioning and Refrigeration Union Lecture Paper Collection H9.4.1).

[0003]

The separation force is determined by the discharge pressure which is the pressure of the fluid in the discharge chamber together with the pressure distribution of the fluid in the compression chamber. The pressure distribution of the fluid in the compression chamber depends almost exclusively on the suction pressure, unless there is an extremely large internal leak. On the other hand, the discharge pressure does not depend on the suction pressure because the discharge pressure and the suction pressure can be arbitrarily changed according to the setting of the use environment where the compressor is placed. Thus, the separation force depends on two independent parameters, suction pressure and discharge pressure. Since the attraction force is a force applied to attract the two end plates against the separation force, from the viewpoint of the load deformation of the scroll member, it is desirable that the magnitude is always substantially the same level as the separation force. . In that case, the urging force acting between the scroll member and the support member is reduced, and when there is a relative movement between the scroll member and the support member, the risk of friction loss and wear there can be reduced. Although the magnitude of the force is always equal to or greater than the separating force, it is desirable that the magnitude is substantially the same.

However, in the actual case, the scroll member receives a force from the fluid in a direction perpendicular to the axial direction, a centrifugal force, and the like. Therefore, the attraction force must counter the tilting moment generated by the force. . For this reason, for each operating condition, it is ideal to control the generation of the attraction force that minimizes the urging force among the sizes in which the end plate of the scroll member can be attracted, but considering the cost,
It is impossible in practice except in special cases. Therefore, the actual attraction force adding means realizes that the magnitude of the attraction force achieves a value obtained by adding an additional amount to counter the tilting moment to the magnitude of the separation force in the entire required operating range. A relatively simple mechanism. As previously mentioned,
Since the separating force is determined by the suction pressure and the discharge pressure, the attraction force applying means must have a mechanism depending on the suction pressure and the discharge pressure.

However, in the prior art, as a method of realizing the attraction force applying means, a rear over-suction pressure region having a pressure dependent only on the suction pressure of suction pressure + constant value (hereinafter referred to as over-suction pressure value). Therefore, if the over-suction pressure value is set so that both end plates are attracted under a wide range of operating conditions, a condition may occur in which the biasing force becomes excessive, and under these conditions, internal leakage increases due to deformation of the scroll member. In addition to the performance degradation due to an increase in the sliding loss of the biasing portion and the urging portion, there is a problem that the danger of abrasion in the sliding portion increases and the reliability decreases.

An object of the present invention is to solve the above-mentioned problems of the prior art and to provide a scroll compressor having high performance in all operating conditions.

[0007]

As a first means for achieving the above object, a head plate and a spiral scroll wrap provided on the end plate are provided, and the scroll plate is perpendicular to an axial direction in which the scroll wrap is provided. A orbiting scroll member that orbits without rotating in the plane, a non-orbiting scroll member that includes a head plate and a spiral scroll wrap standing upright and whose movement in at least a direction perpendicular to the axial direction is substantially restricted. And a compression chamber whose volume is reduced by substantially closing between the scroll members, and the two scroll members opposing a separating force in a direction of separating the end plates of the both scroll members due to the pressure of the fluid on the compression chamber side. Attraction force applying means for applying an attraction force in a direction of attracting the end plate of the member to each of the scroll members; A scroll support member for generating a reaction force of the urging force, which is the sum of the vectors, on each of the scroll members, a suction system for introducing a fluid into the compression chamber, and a discharge system for guiding a fluid pressurized in the compression chamber to the outside In the scroll compressor, at least a part of the attraction force applying means in the orbiting scroll member is a pressure in the suction chamber on a orbiting back surface which is a surface of the end plate of the orbiting scroll member on the side opposite to the compression chamber. It is realized by providing a back excessive intermediate pressure region to apply a pressure that is larger than the intermediate pressure between the suction pressure and the discharge pressure which is the pressure in the discharge system by a fixed value within an error of about 20% of the intermediate pressure. In addition, a pressure control means is provided to suppress the pressure of the compression chamber from becoming higher than the discharge pressure which is the pressure in the discharge system.

As a second means for achieving the above object, there is provided a head plate and a spiral scroll wrap provided on the end plate, and the head is rotated in a plane perpendicular to an axial direction in which the scroll wrap is provided. A non-orbiting scroll member that orbits without orbiting, and includes a head plate and a spiral scroll wrap standing upright, and a non-orbiting scroll member whose movement in at least a direction in a plane perpendicular to the axial direction is substantially restricted, A compression chamber whose volume is reduced by being substantially closed between the scroll members, and a head plate of the both scroll members opposed to a separating force in a direction of separating the head plates of the both scroll members due to the pressure of the fluid on the compression chamber side. Attraction force applying means for applying an attraction force in an attraction direction to each of the scroll members; and a vector sum of the attraction force and the separation force. A scroll support member for generating a reaction force of a certain urging force on each of the scroll members, a suction system for introducing a fluid into the compression chamber, and a discharge system for guiding a fluid pressurized in the compression chamber to the outside; In the scroll compressor, a scroll support member of the non-orbiting scroll member is the orbiting scroll member, and at least a part of the attraction force applying means in the non-orbiting scroll member is an anti-compression chamber of a head plate of the non-orbiting scroll member. A constant value within an error of about 20% of the intermediate pressure between the suction pressure, which is the pressure in the suction chamber, and the discharge pressure, which is the pressure in the discharge system, on the non-swirl back surface which is the side surface. A super-intermediate pressure region is provided to apply a pressure as large as possible. It provided with a control means.

As a third means for achieving the above object, a flow between the discharge back surface and a throttle provided between the discharge system and the back intermediate pressure region together with the first and second means. And a back-over-compressor passage provided between the passage and the back-over-compressor pressure region and an intermediate-compression chamber, which is a compression chamber that becomes the above-described intermediate pressure on a time average. The pressure difference between the pressure region and the intermediate compression chamber
A pressure difference control means was provided to control the pressure to a constant value within an error of about a certain value, and the pressure in the rear intermediate pressure region was set.

[0010] As a fourth means for achieving the above object, a flow between a discharge back surface and a throttle provided between the discharge system and the back intermediate pressure region together with the first and second means. The pressure difference between the back excessive intermediate pressure region and the intermediate compression chamber in the back intake passage provided between the passage and the rear excessive intermediate pressure region and the suction system and the back intake passage. Pressure difference control means was provided to control the pressure to a constant value within an error of about 20%, and the pressure in the rear intermediate pressure region was set.

[0011] The first means is for applying a pressure to the rear surface of the orbiting scroll member that is higher than the intermediate pressure between the suction pressure and the discharge pressure by a constant value (hereinafter referred to as an excessive intermediate pressure value). In order to provide a region, compared to the conventional technology in that the pressure level can be freely set between the suction pressure and the discharge pressure, as compared with the conventional case in which a back over-suction pressure region in which a pressure larger than the suction pressure is applied by a fixed value is provided. There is also a degree of freedom. For this reason, in a wide operating range, the urging force can be set smaller than in the conventional technology, the deformation of the scroll member is suppressed, the management of the seal of the compression chamber is facilitated, the internal leakage is suppressed, and the total adiabatic efficiency is improved. There is an effect that improvement can be realized. In the case where the orbiting scroll member and the supporting member have a relative motion, the urging force acting on the sliding portion is reduced, so that the risk of sliding loss and wear there is reduced, and the total heat insulating efficiency and There is an effect that reliability can be improved.

[0012] The second means may include the contents of the first means, wherein the non-orbiting scroll member is movable in the axial direction and a back excessive intermediate pressure area is provided on the non-orbiting rear surface to convert the non-orbiting scroll member to the orbiting scroll member. This is applied to a scroll compressor of a pressing system, and has the same effect as that of the first means.

The third means introduces a pressure from the own discharge system to the back intermediate pressure region through a discharge back surface flow path with a throttle, and controls the pressure via a pressure difference control means. Since the pressure is discharged to the intermediate pressure chamber by the interflow channel, it is not necessary to provide a pressure source outside. As a result,
In addition to the effects of the first and second means, the compressor can be operated alone without the need for external assistance, and thus there is an effect that usability can be improved. Here, since the restrictor is provided in the flow path between the discharge back surfaces, a large amount of high-pressure fluid does not flow into the back intermediate pressure region. For this reason, it is possible to avoid a reduction in the capacity caused by short-circuit flow from the suction system to the discharge system in the compressor.

The fourth means is such that the pressure introduced in the rear excess intermediate pressure area in the third means is discharged to the intermediate pressure chamber, and the pressure is discharged to the blowing system. As a result, since the swelling of the acupressure diagram caused by the gas flowing into the intermediate pressure chamber in the third means is eliminated, there is an effect that the total adiabatic efficiency can be further improved.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention is a fixed scroll member in which a non-orbiting scroll member is fixed to a casing, and a rear excessive intermediate pressure area is provided on the orbiting back side of the end plate of the orbiting scroll member which is opposite to the compression chamber. In the required operating pressure condition range, the scroll support member of the orbiting scroll member was used as the fixed scroll member, that is, the orbiting scroll member was pressed against the fixed scroll member. One embodiment 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. FIG. 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 pressure difference control valve (P in FIG. 1). FIG. 8 is a longitudinal sectional view (enlarged view of a portion Q in FIG. 7) of the vicinity of the back pressure chamber of the pressure difference control valve, and FIG. 9 is an explanatory diagram of operating conditions where the effect is exhibited. 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 having an involute or an algebraic spiral as a basic line on a head plate 3a, a bearing holding portion 3s having a orbital bearing 3w inserted on the back thereof, and an orbiting Oldham groove 3g. , 3h.

In the fixed scroll member 2, a scroll wrap 2b is erected on a head plate 2a, and a non-turn reference surface 2u which is the same plane as the scroll wrap tooth tip surface is provided, and a peripheral groove 2c is formed there. And four bypass holes 2e are provided in the tooth bottom. The reason why four bypass holes 2e are provided here is to always open the bypass holes in all the formed compression chambers 6. A bypass valve plate 23x, which is a reed valve plate, and a retainer 23a for limiting the opening degree of the valve plate 23x are fixed by a bypass screw 23h so as to cover the bypass hole 2e. Further, a discharge hole 2d is opened near the center. In addition, the suction digging 2
q, 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 this time, the valve body 24a and the check valve spring 24c are inserted to form the suction side check valve 24. Further, a plurality of flow grooves 2r for flowing gas and oil are provided on the outer periphery of the fixed scroll member 2. The motor wire 77 is passed through one of them. A back side conduction path 2β and a valve hole 2f are formed in the peripheral groove 2c to provide a valve sealing surface or a valve sealing line 2j. Then, an intermediate side conduction path 2α is provided which connects the side face of the valve hole 2f and the tooth bottom facing the substantially closed compression chamber for at least a certain period. 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 moved to a valve having a larger diameter than the valve hole 2f in a state where one end of the differential pressure valve spring 100c is inserted into a spring positioning projection 100h. The differential pressure control valve 100 is formed by press-fitting into the cap insertion portion 2k.

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 excessive intermediate pressure value, the depths of the valve hole 2f, the depth of the cap insertion portion 2k, the thickness of the valve body 100a, the spring constant of the differential pressure valve spring 100c, The natural length must be managed accurately. 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, and the excessive intermediate pressure value becomes abnormally small, so that the orbiting scroll member 3 separates from the fixed scroll member 2 and normal operation becomes 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 regular value.

The pressing force at this time is the same as that of the back side conductive path 2β.
A method is adopted in which a rod is inserted into the valve body and one end is attached to the valve body 24a, and the force applied to the rod is detected. In this case,
Since there is no need to precisely control the dimensions and the values of the spring constants of the above-described parts, there is an effect that the mass productivity is improved. In both of these two methods, when the assembly is completed, the outer peripheral portion of the valve cap 100f and the valve cap insertion portion 2
The space between the inner circumferences of k must be completely sealed. Adhesion or welding may be performed to complete the seal. Here, the spring positioning protrusion 100
A tapered shape in which the diameter of the tip is smaller than the root of h may be used. 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 does not contact the positioning protrusion 100h,
The natural length of the spring is maintained as it is when the spring is used alone.
Therefore, there is a specific effect that an error from the set value of the excessive intermediate pressure value can be reduced.

The frame 4 has a fixed mounting surface 4b for mounting the fixed scroll member 2 on the outer periphery thereof, and a revolving sandwiching surface 4d provided inside the fixed mounting surface 4b. A recessed surface groove 4α is provided. Further inside, in order to arrange the Oldham ring 5 between the frame 4 and the orbiting scroll member 3, frame Oldham grooves 4e and 4f (both not shown) are provided. Also,
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. A lateral hole 4n is opened from the side of the frame toward the space 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. The motor wire 77 is passed through one of them.

Frame protrusions 5a and 5b (both not shown) are provided on one surface of the Oldham ring 5, and revolving protrusions 5c and 5d are provided on the other surface.

The shaft 12 has a shaft oil supply hole 1 therein.
2a, a main bearing lubrication hole 12b, a shaft seal lubrication hole 12c, and an auxiliary bearing lubrication hole 12i are provided. A balance holding portion 12h having an enlarged diameter is provided at an upper portion thereof, and a shaft balance 49 is press-fitted therein. Further, an eccentric portion 12f is provided.

The rotor 15 incorporates an unmagnetized permanent magnet (not shown) in a laminated steel plate 15a, and a rotor balance 1 at both ends.
5c and 15p are provided.

The stator 16 is provided with 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 16b, and has a coil through hole 16v formed therein. The coil 16w passes here, and the sub-bearing side coil end 16x and the main bearing side coil end 16x, which are the folded portions of the coil, are provided.
y are arranged on both sides of the stator 16. By the way, in place of the stator groove 16c or together with the stator groove 16c, the coil through hole 1 is formed inside the laminated steel plate 16b.
A through hole may be formed outside 6v.

These components are assembled as follows. First, the shaft 12 in which the shaft balance 49 is press-fitted or bonded to the main bearing 4a of the frame 4
And press-fit or shrink-fit the rotor 15.
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
While inserting the turning protrusions 5c and 5d of the Oldham ring 5 into the turning Oldham grooves 3g and 3h and inserting the eccentric portion 12f of the shaft 12 into the turning bearing 3w,
It is mounted on the swivel pinching 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 cover screw 53 at a position where the rotational torque is minimized while rotating the shaft 12. At this time, the end plate 3a of the orbiting scroll member 3
The thickness of the orbiting scroll member 3 and the fixed scroll member 2 in the axial direction is determined so that the thickness of the orbiting scroll member 3 and the fixed scroll member 2 is smaller than the distance between the orbiting sandwiching surface 4d and the non-orbiting reference surface 2u. I do. Further, an orbiting excessive intermediate pressure area 99 is provided on the back surface of the orbiting scroll member 3.

Next, the above-mentioned assembly portion is inserted into the cylindrical casing 31 to which the bearing support plate 18 to which the gas cover 88 having the gas vent passage 88a has been welded or press-fitted is pre-fitted with the stator 16 or press-fitted. Then, tack welding is performed on the side surface of the frame 4 or the fixed scroll member 2. Here, bonding may be performed instead of tack welding. At this time, deformation of the assembled portion due to welding is eliminated, and the performance is improved.

Thus, the motor 19 is formed by the rotor 12 and the stator 16, and the bearing support plate 1 is formed.
A motor chamber 62 is formed between the frame 8 and the frame 4. Next, the bearing housing is assembled so that one end of the shaft 12 protruding from the hole at the center of the bearing support plate 18 is inserted into the cylindrical hole of the spherical bearing 72 mounted on the bearing housing 70, and the rotation of the shaft 12 is performed. The position of the bearing housing 70 is adjusted while detecting the torque, and the bearing housing 70 is spot-welded to the bearing support plate 18 at a position where the rotational torque is minimized.

Then, the oil supply cap 90 to which the oil supply pipe 71 is welded is screwed into the bearing housing 70 with the seal 73 interposed therebetween. Here, the oil supply pipe 71 is bent downward after screwing the oil supply cap 90 into the bearing housing 70.
Alternatively, a spotless welding cap with a bent oil supply pipe may be inserted into a threadless bearing housing. Here, the accuracy of the seal surface may be increased and the pressing force of the seal surface may be increased so that the seal is performed without sandwiching the seal 73. Then, the bottom casing 21 in which the discharge pipe 55 is welded to the upper part of the cylindrical casing 31 is welded to form an oil storage chamber 80. Refueling pipe 7
A magnet 89 is provided near the front end of the first.

Further, the upper casing 20 in which the hermetic terminal 22 is welded to the upper portion of the cylindrical casing 31 is welded by attaching a motor wire 77 to an inner terminal of the hermetic terminal 22 and welding the suction pipe 54. , The fixed rear chamber 61 is formed. In this state, the stator 1
6, a permanent magnet 15 b inside the rotor 15 is magnetized to form a motor 19. Then add the oil.

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

When the motor 19 starts rotating, the shaft 12 rotates and the orbiting scroll member 3 starts to orbit. Here, the Oldham ring 5
As a result, the rotation of the orbiting scroll member 3 is prevented. By this operation, the compressible gas in the suction chamber 60 is confined in the compression chamber 6 formed between the two scroll members, is compressed, and starts to be discharged from the discharge hole 2d to the fixed rear chamber 61. By the way, the thickness of the end plate 3a of the orbiting scroll member 3 is set to be smaller than the distance between the orbiting sandwiching surface 4d and the non-orbiting reference surface 2u by about 5 to 20 [mu] m, so that the orbiting scroll member 3 and the fixed scroll are fixed. The maximum separation distance in the axial direction of the member 2 is defined.

For this reason, immediately after the start of the compressor, the orbiting scroll member 3 is separated from the fixed scroll member 2 by the separating force of the gas in the compression chamber 6 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 pinching surface 4d,
A gap is formed between the lap side of the end plate 3a and the non-swirl reference surface 2u by the maximum separation distance described above. at the same time,
Since the gap between the tooth tip and the tooth bottom of the lap is almost the same, internal leakage is large and high-efficiency operation cannot be performed.
If the maximum separation distance is approximately the same, the internal rotation can be suppressed by increasing the motor rotation speed to the maximum allowable value immediately after startup, and the suction pressure can be sufficiently reduced or the discharge pressure can be sufficiently increased. . The gas discharged into the fixed rear chamber 61 enters the motor chamber 62 through the fixed scroll member 2 and the flow grooves 2r and 4h formed on the outer periphery of the frame 4.

The gas entering the motor chamber 62 cools the stator 16 while passing through the stator groove 16c, cools the rotor 15 while passing through the through hole 15h of the rotor 15, and further cools the rotor and the stator. Cool both through the gap. Here, the stator groove 1
Eliminating 6c has a unique effect of improving motor efficiency because a large amount of gas and oil comes into contact with the rotor to promote cooling of the rotor. In the process, the gas collides with each part of the motor 19 and separates the oil contained therein. The separated oil falls to the lower part of the motor chamber 62. The gas inside the motor chamber 62 passes through the vent hole 18b and flows into the upper part of the oil storage chamber 80, and the discharge pipe 55
Get out more. Here, the pressure in the oil storage chamber 80 becomes lower than the pressure in the motor chamber 62 due to the flow path resistance of the ventilation hole 18b. Therefore, the oil in the motor chamber 62 flows into the oil storage chamber 80 through the oil guide hole 18a. At this time, gas also flows into the oil storage chamber 80 from the oil guide hole 18a at the same time and rises as oil bubbles in the oil in the oil storage chamber 80. The oil storage chamber 8 rises inside the oil storage chamber 8 through the passage opening 88b.
Since the gas flows to the upper gas portion, no air bubbles enter the oil supply pipe 71, and there is a specific effect that the reliability of the bearing can be improved.

As described above, the oil level in the motor chamber 62 does not reach the rotor 15 or the shaft 12, and the oil can be stored in the small compressor. Can be realized in a small size, which is an effect unique to the present embodiment. Immediately after the compressor is started, the pressure in the back intermediate 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 pressure in the oil storage chamber 8 is determined by a pressure difference between the pressure in the rear excess intermediate pressure area 99 and the oil storage chamber 80 which is almost close to the discharge pressure.
The oil of No. 0 enters the oil supply cap 90 from the oil supply pipe 71 where the spherical bearing 7
2 is supplied to the bearing portion on the spherical surface side.

Further, the shaft 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 center hole of the spherical bearing 72 passes through the auxiliary bearing oil supply hole 12i when a centrifugal force is applied. Supplied to the side bearing,
The other part is similarly supplied to the shaft seal 4a through the shaft seal oil supply hole 12c by applying centrifugal force,
The other part is supplied to the main bearing 4m through the main bearing oil supply hole 12b by centrifugal force, and the rest reaches the center of the back surface of the orbiting scroll member 3 and then the same differential pressure and centrifugal force as described above. It is supplied to the swing bearing 3w.

As a result, a back surface 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 oil supplied to the main bearing 4m and the slewing bearing 3w enters the rear excessive intermediate pressure area 99 after the temperature rises due to the friction there. At this time, the average pressure of the oil in the bearing portion is higher than the pressure in the back intermediate pressure region 99 in the oil storage chamber 80.
Since it is a high pressure close to the pressure on the side, it blows out to the back excessive intermediate 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, since heat of vaporization is taken from the surroundings, there is a specific effect that the reliability of the main bearing 4m and the slewing bearing 3w is improved in order to suppress the temperature level in the vicinity thereof to be low.

Also, since the oil here becomes a mist,
The sliding portion of the Oldham ring 5 can be reliably lubricated, and there is a specific effect that reliability is improved. As a result, the amount of gas flowing into the rear excess intermediate pressure region 99 increases rapidly immediately after the start of the compressor. 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. Since the gap of 2u is small and the amount of oil in the flowing fluid is large and partially forms a seal portion, the amount of outflow is smaller than the amount of inflow to the back excess intermediate pressure area 99, and the back excess The pressure in the pressure region 99 rises sharply.

As a result, together with the contribution of the pressure increase in the back discharge pressure region 95 due to the rise of the discharge pressure, the attractive force applied to the orbiting scroll member 3 sharply increases, and almost immediately after the start of the compressor or in an emergency. In a short time, the magnitude of the attraction force becomes greater than the magnitude of the separation 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 or eliminated, so that the hermeticity of the compression chamber 6 is improved, the amount of internal leakage of gas during compression is reduced, and immediately after startup, The performance is dramatically improved as compared to the normal operation state.

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 all the gas and oil flowing into the rear excess intermediate pressure area 99 do not directly flow into the suction chamber 60, the operation is the same as that immediately after the start of the compressor, so only this part will be described. The gas and oil flowing into the rear excess intermediate pressure region 99 pass through the sandwiching surface groove 4α and the gap between the anti-lap surface of the end plate 3a and the turning sandwiching surface 4d,
It enters a turning side surface area 67 which is a space between the side surface of the end plate 3a and the frame 4. Some of these flow into the suction chamber 60 while lubricating both sliding surfaces of the lap side of the end plate 3a and the non-swirl reference surface 2u. Since the flow resistance between the turning side surface region 67 and the back excessive intermediate pressure region 99 is small, the pressure in the turning side region 67 is substantially equal to the pressure in the rear excessive intermediate pressure region 99.

As can be seen from FIG. 8, since the peripheral groove 2c always communicates with the turning side surface area 67, the pressure in the peripheral groove 2c becomes the pressure of the rear excessive intermediate pressure area 99, and The pressure of the back excess intermediate pressure region 99 is applied to the frame-side surface of the valve body 100a of the differential pressure control valve 100 via the conduction path 2β. The space on the opposite surface side of the valve element 100a communicates with the intermediate pressure chamber 68, which is an intermediate pressure whose time average is the pressure between the suction pressure and the discharge pressure by the intermediate conduction path 2α. Intermediate pressure area 99
Is higher than the intermediate pressure, that is, the excess intermediate pressure value which is a constant value corresponding to the pressing force of the differential pressure valve spring 100c, the valve body 100a moves toward the differential pressure valve spring 100c. As a result, except for the gas and oil in the swivel side surface region 67 which have flowed into the suction chamber 60 via the sliding surface, the back side passageway 2β, the valve body 100c
And through the gap between the valve seal surface 2j, the side surface of the valve body 100c, the valve hole 2f, and the intermediate side passageway 2α, and flows into the intermediate pressure chamber 68. Then, it is mixed with the gas in the compression chamber and compressed, and is discharged from the discharge hole 2d.

As described above, as a result of not returning the entire amount to the suction chamber 60, there is an effect that the volume efficiency is improved, and a compact and high-performance compressor can be provided. In this way, the pressure in the rear excess intermediate pressure region 99 is controlled to a pressure higher than the intermediate pressure by a constant value corresponding to the pressing force of the differential pressure valve spring 100c. The intermediate pressure is controlled to a value substantially proportional to the suction pressure, and the proportional constant roughly corresponds to the distance from the wrap end along the wrap of the intermediate pressure chamber side opening end of the intermediate side passageway 2α. Value. Under the condition that the bypass valve 23 opens during the period in which it opens into the intermediate pressure chamber 68, the pressure of the intermediate pressure chamber thereafter does not increase significantly due to the opening of the bypass valve 23, and the proportional constant is larger than when the bypass valve 23 does not open. Becomes smaller, and the decrease rate becomes
The larger the ratio of the opening period of the bypass valve 23 to the period during which the bypass valve 23 opens to the intermediate pressure chamber 68, the larger the ratio. In summary, the pressure in the excessive intermediate pressure region 99 is roughly controlled as follows.

Assuming that A, B (excess intermediate pressure value) and C are certain constants:
(B) When the bypass valve 23 is open during the period in which the bypass valve 23 is open to the intermediate pressure chamber 68, the pressure ΔC · suction pressure + B (where C <A) Here, the value of A can be arbitrarily set by changing the distance from the end of the wrap winding along the wrap of the intermediate pressure chamber side opening end of the intermediate side passageway 2α. Accordingly, the value of C also changes.

As described above, the intermediate pressure can be arbitrarily set together with the excess intermediate pressure value. Therefore, by selecting an optimum combination of the intermediate pressure and the excess intermediate pressure value according to the operating conditions of the compressor, the conventional art can be used. As compared with the case, the orbiting scroll member is pressed against the fixed scroll member in the entire required operating range, and a high-performance compressor having a small urging force and a small sliding loss in a wide operating condition range can be realized.

Further, in the case of this embodiment, the oil supply passage of the main bearing 4m and the swivel bearing 3w having the throttle portion as a bearing gap serves as the oil supply passage of the discharge back-to-back passage 102. As is clear from the description, the compressor itself can be started without using external force, and thus, there is an effect that usability is improved.

By the way, the back intermediate pressure region 99
Is short-circuited from the discharge system in the compressor to the intermediate pressure chamber 68 in the middle of compression. is necessary. 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, a porous solid 88c formed by knitting or randomly entangled heat-resistant fibers or heat-resistant wires is disposed inside the gas vent passage 88b. Thereby, the bubbles rising in the oil inside the degassing passage 88b reach the surface of the oil and are supplemented with the mist-formed oil when crushed, and the rising speed of the bubbles in the oil is reduced to form the mist. There is an effect that the amount of oil is reduced and the amount of oil discharged from the compressor is reduced.

Further, since the gas nucleus is formed at a location where bubble nuclei are generated to trigger gas components supersaturated in oil to be vaporized, a decrease in oil viscosity can be suppressed, and the effect of improving the reliability of each bearing can be improved. is there. A dryer layer 88d filled with a large number of dryer particles is provided inside the porous solid 88c. The dryer layer 88d has the above-described effect as a porous solid and removes moisture in oil.
Inside the gas vent passage 88b, the oil is constantly agitated by the gas bubbles of the rising gas, so that the moisture adsorption efficiency of the dryer increases, and the moisture in the oil can be removed in a short time.

As a result, in the case of an ester-based oil or the like which produces a problematic substance which causes the oil to hydrolyze and cause the abrasion of a material such as an acid, a specific effect of improving the reliability of the sliding portion is obtained. This has the effect of suppressing the generation of rust in the compressor.

Since the dryer layer 88d is surrounded by the porous solid 88c, the particles of the dryer do not rub against each other. Therefore, the flow velocity of the gas in the gas vent passage 88b is small. As a result, since the particles of the dryer do not rub against each other to generate a hard dryer powder, they do not mix with the oil and wear the bearings and the like, and have a specific effect that the reliability is improved. .

By providing a dryer not only in the gas cover 88 but also in the portion of the compressor where oil is stored, the contact time between the dryer and the oil can be lengthened, and the adsorption rate of moisture can be greatly increased. And reliability is improved.
In particular, when a dryer is installed in the piping system outside the compressor, water in the oil is mainly adsorbed only during operation. Water can be adsorbed, which is effective in increasing the reliability of the compressor under the operating conditions where the operation frequency is low.

The end plate 2 of the fixed scroll member 2
a 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 the bypass screw 23h is provided together with the retainer 23a.
And the bypass valve 23 is formed. 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 in the fixed rear chamber 61 is the discharge pressure, this bypass valve is connected to the compression chamber 6.
When the pressure is higher than the discharge pressure, the compression chamber 6 and the discharge system are communicated with each other, thereby forming a control bypass. 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 excessive intermediate pressure region 99 is provided on the back of the orbit as an attractive force applying means for the orbiting scroll member 3, and the bypass valve 23 serving as a control bypass is provided.
Also, the excessive intermediate pressure value can be set small, and the urging force can be set small over a wide operating range. As a result, there is an effect that the total adiabatic efficiency and reliability can be increased in a wide operation range.

By the way, as shown in FIG. 5, four bypass holes 2e are provided so as to always connect the compression chamber 6 and the fixed back chamber 61, so that liquid compression may occur at any timing. Before the pressure rises extremely, the bypass valve opens and the fluid is discharged into the fixed back chamber 61. As a result, there is an 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.

Here, the part P in FIG. 1 of this embodiment is
As shown in FIG. 2, A is set to 1 in the above equation when the intermediate side passage 2α is provided at a position which does not always face the compression chamber that substantially closes the opening end of the intermediate pressure chamber side, that is, at the suction chamber 60. be able to. Accordingly, C also becomes 1. At this time, as is apparent from the above equation, the back excessive intermediate pressure region 99
Is controlled to the suction pressure + a constant value. In other words, it can be understood that the means of this embodiment is a basic means that, if developed, becomes a conventional technique. Therefore, the effects specific to the present embodiment described above and the effects specific to the embodiments described hereinafter are also the effects of the prior art embodiment in which the suction pressure + a fixed value is applied to the back surface of the orbiting scroll member.

Here, the part P in FIG. 1 of this embodiment is
As shown by 3, if the intermediate pressure chamber side opening end of the intermediate side passageway 2α is provided in the communication groove 2δ serving as a suction pressure, the same effect is obtained, and the pressure in the valve hole 2f is caused by the movement of the wrap. Since it is not affected by local pressure fluctuation, there is a specific effect that the controllability of the back pressure of the orbiting scroll member 3 is improved.

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.

The orbiting scroll member 3
The bottom surface of the bearing holding portion 3s at the center of the rear surface of the end plate 3a has a swirling discharge pressure region 95 because the oil of the discharge pressure from the shaft oil supply hole 12a enters. The discharge pressure region 95 is a region of the inner diameter of the swing bearing 3w). Moreover, the projected area viewed from the axial direction is the maximum value and the minimum value of the sum of the projected area viewed from the axial direction of the discharge chamber and half the tip area of both scroll wraps forming the boundary between the compression chambers surrounding the projected area. Therefore, it is not necessary to consider the contribution of the ejection pressure to the separation force. Therefore, since the excessive intermediate pressure value in the pressure in the rear excessive intermediate pressure region 99 can be set smaller, there is an effect that the overall adiabatic efficiency and reliability can be further improved.

Here, an example of the projected area is shown in FIG. This figure shows the moment when the innermost compression chambers A1 and A2 communicate with the discharge chamber A3. Assuming that it is immediately after communication,

[0063]

## EQU1 ## A1 + A2 + A3 + K2 + K3 + S2 + S3 +
(K1 + S1) / 2 is the maximum value of the projection area in question. Also, if it is considered immediately before communication, A3 + (K3 + S3) / 2, which is the minimum value of the projection area in question.

Here, when this compressor is used as a compressor for a refrigeration cycle, the operating range of the suction pressure and the discharge pressure is as follows.
As shown in FIG. 9, the discharge pressure becomes low under the condition that the suction pressure is high. Therefore, if there is a control bypass, over-compression is suppressed or does not occur, so that even if the suction pressure increases, the separation force decreases. Therefore, there is an effect that the excessive intermediate pressure value can be set even smaller, and the overall adiabatic efficiency and reliability can be improved. The refrigeration cycle is one of applications requiring an operation range as shown in FIG. 9, and this effect is not limited to this. Other than this, the same effect is obtained in applications requiring similar operating conditions under pressure conditions.

Next, a second embodiment will be described with reference to a longitudinal sectional view (an enlarged view of a portion P in FIG. 1) of the vicinity of the pressure difference control valve in FIG. Valve seal surface 100j and back side conduction path 10
This is the same as the first embodiment except that a valve seal member 100i having 0β is fixedly arranged near the opening of a valve hole 2f opened from the non-orbiting reference surface 2u side of the fixed scroll member 2 and a concave portion 100g is provided. Therefore, description of the structure, operation, and effects of the other parts will be omitted. The valve seat surface is liable to be worn by being hit by the valve body 100a as the differential pressure control valve 100 is opened and closed. There is a specific effect that a valve can be realized. For example, a material having a higher hardness than the material of the fixed scroll member 2 is used.
Furthermore, since the concave portion 100g is formed, it is not necessary to limit the position of the back side conduction path to the position of the peripheral groove,
There is also a specific effect that the degree of freedom in design is improved.

Next, a third embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion P in FIG. 1) near the pressure difference control valve in FIG. Since it is the same as the first embodiment except that the gas and oil introduced into the rear excess intermediate pressure region are discharged to the blowing system, the description of the structure, operation and effect of the other parts is omitted. In the first embodiment, the valve hole 2f
The suction-side flow passage 2i communicating with the suction chamber 60 is provided in the, the valve seat surface is eliminated, and a cylindrical valve body 100d having a cylindrical surface on its side serving as a sealing surface is incorporated in place of a plate-like valve body. An intermediate pressure is applied to the side of the differential pressure valve spring 100c of the cylindrical valve body 100d, and a back excessive intermediate pressure area 99 is provided on the opposite surface.
Pressure. When the distal end of the cylindrical valve body 100d moves to the position of the suction side flow passage 100i, the back side flow passage 2β and the suction side flow passage 2i communicate with each other, and the flow path between the back compression chambers is opened. , The suction side flow path 2
By changing the position i and the spring constant or natural length of the differential pressure valve spring 100c, the excessive intermediate pressure value can be set arbitrarily. As a result, in the first embodiment, since the swelling of the acupressure diagram caused by the gas flowing into the intermediate pressure chamber 68 is eliminated, there is an effect that the overall adiabatic efficiency can be improved.

Further, a valve body seal 100k, which is a ring-shaped seal member, may be provided on the cylindrical surface of the cylindrical valve body 100d. As a result, the sealing on the side surface of the valve element is ensured, and the swelling of the acupressure diagram described above is reliably eliminated, so that there is an effect that the total heat insulation efficiency can be reliably improved. Also,
A conduction path capillary 100m may be inserted into the intermediate pressure chamber side end of the intermediate conduction path 100β or a portion near the end. Thereby, since the amount of gas in the intermediate side passageway 2α flowing into and out of the intermediate pressure chamber due to the pressure fluctuation of the intermediate pressure chamber can be reduced, the swelling of the acupressure diagram caused by this can be reduced, and the total adiabatic efficiency can be reduced. There is an effect that it can be improved.

Next, a fourth embodiment will be described with reference to a longitudinal sectional view near the pressure difference control valve in FIG. The third embodiment is the same as the third embodiment except that the cylindrical groove 2γ and the suction-side conduction path 2i are provided between the cylindrical groove 2γ and the communication groove 2δ, so that the description of the structure, operation, and effects of the other parts is omitted. By providing the cylindrical groove 100p, the timing of conduction between the suction-side conduction path 2i and the back-side conduction path 2β can be accurately defined, so that there is a unique effect that variation in the excessive intermediate pressure value during mass production can be reduced. Further, the opening position of the suction side flow passage 2i on the suction chamber side is defined as a communication groove 2δ. Since the pressure fluctuation in the communication groove 2δ due to one rotation of the shaft 12 is smaller than the pressure fluctuation in the other part in the compression chamber 60, the suction-side conduction path 2
There is a unique effect that the flow rate therethrough during the conduction between i and the back side conduction path 2β does not fluctuate in an unstable manner, and the controllability of the differential pressure control valve 100 can be improved.

Next, a fifth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a Q portion in FIGS. 7, 11 and 12) of the pressure difference control valve in the vicinity of the back pressure chamber of FIG. The first, the third and the fourth except that the opening of the back side conduction path 2β on the side of the turning side surface area 67 is removed from the peripheral groove 2c, and the end plate 3a is intermittently closed. Since this embodiment is the same as the embodiment, the description of the structure, operation and effect of the other parts will be omitted. Immediately after the compressor is started, at the moment when the orbiting scroll member 3 starts to be pressed against the fixed scroll member 2, the surface of the end plate 3a on the lap side of the end plate 3a, which is the flow path through which the fluid escapes from the orbiting side surface region 67, and the non-orbiting reference. Face 2
Since the gap u is instantaneously shut off, the pressure in the turning side surface area 67 increases at a stretch.

When the opening on the side of the turning side surface 67 of the back side conduction path 2β is provided in the peripheral groove 2c, an impact force is applied to the valve body 100a due to the rapid pressure increase, and the valve body 100a The phenomenon that the orbiting scroll member 3 separates from the fixed scroll member 2 again easily occurs because the gas is excessively removed due to excessive movement and the attractive force is reduced. In rare cases, this phenomenon is repeated, in which case it takes a long time to shift to the normal operating state, or in the worst case, there is a risk that the normal operating state cannot be transferred.

On the other hand, in the present embodiment, the intermittent closing of the opening by the end plate 3a causes
The pressure change speed and the pressure change amount within α are reduced, the excessive movement of the valve body 100a is suppressed, the gas does not escape too much, and the orbiting scroll member 3 is stably pressed against the fixed scroll member 2. . As a result, there is a specific effect that the orbiting scroll member 3 of the compressor can always be smoothly shifted to the normal operation state in which the orbiting scroll member 3 is pressed against the fixed scroll member 2.

Next, a sixth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion P in FIGS. 7, 11 and 12) of the vicinity of the back pressure chamber of the pressure difference control valve in FIG. The opening of the back side conduction path 2β on the side of the turning side surface area 67 is connected to the peripheral groove 2
c, except that the flow path resistance between the back side conduction path 2β and the peripheral groove 2c is between the first embodiment and the fifth embodiment. Since it is the same as the fifth embodiment, the description of the structure, operation, and effects of the other parts will be omitted. Immediately after the start of the compressor, at the moment when the orbiting scroll member 3 starts to be pressed against the fixed scroll member 2, the opening is not closed by the end plate 3 a,
The throttle portion 2γ reduces the pressure change speed and the pressure change amount in the intermediate-side passageway 2α, suppresses excessive movement of the valve body 100a, does not cause too much gas to escape, and the orbiting scroll member 3 It is stably pressed against the fixed scroll member 2. As a result, there is a specific effect that the orbiting scroll member 3 of the compressor can always be smoothly shifted to the normal operation state in which the orbiting scroll member 3 is pressed against the fixed scroll member 2.

Further, since the pressure of the revolving side surface area 67 is constantly applied to the valve element 100a, the operation of the valve element 100a after shifting to the normal operation state becomes smooth. There is a specific effect that controllability is improved.

Next, a seventh embodiment will be described with reference to a longitudinal sectional view of the vicinity of the bypass valve in FIG. 15 (an enlarged view of a portion R in FIG. 1). This is the same as the first to sixth embodiments except that the end plate 2a of the fixed scroll member 2 is provided with the bypass digging 2ω into which the bypass valve 23 enters. Therefore, the description of the structure, operation and effect of the other parts will be omitted. As a result, the length of the bypass hole 2e is reduced, and the volume of the hole is accordingly reduced. As shown in FIG. 5, since the compression chamber 6 moves from the periphery of the scroll wrap toward the center, the bypass hole 2 e provided in the fixed scroll member and fixed and not moved is provided in the suction chamber 60 or the compression reduced to a certain volume. After communication with the chamber 6, the communication with the compression chamber 6 is interrupted at a point in time when a certain volume reduction occurs and the pressure increases accordingly. Then, the compression-chamber-side opening of the bypass hole 2e is closed by the tooth top surface of the scroll wrap 3b until it communicates with the one outer compression chamber 6 that moves from its surroundings thereafter.

For this reason, under conditions other than the condition where the bypass valve 23 is already operated when the communication between the compression chamber 6 and the bypass hole 2e is started, the pressure of the gas or oil confined in the bypass hole 2e is as described above. If the sealability of the scroll wrap 3b by the tooth tip surface is perfect, the height at the time when the communication with the compression chamber 6 is interrupted by the bypass hole 2e is maintained, except for the pressure increase due to heating. If the tip surface leaks, the pressure may slightly decrease or slightly increase depending on the case. However, the pressure of the gas or oil trapped in the bypass hole 2e increases.
It is still a high level.

Therefore, under conditions other than the condition where the bypass valve 23 is already operated at the time when the communication between the compression chamber 6 and the bypass hole 2e is started, when the bypass hole 2e starts to communicate with the compression chamber 6, the inside of the bypass hole 2e is A phenomenon occurs in which the gas or oil trapped in the air blows out to the compression chamber 6. This is a substantial endoleak and causes performance degradation. Therefore,
As in the present embodiment, if the volume of the bypass hole 2e is small, the amount of air blown out is reduced, so that there is a specific effect that the performance degradation can be suppressed.

Next, an eighth embodiment will be described with reference to a longitudinal sectional view of the fixed back chamber 61 near the bypass valve in FIG. 16 (an enlarged view of the R section in FIG. 1 on the fixed back chamber side). Except that a bypass hole chamfer 2ε is provided on the bypass valve 23 side of the bypass hole 2e, it is the same as the first to seventh embodiments.
The description of the structure, operation, and effects of the other parts is omitted. The pressure distribution on the bypass valve seal surface 2λ changes depending on the operation state of the bypass valve 23 and is uncertain. Therefore, when the pressure at this location is much lower than the surrounding pressure, the pressure in the bypass hole 2e is
1 until the pressure is significantly higher than
Does not open, it is difficult to suppress overcompression, and performance under overcompression conditions is reduced.

Conversely, if the pressure at this location is significantly higher than the surrounding pressure, the bypass valve 23 is opened when the pressure in the bypass hole 2e is significantly lower than the pressure in the fixed back chamber 61. As a result, backflow from the fixed rear chamber 61 to the compression chamber 6 occurs, causing substantial internal leakage and deteriorating performance. By providing the bypass hole chamfer 2ε, the area of the bypass valve sealing surface 2λ, which is an uncertain part of the pressure distribution, can be reduced. There is a specific effect that it becomes smaller. here,
When the discharge pressure is low, the area of the sealing surface is small,
The danger that the sealing performance is reduced increases.

As a countermeasure, the bypass valve plate 23x
17 has a curved shape when viewed from the side rather than the plane, and FIG.
It is good to fix to a fixed scroll so that a concave part may come to the fixed scroll side as shown in FIG. (Here, FIG. 17 shows an extremely bent bypass valve plate 2 for ease of explanation.
3x, and the actual bending is smaller than that in FIG. This allows the bypass valve plate 23x to be constantly pressed against the bypass valve sealing surface 2λ by its own spring force, so that even when the discharge pressure is low, a stable sealing property can be ensured, and leakage from there is suppressed. There is a specific effect that the performance is improved by being performed. Conversely, when the fixed scroll is fixed to the fixed scroll so that the convex portion comes to the fixed scroll side, an effect of suppressing over-compression due to flow path resistance when the bypass valve is opened appears.

Next, a ninth embodiment will be described with reference to a longitudinal sectional view of the fixed rear chamber side near the bypass valve in FIG. 18 (an enlarged view of the R section in FIG. 1 on the fixed rear chamber side). Except that a bypass valve sealing line 2τ having a hemispherical cross section is provided in order to make the sealing portion of the bypass valve linear, the structure, operation, and effects of the other portions are not described. Omitted. This is considered to be the limit of the means for reducing the area of the sealing surface performed in the eighth embodiment, and the effect is the same as that of the eighth embodiment. Further, the method shown in FIG. 17 is also effective in reducing the sealing property, which is a disadvantage of this means.

Next, a tenth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion R in FIG. 1) near the bypass valve in FIG.
A description will be given based on a vertical cross-sectional view of the cylindrical retainer No. 0. Since the configuration is the same as that of the first to ninth embodiments except that the bypass valve is configured differently from the reed valve, the description of the configuration, operation, and effects of the other parts is omitted.

First, the configuration will be described. The bypass hole 2
A cylindrical dug 2σ for arranging the circular bypass valve plate 23y is provided on the fixed back chamber 61 side of e, and a bypass valve seal surface 2λ is provided at the bottom thereof. An enlarged portion 2ρ is provided on the fixed rear chamber 61 side of the cylindrical dug 2σ. The circular bypass valve plate 23y is inserted into the cylindrical dug 2σ, the cylindrical retainer 23b is inserted, and fixedly disposed on the fixed scroll member 2. A bypass valve stopper surface 23c is provided on the compression chamber 6 side of the cylindrical retainer 23b, and a central discharge hole 23e is provided at the center thereof, and one or a plurality of peripheral discharge holes 23f are provided therearound. The total cross-sectional area of these holes is approximately equal to or larger than the cross-sectional area of the bypass hole 2e. At this time, the insertion depth is defined by the stepped portion of the enlarged portion 2ρ,
There is a unique effect that the assemblability at the time of insertion is good. Here, the bypass valve stopper surface 23c defines a maximum distance at which the circular bypass valve plate 23y is separated from the bypass valve seal surface 2λ.

The maximum distance may be set according to the following equation in order to secure a cross-sectional area of about the cross-sectional area of the bypass hole 2e or more. If the bypass hole diameter is D, the maximum distance L is

[0084]

[Number 2] and L ≒ or> value indicated by ^{(πD 2/4) / πD} = D / 4. In addition, as for the fixed arrangement method of the cylindrical retainer 23b, press fitting is common. Further, a method is also conceivable in which tapered screws are provided on the outer peripheral portion of the enlarged portion 2ρ and the outer periphery of the cylindrical retainer 23b, and are fixedly arranged by screwing them. However, if press fitting or screwing is performed, there is a risk that the fixed scroll member 2 is deformed.

In order to avoid this, adhesion is conceivable. Further, as shown by a two-dot chain line, an outer peripheral excavation 23g is provided near the outer periphery to reduce the rigidity of the outer peripheral surface of the cylindrical retainer 23b, and to reduce the rigidity of the fixed scroll member 2 caused by press-fitting.
A method of avoiding deformation of the fixed scroll member 2 by reducing the applied force is also conceivable. By these methods,
Deformation of the fixed scroll member 2 is suppressed or eliminated, and the management of the gap between the scroll wraps is facilitated, and there is a unique effect that the variation in performance during mass production is small.

Next, the operation will be described. Usually, the circular bypass valve plate 23x has the bypass valve stopper surface 2
The fixed rear chamber 6 having substantially the discharge pressure applied to the surface on the 3c side.
Since the pressure of 1 is higher than the pressure of the compression chamber applied to the other surface, it is pressed against the seal surface 2λ of the bypass valve, and the bypass valve 23 is closed. However, under the over-compression condition, the pressure in the compression chamber tends to be higher than the discharge pressure.
x moves away from the bypass valve sealing surface 2λ, and the bypass valve 23 opens. Therefore, the compression chamber and the fixed rear chamber 61
And the fluid flows out of the compression chamber. This bleeding continues until the pressure in the compression chamber becomes the same level as or lower than the pressure in the fixed rear chamber 61.

As described above, the bypass valve 23 serves as a control bypass for controlling the pressure in the compression chamber to be suppressed from becoming higher than the discharge pressure. This bypass valve 23 can reduce the volume of the bypass hole only by providing a digging small enough to arrange a very small circular bypass valve which is slightly larger than the diameter of the bypass hole by a seal portion or the like. There is no need to provide a large digging as in the seventh embodiment.

Therefore, since the strength of the end plate 2a of the fixed scroll member 2 is suppressed and the amount of gas or oil trapped in the bypass hole blown out to the compression chamber can be suppressed, the deformation of the fixed scroll member can be reduced. There is a specific effect that the gap between the wraps can be kept small, and the substantial internal leakage due to the blowing of the gas or oil into the compression chamber can be suppressed, and the performance can be improved.

In the bypass valve of the reed valve type in the embodiments described above, the greater the degree of opening, the greater the force in the closing direction due to the elasticity of the bypass valve itself. However, there is a disadvantage that the flow path resistance increases and overcompression is difficult to suppress. In this embodiment, since the bypass valve itself has no elasticity, no closing force is generated by the valve even if the opening degree is large. Therefore, since there is no force that hinders the opening operation of the bypass valve, overcompression is easily suppressed, and there is also a specific effect that performance is improved.

Next, an eleventh embodiment will be described with reference to a longitudinal sectional view of the vicinity of the bypass valve in FIG. 21 (an enlarged view of a portion R in FIG. 1). Except that the bypass hole chamfering 2ε is provided on the bypass valve side of the bypass hole 2e, it is the same as the tenth embodiment, and the description of the structure, operation, and effects of the other parts is omitted. The pressure distribution on the bypass valve seal surface 2λ changes depending on the operation state of the bypass valve 23 and is uncertain.
Therefore, when the pressure at this location is significantly lower than the surrounding pressure, the bypass valve 23 does not open until the pressure in the bypass hole 2e becomes significantly higher than the pressure of the fixed back chamber 61, It becomes difficult to suppress overcompression, and performance under overcompression conditions decreases.

Conversely, when the pressure at this point is significantly higher than the surrounding pressure, the bypass valve 23 is opened when the pressure in the bypass hole 2e is significantly lower than the pressure in the fixed back chamber 61. As a result, backflow from the fixed rear chamber 61 to the compression chamber 6 occurs, causing substantial internal leakage and deteriorating performance. By providing the bypass hole chamfer 2ε, the area of the bypass valve sealing surface 2λ, which is an uncertain part of the pressure distribution, can be reduced. There is a specific effect that it becomes smaller.

Next, a twelfth embodiment will be described with reference to a longitudinal sectional view of the vicinity of the bypass valve in FIG. 22 (an enlarged view of a portion R in FIG. 1). Except that a bypass valve seal line 2τ having a hemispherical cross section is provided in order to make the bypass valve seal portion linear, the structure, operation, and effects of the other portions are not described because they are the same as in the tenth embodiment. I do. This is considered to be the limit of the means for reducing the area of the sealing surface performed in the eleventh embodiment, and the effect is the same as that of the eleventh embodiment. It is even larger than in the example.

Next, a thirteenth embodiment will be described with reference to a plan view of a circular bypass valve plate shown in FIG. Seal part or seal line of bypass valve plate (hatched area in FIG. 23)
Except for the provision of the plurality of valve body flow paths 23i outside the above, the structure is the same as that of the tenth to twelfth embodiments, and the description of the structure, operation, and effects of other parts is omitted. Thereby, the flow path cross-sectional area extending from the seal side of the valve body to the stopper surface side can be enlarged while securing the seal portion, and thus there is a specific effect that the overcompression loss can be further reduced. Here, the diameter of the outer periphery of the circular bypass valve plate 23y may be close to the cylindrical excavation 2σ.

In this way, the movement of the valve element in the direction perpendicular to the central axis direction of the cylindrical digging 2σ is restricted, and the movement of the valve element in the central axis direction becomes smooth. Can be further suppressed, and there is a specific effect that performance is improved. The valve body of FIG. 24 is better than the valve body of FIG.
Since the area of the valve element passage is large and the passage resistance is small, there is a specific effect that the overcompression loss can be further suppressed and the performance is improved. When the diameter of the outer periphery is close to the cylindrical dug 2σ, the sliding area at that portion is small.
Friction is small, and the movement of the valve element in the direction of the central axis is further smoothed, overcompression loss can be further suppressed, and performance is further improved.

Next, a fourteenth embodiment will be described with reference to a longitudinal sectional view of a circular bypass valve plate 23y of FIG. The thirteenth embodiment differs from the thirteenth embodiment in that the diameter of the outer periphery is close to the diameter of the cylindrical dug 2σ except that an outer peripheral projection 23j is provided on the outer periphery of the bypass valve stopper surface side of the circular bypass valve plate 23y. Therefore, the description of the structure, operation, and effects of the other parts is omitted. Thus, even if the circular bypass valve plate 23y attempts to rotate around an axis perpendicular to the axial direction, the circular bypass valve plate 23y can hardly rotate due to the presence of the outer peripheral projection 23j, and the posture of the circular bypass valve 23b is further increased. There is a specific effect that the operation is stabilized, the operation in the axial direction is ensured, the overcompression loss is further suppressed, and the performance is further improved.

The outer peripheral projection 23j serves as a rib for increasing the rigidity of the circular bypass valve plate 23y. Therefore, the thickness of the valve body can be reduced even with the same rigidity, so that the weight is reduced. As a result, the responsiveness of the opening / closing operation of the bypass valve 23 can be improved, and there is a specific effect that the excessive compression loss is further suppressed and the performance is further improved. Here, the valve element flow path 2
Of course, the flow path resistance may be further reduced by bringing the 3i into the inside of the outer peripheral projection 23j and bringing it to the X line. Further, the outer peripheral projection 23j may be provided on the seal surface side. In this case, the height and inner diameter of the protrusion are set to the bypass valve sealing surface 2λ or the bypass valve sealing line 2τ.
So as not to interfere with the base of the

Next, a fifteenth embodiment will be described with reference to a longitudinal sectional view of a conical bypass valve element shown in FIG. When the conical bypass valve body 23z and the fixed scroll member 2 have the bypass valve sealing surface 2λ, they are the same as the fourteenth embodiment except that they have a conical shape. I do. Thereby, since the flow on the seal surface or the seal line when the bypass valve is opened becomes smooth, there is a specific effect that the overcompression loss is further suppressed and the performance is further improved. Here, the conical surfaces of the valve body and the sealing surface may be spherical surfaces as shown in FIG. In this way, the sealing is performed even if the valve body is tilted, so that there is a unique effect that the leakage at the time of closing the bypass valve can be reliably avoided. Also, this conical bypass valve body 23z
May be an aluminum alloy or a plastic material having a small specific gravity. Thereby, the weight can be reduced, the responsiveness of the opening / closing operation of the bypass valve 23 can be improved, the overcompression loss is further suppressed, and the performance is further improved.

Next, a sixteenth embodiment will be described with reference to a longitudinal sectional view of a cylindrical retainer shown in FIG. Except that the portion including the bypass valve stopper surface 23c of the cylindrical retainer 23b is a separate stopper portion 23w made of a material softer than metal such as plastic, the same as in the tenth to fifteenth embodiments, the other portions are the same. The description of the structure, operation, and effects of is omitted. Thereby, there is a specific effect that the sound when the valve body collides with the bypass valve stopper surface 23c when the bypass valve is opened can be reduced. This separate stopper portion 23w may be insert-molded or bonded to another portion of the cylindrical retainer 23b. The entire cylindrical retainer 23b may be made of a material such as plastic, which is more flexible than metal.

Next, a seventeenth embodiment will be described with reference to a longitudinal sectional view of a cylindrical retainer shown in FIG. The cylindrical retainer is the same as the tenth to fifteenth embodiments except that the thickness of the entire region is approximately constant, which is suitable for press molding. Therefore, the description of the structure, operation, and effects of other parts is omitted. I do. Accordingly, there is a specific effect that the processing cost can be reduced when processing is performed by press molding. Also,
Since the rigidity of the cylindrical retainer 23b is small, when the press-fitting is performed on the fixed scroll member 2, even if the press-fitting allowance is excessively large, the fixed scroll member 2 is not deformed so as to deteriorate the performance, and is low. There is a unique effect that mass production can be performed with processing accuracy and processing cost can be reduced.

Next, an eighteenth embodiment will be described with reference to an enlarged longitudinal sectional view of a main part of the bypass valve 23 shown in FIG. Except that a bypass spring 23k is provided between the cylindrical retainer 23b and the circular bypass valve plate 23x or the conical valve body 23z, the structure is the same as that of the tenth to seventeenth embodiments. Description is omitted.

When the bypass spring 23k is used as a compression spring, the valve bodies 23x and 23z are pressed against the bypass valve seal surface 2λ or the bypass valve seal line 2τ when the bypass valve 23 is closed. There is a specific effect that the performance is improved, the internal leakage is reduced, and the performance is improved.

By the way, one end of the bypass spring 23k and the valve bodies 23x and 23z, and the other end of the bypass spring 23k and the cylindrical retainer 23b are fixed, and when the bypass valve 23 is closed, it is slightly pulled. The natural length of the bypass spring 23k may be set so as to be as follows. The control bypass realized by this is opened slightly before the pressure of the compression chamber reaches the discharge pressure.

In the control bypass described in the previous embodiments, since the flow passage cross-sectional area at the start of opening of the bypass is small, there is no flow in the control bypass sufficient to avoid over-compression, and the over-compression is considerably large. In addition, performance degradation due to over-compression loss under over-compression conditions was caused, and this was also a factor in increasing the setting of the over-intermediate pressure value, resulting in performance degradation due to an increase in the urging force under under-compression conditions. As shown here, by forming the control bypass with a tension spring, the control bypass is opened slightly before the pressure of the compression chamber reaches the discharge pressure, so that the compression chamber pressure and the discharge pressure are the same. At times, the flow passage cross-sectional area of the bypass is large, so that excessive compression can be greatly reduced. As a result, under the over-compression condition, the performance can be improved by reducing the over-compression loss, and since the set value of the over-intermediate pressure value can be reduced, the performance can be improved by reducing the urging force under the under-compression condition. effective.

When the valve body has an outer peripheral projection 23j, the bypass spring 2 is provided on the inner periphery of the outer peripheral projection 23j.
The shape may be such that 3k is just loosely press-fitted. As a result, the center axis of the bypass spring 23k and the center axis of the valve body can always be aligned, so that the amount of contraction or expansion of the bypass spring 23k when the bypass valve 23 is closed is always constant. Thus, there is a specific effect that the condition for opening the bypass valve is constant and stable performance can be realized. In particular, it is more preferable that the height of the outer peripheral projection 23j is equal to or larger than the radius of the element wire of the bypass spring 23k and approximately equal to the diameter. In this case, since the valve body and the bypass spring 23k can be connected to each other without substantially hindering the expansion and contraction of the bypass spring 23k, the spring constant during operation can be kept substantially constant at all times, and the operation reliability of the bypass valve 23 is ensured. There is a special effect that it can be done.

As shown in FIG. 31, a bypass spring 23k is provided in the bypass hole 2e side of the valve body, contrary to the embodiment of FIG.
May be provided. At this time, the same effect can be obtained by using the setting state of the bypass spring 23k, contrary to the embodiment of FIG.

Next, a nineteenth embodiment will be described with reference to an enlarged vertical sectional view of the surface of the central projection of the cylindrical retainer shown in FIG. The structure is the same as that of the eighteenth embodiment except that the central protruding portion 23p is tapered so that the center protruding portion 23p becomes thinner toward the front end, so that the description of the structure, operation, and effects of the other portions is omitted. Accordingly, the cylindrical retainer 23b and the bypass spring 23k can be connected without obstructing the expansion and contraction of the bypass spring 23k. Therefore, the spring constant during operation can be kept substantially constant at all times, and the operation of the bypass valve 23 can be reliably performed. There is a specific effect that it can be secured. Further, as shown in FIG. 33, a spring groove 23q into which a ring at the end of the bypass spring 23k fits may be provided at the base of the central projection 23p. With this configuration, since the posture of the bypass spring 23k is stabilized, there is a unique effect that the operation of the bypass valve 23 is further ensured.

Next, a twentieth embodiment will be described with reference to a longitudinal sectional view (enlarged view of a portion R in FIG. 1) near the bypass valve in FIG. 34 and a plan view of a self-spring circular bypass valve plate 23m in FIG. It will be described based on the following. Since the parts other than those shown in these figures are the same as those of the tenth to nineteenth embodiments, the description of the structure, operation and effect of the other parts will be omitted. The self-spring circular bypass valve plate 23m has a structure in which a surrounding valve sandwiching portion 23t and a central circular valve body 23r are connected by four radial valve holding portions 23s. A cylindrical dug 2σ is provided on the side opposite to the lap of the bypass hole 2e.

On the bottom, a fixed sandwiching surface 2
θ, a bypass valve sealing surface 2λ or a bypass valve sealing line 2τ is formed at the center, and these are made substantially the same surface. The self-spring type circular bypass valve plate 23
m, the valve sandwiching portion 23t is placed on the fixed sandwiching surface 2θ, and the valve body 23r is further placed on the bypass valve seal surface 2λ. Then, the retainer 23u with a spring retainer is press-fitted or bonded to the cylindrical digging 2σ,
By pressing the valve pinching portion 23t on the bottom surface of the outer periphery,
The self-spring circular bypass valve plate 23m is fixedly arranged,
A bypass valve 23 is formed. The retainer with spring retainer 23u includes the cylindrical retainer 2 used in the above-described embodiment.
Either or both of the central discharge hole 23e and the peripheral discharge hole 23f, and the bypass valve stopper surface 23c, which have the same function as that of the valve 3b, are provided.

As a result, the elasticity of the radial valve holding portion 23s incorporated in the valve body allows the bypass valve 23 to be opened after the bypass valve 23 is opened, without providing a separate spring from the valve body as in the above-described embodiment. There is a specific effect that the certainty of the operation when closing again can be improved. Here, the number of the radial valve holding portions is four, but any number may be used. In particular, the self-spring type circular bypass valve plate 23
It is even better if the shape has a straight line which is symmetrical with a straight line passing through the center of m. Thus, even when the bypass valve 23 is opened, the posture of the valve body 23r is substantially parallel to the bypass valve sealing surface 2λ. Therefore, since the flow of the gas flowing out of the bypass hole 2e to the cylindrical digging 2σ is not biased, the flow path resistance is reduced, the overcompression loss can be further reduced, and the performance can be improved.

The fixed sandwiching surface 2θ may be shallower than the bypass valve sealing surface 2λ. In this case, the same operation as in the eighteenth embodiment when the bypass spring is used in a tensioned state is produced. Therefore, under the over-compression condition, the performance can be improved by reducing the over-compression loss, and the setting value of the over-intermediate pressure value can be reduced. There is. In addition, the fixed sandwiching surface 2
θ may be deeper than the bypass valve sealing surface 2λ.
In this case, the same operation as in the eighteenth embodiment when the bypass spring is used in a compressed state is produced. Therefore, there is a specific effect that the internal leakage is reduced and the performance is improved.

Next, the twenty-first embodiment will be described with reference to FIGS.
A description will be given based on a plan view of the self-spring circular bypass valve plate 23m shown in FIG. The same as in the twentieth embodiment except that the valve pinching portion 23t and the central circular valve body 23r are connected by two, three, and four maze-shaped valve holding portions 23n, respectively. The description of the structure, operation, and effects is omitted. The rigidity in the direction perpendicular to the plane of the maze-shaped valve holding portion 23n can be designed to be considerably smaller than that of the radial valve holding portion 23s of the twentieth embodiment. Are equally large.
The former stiffness is necessary to give an opportunity to shift to an operation of closing after the bypass valve 23 opens, and the smaller the better, the better. On the other hand, the latter rigidity is necessary for always returning the valve body 23r to the normal position on the bypass valve seal surface 2λ or the bypass valve seal line 2τ, and the greater the rigidity, the better. Thus, there is a specific effect that the operation of the bypass valve can be made closer to ideal.

Next, a twenty-second embodiment will be described with reference to a longitudinal sectional view of the orbiting scroll member 3 shown in FIG. 39 and the differential pressure control valve 10 shown in FIG.
The description will be made based on a vertical cross-sectional view of FIG. FIG. 1 without the differential pressure control valve in the P section in FIG. 1
39 and 40 are the same as those of the first and second embodiments and the fifth to twenty-first embodiments except for the portions shown in FIGS. 39 and 40, and therefore the description of the structure, operation, and effects of other portions is omitted. I do. A valve hole 3f is provided on the back intermediate pressure region 99 side of the end plate 3a of the orbiting scroll member 3, and a spring positioning projection 3h and an intermediate conduction path 3α are provided at the bottom thereof. Here, the intermediate-side conduction path 3α opens at the tooth bottom of the orbiting scroll member 3 in which the intermediate pressure chamber 68 is formed.

After inserting the differential pressure valve spring 100c and the valve body 100a into the valve hole 3f, the valve hole 3f is covered with a valve seal member 100i having a valve seal surface 100j and a through hole 100β which is a through hole. I do. Here, the valve seal member 100i is fixedly arranged on the orbiting scroll member 3 by press-fitting or bonding. Since the valve seal member has an outer peripheral excavation of 100 m, even if the valve seal member 100i is pressed into the orbiting scroll member 3, the orbiting scroll member 3 hardly deforms. Although the differential pressure control valve 100 formed in this way has a difference that it is formed on the orbiting scroll member 3, it performs exactly the same operation as the differential pressure control valve of the first embodiment (therefore, the same name). Therefore, the description of the operation and effect thereof will be omitted. In this embodiment, there is a specific effect that the structure of the intermediate side conduction path 3α is simplified.

When the intermediate side passage 3α is provided not in the intermediate pressure chamber 68 but in the suction chamber 60 (FIG.
9 (an enlarged view of the portion V). At this time, the pressure in the back intermediate pressure region is set to a pressure that is approximately a fixed value higher than the suction pressure, that is, the back excessive suction pressure, and the effect and the like are the same as in the case of the back excessive intermediate pressure.

Next, according to the present invention, the non-orbiting scroll member is made movable in the axial direction, and the rear intermediate pressure region is provided on the side of the end plate opposite to the compression chamber so that the non-orbiting scroll member can be operated within the required operating pressure condition range. The twenty-third embodiment implemented in a vertically mounted non-orbiting float scroll compressor in which the scroll support member is mainly a orbiting scroll member, that is, a non-orbiting scroll member is pressed against the orbiting scroll member, FIG. This will be described with reference to FIGS. 41 is a longitudinal sectional view of the compressor, FIG. 42 is a longitudinal sectional view near the differential pressure control valve (an enlarged view of a portion P in FIG. 41), FIG. 43 is a plan view of a valve element of the differential pressure control valve, and FIG. FIG. 45 is a cross-sectional view of the spring attitude holding cylinder, FIG. 45 is a top view when the upper casing and the pressure partition are removed, and FIG. 46 is an enlarged view of the central portion of the upper surface of the non-orbiting scroll member.

First, the structure will be described.

In the orbiting scroll member 3, a scroll wrap 3b is erected on a head plate 3a, and a bearing holder 3s in which orbital grooves 3g and 3h and a orbital bearing 3w are press-fitted is provided on the back surface thereof.
And a thrust surface 3d.

In the non-orbiting scroll member 2, a scroll wrap 2b is provided upright on a head plate 2a, and a central base 2w is provided at a central portion on the back surface thereof. . A bypass valve 23x and a retainer 23a, which are reed valve plates, are fixed to the bypass hole 2e with a bypass screw 23h, and a bypass valve 23 is provided. A seal groove 2s is provided around the center base 2w. An outer peripheral projection 2t is provided near the outer periphery of the rear surface, and a rear concave portion 2x is provided between the outer peripheral protrusion 2t and the central base 2w.

Then, a valve hole 2f is dug into the rear recess 2x, and from the bottom thereof, the intermediate pressure chamber 6 on the scroll wrap side is formed.
8, the intermediate side conduction path 2α is opened. A spring positioning projection 21 is provided at the bottom of the valve hole 2f. Here, the valve hole 2f
Incorporates a differential pressure control valve 100 described below. First, a spring attitude holding cylinder 100p made of plastic or the like and provided with a flow longitudinal groove 100q on the inner periphery is press-fitted or bonded. Next, the spring positioning projection 2 at the bottom of the valve hole 2f
1, a differential pressure valve spring 100c is inserted, and a valve body 100a provided with a valve flow path 100r on the outer periphery is placed on the other end.

Then, the valve seal member 100i having the valve seal surface 100j and the back-side conduction path 100β is connected to the valve hole 2
f, press-fitting, bonding or welding to the enlarged valve hole portion 2y.
At this time, the differential pressure valve spring 100c is compressed, and presses the valve body 100a against the valve seal surface 100j. Since this pressing force determines an excessive intermediate pressure value, the depth of the valve hole 2f, the depth of the valve hole enlarged portion 2y, the spring constant of the differential pressure valve spring 100c, the natural length, and the axial direction, which are dimensions for determining the intermediate pressure value, are determined. The orthogonality at both ends must be managed accurately.

The frame 4 has a plurality of projecting scroll mounting portions 4 on the outer peripheral portion of which the non-orbiting scroll member 2 is mounted via a plate-shaped scroll mounting spring 75.
and a sliding thrust bearing 4g and frame Oldham grooves 4e and 4f (both not shown) are provided on the inside thereof. A plurality of suction grooves 4r are provided on the outer peripheral portion. The sliding thrust bearing 4g is provided with an annular or radial oil groove 4i in the radial direction. 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 discharge path 4s is provided to pass from the lowest part of the upper surface of the frame 4 to the lower surface of the frame. The shaft seal 4a and the main bearing 4
A lateral hole 4n is opened from the side of the frame toward the space between m.

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

The pressure partition 74 has a discharge opening 7 at the center.
4c, an inner peripheral seal groove 74a is provided below the inner peripheral portion, and an outer peripheral seal groove 74b is provided near the center of the lower surface. A flow path 74d between the back and the discharge is provided with a throttle that communicates the lower surface and the upper surface between the two seal grooves. Here, another piece having a small diameter hole is press-fitted and formed.

The shaft 12 has a shaft oil supply hole 1 inside.
2a, a main bearing lubrication hole 12b, a shaft seal lubrication hole 12c, and an auxiliary bearing lubrication hole 12i are provided. A bearing holding portion 12w having an enlarged diameter is provided at an upper portion thereof, and a shaft balance 49 is press-fitted therein. Further on the eccentric part 1
There is 2f.

Since the rotor 15 and the stator 16 are the same as those in the first known example, description thereof will be omitted.

These components are assembled as follows. First, the shaft 12 is inserted into the main bearing 4m of the frame 4, and the rotor 15 is fixed. Next, the Oldham ring 5 is inserted into the frame Oldham grooves 4e and 4f (both not shown) of the frame 4 so that the frame projections 5a and 5b (both not shown) of the Oldham ring 5 are inserted. And attach it.

Next, the orbiting scroll member 2 is inserted into the eccentric portion 12f of the shaft 12 by inserting the orbiting bearing 3w,
The rotating Oldham grooves 3g, 3h are inserted into the rotating protrusions 5c, 5d of the Oldham ring 5, and the frame 4
The thrust surface 3d is mounted on the sliding thrust bearing 4g, and incorporated.

Next, the non-orbiting scroll member 2 in which the scroll mounting spring 75 is screwed in advance with three spring mounting screws 57 is moved so that the scroll wrap is engaged with the frame mounting portion 4q of the frame 4.
Place on top of While incorporating each element as described above, while rotating the shaft 12 or the rotor 15,
The non-orbiting scroll member 2 is fixed to the frame 4 by a cover screw 53.

Next, the cylindrical casing 3 to which the suction pipe 54 and the hermetic terminal 22 are welded in advance.
1, the stator 16 is shrink-fitted or press-fitted, and the motor wire 77 is inserted into the terminal inside the hermetic terminal 22.
After mounting, the bearing support plate 18 is press-fitted or welded. Then, the above-mentioned assembly part is inserted and the frame 4 is inserted.
Tack welding on the side of

Next, the bearing housing is assembled so that one end of the shaft 12 coming out of the hole at the center of the bearing support plate 18 is inserted into the 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 of the shaft 12, and the bearing housing 70 is spot-welded to the bearing support plate 18 at a position where the rotation torque is minimized. The shaft lubrication hole 12a is formed in the lower surface of the bearing housing 70.
A refueling pump 56 is provided so as to refuel. Also,
At this time, a motor chamber 62 is formed between the frame 4 and the bearing support plate 18. Then, the bottom casing 21 is welded to the cylindrical casing 31 to form an oil storage chamber 80.

Next, the inner peripheral seal groove 74a and the outer peripheral seal groove 74b of the
1 and cover the cylindrical casing 31 while inserting the outer peripheral seal 58. At this time, the non-orbiting scroll member 2
Between the inner peripheral seal 57 and the outer peripheral seal 58 on the upper surface of the upper surface of the non-orbiting scroll member 2.
Is provided. Then, the upper casing 20 to which the discharge pipe 55 is welded is further placed thereon and welded.
At this time, the area inside the inner peripheral seal 57 on the upper surface of the non-orbiting scroll member 2 becomes the back discharge pressure area 95 of the non-orbiting scroll member 2. A non-swirl rear chamber 61 is formed between the pressure partition wall 74 and the upper casing 20. In this state, a current is applied to the stator 16 to magnetize the permanent magnet 15b inside the rotor 15, thereby forming a motor 19. Finally, add the oil.

Next, the operation will be described.

The gas sucked into the suction chamber 60 from the suction pipe 54 is supplied to the orbiting scroll member 3.
Is compressed in the compression chamber 6 by the orbital movement of the scroll member, and is discharged from the discharge hole 2d to the non-orbiting rear chamber 61 above the non-orbiting scroll member 2. The gas exits the compressor through the discharge pipe 55.

The non-orbiting scroll member 2 receives a separating force in a direction away from the orbiting scroll member 3 due to the gas pressure inside the compression chamber 6, but the back excessive intermediate pressure region 99 and the back discharge pressure region 95. The orbiting scroll member 3 is pressed against the orbiting scroll member 3 by the attraction force due to the pressure from. Therefore, the urging force of the non-orbiting scroll member 2 is given from the orbiting scroll member 3.

On the other hand, the orbiting scroll member 3 has no attraction force, and obtains the urging force by the sliding thrust bearing on the orbiting back surface. As a result, the gap between the tooth tip and the tooth bottom of the scroll member is not enlarged, and the compression operation can be continued. Here, the pressure control method of the back excess intermediate pressure region 99 is as follows.
A discharge pressure is introduced from a discharge system by the discharge back surface flow path 74d with a throttle, and the pressure is controlled by the differential pressure control valve 100. This is different from the above-described embodiment only in that pressure is introduced by gas and oil passing through the bearing.

As a result, it is possible to perform a design considering only the introduction of pressure into the over-suction pressure region 99, so that an optimum design is possible. In addition, since the bypass valve 23 is also provided in the same manner as in the first to eighth embodiments, the combination thereof improves the compression efficiency with improved overall adiabatic efficiency and reliability over a wide operating range as in these embodiments. There is an effect that a machine can be provided. Further, since the projected area in the axial direction of the back discharge pressure region 95 is set to the size described in the first embodiment, the excessive intermediate pressure value can be set even smaller. There is an effect that efficiency and reliability can be improved.

The oil remaining at the bottom of the compressor is supplied to the orbiting bearing 12c by the oil supply pump 56 through the shaft oil supply hole 12a. In addition, the horizontal lubrication hole 1
The oil is supplied to the main bearing 4a via 2b. After the oil enters the turning back pressure chamber 11, a part of the oil enters the suction chamber 60 while sliding through the oil groove 4i and lubricating the thrust bearing 4, and the other passes through the oil discharge path 4s. After entering the motor chamber 62, it returns to the oil storage chamber 80.

The pressure bulkhead 74 forms a gas layer at the lower portion thereof, so that the heat from the high-temperature gas in the non-swirl back chamber 61 is prevented from being transmitted to the compression chamber 6. This has an effect peculiar to the present embodiment that a decrease in the total adiabatic efficiency due to this can be suppressed.

As a method for introducing pressure into the back intermediate pressure region 99, instead of providing the discharge back-to-back flow path 74d, a minute groove is provided in the inner peripheral seal 51 to reduce the sealing property. The non-swirl rear chamber 6 passing therethrough
A leak flow from one may be used. There is also a method of removing the inner peripheral seal 51 to form a clearance fit and managing the clearance.

Since the flow longitudinal groove 100q is provided on the inner periphery of the spring attitude holding cylinder 100p of the differential pressure control valve 100, the flow resistance of the gas or oil passing through the differential pressure control valve 100 is reduced. This has the unique effect of reducing the size and realizing reliable back pressure control.

Here, as shown in FIG. 54, the portion P in FIG. 41 of this embodiment is positioned at a position which does not always face the compression chamber which substantially closes the opening end of the intermediate side passageway 2α on the side of the intermediate pressure chamber. When provided in the suction chamber 60, the pressure in the rear intermediate pressure region 99 is controlled to the suction pressure + a fixed value. That is,
It can be seen that the means of the present embodiment is a basic means which, if developed, becomes the prior art. Therefore, the effects specific to the present embodiment described above and the effects specific to the embodiments described hereinafter are the same as the suction pressure +
This is also the effect of the prior art embodiment applying a constant pressure.

Next, a twenty-fourth embodiment will be described with reference to a longitudinal sectional view of the vicinity of the differential pressure control valve in FIG. 47 (an enlarged view of a portion P in FIG. 41). Except for once assembling the differential pressure control valve 100 inside the valve case 100n and then press-fitting or adhering it into the valve hole 2f of the non-orbiting scroll member 2, it is almost the same as the twenty-third embodiment. The description of the structure, operation, and effects of is omitted. Thus, the differential pressure control valve 100, which is a fine work, can be assembled separately from the compressor assembling, and there is a specific effect that the assemblability is improved. In addition, the spring positioning projection 21 of the twenty-third embodiment is eliminated, and the lower projection 100 having a small inner diameter is provided below the spring attitude holding cylinder 100p.
s is provided and the differential pressure valve spring 100c is fixed there. Therefore, even if the differential pressure valve spring 100c is compressed and its coil diameter is enlarged, the differential pressure valve spring 100c is more reliably secured.
c is positioned, so that the differential pressure control valve 10 has good controllability.
0 is realized.

Next, a twenty-fifth embodiment will be described with reference to a longitudinal sectional view of the fixed scroll member shown in FIG. 48 and a longitudinal sectional view of the vicinity of the bypass valve shown in FIG. 49 (an enlarged view of a portion T in FIG. 48). . The parts other than those shown in these figures are the same as those in the twenty-fourth embodiment, and the description of the structure, operation, and effects of the other parts will be omitted. Using a separate central base 43 which is separate from the central base of the non-orbiting scroll member 2, a cylindrical dug 2σ is provided at the bottom of the dug of the non-orbiting scroll member 2 in which the central base 43 is accommodated. A bypass valve 23 similar to the bypass valve in the eighteenth embodiment is provided inside the cylindrical dug 2σ.
Is configured.

After assembling the bypass valve 23, the separate center base 43 is set at an angle such that the cylindrical retainer 23b enters the retainer insertion dug 43a on the bottom surface.
The non-orbiting scroll member 2 is fixedly arranged. A bypass passage 43d leading to the non-swirl rear chamber 61 is opened in the retainer insertion dug 43a. At this time, the side face of the separate central base 43 is sealed by the base seal 59. As a result, in the non-orbiting float scroll compressor, the bypass valve as in the eighteenth embodiment can be set, and the same effect as that of the bypass valve at that time can be obtained. Here, since the separate central base portion 43 is provided with the retainer insertion dug 43a, this is
It serves as a positioning hole when the 3 is inserted into the non-orbiting scroll member, and has a specific effect that the assemblability is improved.

Finally, a twenty-sixth embodiment is a longitudinal sectional view of the vicinity of the differential pressure control valve shown in FIG. 50 (an enlarged view of a portion P in FIG. 41).
It will be described based on. Except that the hole of the cylindrical retainer 23b and the bypass passage provided in the separate central base portion 43 are eliminated, and the bypass groove 2z is provided, the structure is the same as that of the twenty-fifth embodiment, so the structure, operation, and The description of the effect is omitted. This facilitates formation of the flow path of the fluid that has passed through the bypass valve, and has a specific effect of improving workability.

[0146]

According to the present invention, there is an effect that it is possible to provide a scroll compressor which is high in total adiabatic efficiency and reliability and easy to use in a wide pressure operation range.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment.

FIG. 2 is a plan view of the fixed scroll member of FIG. 1 as viewed from a 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 an explanatory diagram of a region where a discharge pressure is applied according to 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 pressure difference control valve according to the first embodiment (an enlarged view of a portion P in FIG. 1).

FIG. 8 is a longitudinal sectional view of the vicinity of the back pressure chamber of the pressure difference control valve according to the first embodiment (an enlarged view of a portion Q in FIG. 7).

FIG. 9 is a diagram showing a pressure range in which operation is required when used as a refrigeration cycle compressor.

FIG. 10 is a vertical cross-sectional view of the vicinity of the pressure difference control valve according to the second embodiment (an enlarged view of a portion P in FIG. 1).

FIG. 11 is a vertical cross-sectional view of the vicinity of a pressure difference control valve according to a third embodiment (an enlarged view of a portion P in FIG. 1).

FIG. 12 is a vertical cross-sectional view of the vicinity of a pressure difference control valve according to a fourth embodiment (an enlarged view of a portion P in FIG. 1).

FIG. 13 is a longitudinal sectional view of the vicinity of a back pressure chamber of a pressure difference control valve according to a fifth embodiment (an enlarged view of a Q portion in FIGS. 7, 11, and 12).

FIG. 14 is a longitudinal sectional view of the vicinity of a back pressure chamber of a pressure difference control valve according to a sixth embodiment (an enlarged view of a Q portion in FIGS. 7, 11, and 12).

FIG. 15 is a vertical cross-sectional view of the vicinity of a bypass valve according to a seventh embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 16 is a vertical cross-sectional view of the fixed rear chamber side near the bypass valve according to the eighth embodiment (an enlarged view of the R section in FIG. 1 on the fixed rear chamber side).

FIG. 17 is a side view of a bypass valve according to a modified example of the eighth embodiment.

FIG. 18 is a vertical cross-sectional view of the fixed rear chamber side near the bypass valve according to the ninth embodiment (an enlarged view of the R section in FIG. 1 on the fixed rear chamber side).

FIG. 19 is a longitudinal sectional view of the vicinity of a bypass valve according to a tenth embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 20 is a longitudinal sectional view of a cylindrical retainer according to a tenth embodiment.

FIG. 21 is a longitudinal sectional view of the vicinity of a bypass valve according to an eleventh embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 22 is a longitudinal sectional view of the vicinity of a bypass valve according to a twelfth embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 23 is a plan view of a circular bypass valve plate according to a thirteenth embodiment.

FIG. 24 is a perspective view of a stopper member according to a thirteenth embodiment.

FIG. 25 is a longitudinal sectional view of a circular bypass valve plate according to a fourteenth embodiment.

FIG. 26 is a longitudinal sectional view of a conical bypass valve element according to a fifteenth embodiment.

FIG. 27 is a longitudinal sectional view of a bypass valve element according to a modification of the fifteenth embodiment.

FIG. 28 is a longitudinal sectional view of a cylindrical retainer 23b according to a modification of the sixteenth embodiment.

FIG. 29 is a longitudinal sectional view of a cylindrical retainer according to a seventeenth embodiment.

FIG. 30 is an enlarged longitudinal sectional view of a main part of a bypass valve according to an eighteenth embodiment.

FIG. 31 is an enlarged longitudinal sectional view of a main part of a bypass valve according to a modification of the eighteenth embodiment.

FIG. 32 is an enlarged vertical sectional view of the surface of the central projection of the cylindrical retainer according to the nineteenth embodiment.

FIG. 33 is an enlarged longitudinal sectional view of a main part of a bypass valve according to a nineteenth embodiment.

FIG. 34 is a vertical cross-sectional view of the vicinity of a bypass valve according to a twentieth embodiment (an enlarged view of a portion R in FIG. 1).

FIG. 35 is a plan view of a self-spring circular bypass valve plate according to a twentieth embodiment.

FIG. 36 is a plan view of a self-spring circular bypass valve plate according to a twenty-first embodiment.

FIG. 37 is a plan view of a self-spring circular bypass valve plate according to a modification of the twenty-first embodiment.

FIG. 38 is a plan view of a self-spring circular bypass valve plate according to a second modification of the twenty-first embodiment.

FIG. 39 is a longitudinal sectional view of the orbiting scroll member according to the twenty-second embodiment.

FIG. 40 is a longitudinal sectional view of the vicinity of the differential pressure control valve according to the twenty-second embodiment (an enlarged view of a portion T in FIG. 39).

FIG. 41 is a longitudinal sectional view of a twenty-third embodiment.

FIG. 42 is a longitudinal sectional view of the vicinity of the differential pressure control valve according to the twenty-third embodiment (an enlarged view of a portion P in FIG. 41).

FIG. 43 is a plan view of a valve body of a differential pressure control valve according to a twenty-third embodiment.

FIG. 44 is a cross-sectional view of the spring attitude holding cylinder of the twenty-third embodiment.

FIG. 45 is a top view of the twenty-third embodiment when the upper casing and the pressure partition are removed.

FIG. 46 is an enlarged view of the center of the upper surface of the non-orbiting scroll member according to the twenty-third embodiment.

FIG. 47 is a longitudinal sectional view of the vicinity of the differential pressure control valve according to the twenty-fourth embodiment (an enlarged view of a portion P in FIG. 41).

FIG. 48 is a longitudinal sectional view of a fixed scroll member of the twenty-fifth embodiment.

FIG. 49 is a longitudinal sectional view of the vicinity of the bypass valve according to the twenty-fifth embodiment (an enlarged view of a portion T in FIG. 48);

50 is a longitudinal sectional view of the vicinity of the bypass valve according to the twenty-sixth embodiment (an enlarged view of a portion T in FIG. 48).

FIG. 51 is a longitudinal sectional view of a conventional example.

FIG. 52 is a vertical cross-sectional view of the vicinity of the differential pressure control valve when a back over-suction pressure region which is the limit of the back over-intermediate pressure region is set (FIG. 1)
FIG.

FIG. 53 is a vertical cross-sectional view (an enlarged view of a portion P in FIG. 1) of the vicinity of the differential pressure control valve in another case in which a rear excessive suction pressure region which is the limit of the rear excessive intermediate pressure region is set.

FIG. 54 is a vertical cross-sectional view (an enlarged view of a portion P in FIG. 41) of the vicinity of the differential pressure control valve in another case where a rear excessive suction pressure region which is the limit of the rear excessive intermediate pressure region is set.

[Explanation of symbols]

2 ... fixed scroll member (non-orbiting scroll member), 2
e: bypass hole, 2i ... suction side conduction path, 2α ... middle side conduction path, 2β ... rear side conduction path, 2λ ... bypass valve sealing surface, 2τ ... bypass valve sealing line, 3 ... revolving scroll member, 3α ... middle side Conduction path, 4 ... frame, 5 ... Oldham ring, 6 ... compression chamber, 12 ... shaft, 19 ... motor,
23 ... bypass valve, 23x ... bypass valve plate, 23y ... circular bypass valve plate, 60 ... suction chamber, 61 ... fixed rear chamber (non-rotating rear chamber), 62 ... motor chamber, 67 ... rotating side area, 68 ... middle Pressure chamber, 95: Back discharge pressure area, 96 ...
Discharge chamber, 99 ... rear excessive intermediate pressure area (rear excessive suction pressure area),
100: differential pressure control valve, 100a: valve body, 100c: differential pressure valve spring, 100j: valve seal surface, 100β: back side conduction path,
100c: Differential pressure valve spring, 102: Flow path between discharge back surfaces.

Claims (1)

[Claims] An orbiting scroll member having a head plate and a spiral scroll wrap standing upright on the head plate, and orbiting in a plane perpendicular to the axial direction on which the scroll wrap stands up;
A non-orbiting scroll member that includes a head plate and a spiral scroll wrap standing upright and that is substantially restricted in at least a direction in a plane perpendicular to the axial direction is engaged, and the volume is substantially closed by being closed between the scroll members. Each of the scrolls has a pulling force in a direction of pulling the head plates of the scroll members against a separating force in a direction of pulling the head plates of the both scroll members apart due to the pressure of the fluid in the compression chamber. Means for applying an attractive force to a member, a scroll support member for generating a reaction force of an urging force, which is a vector sum of the attractive force and the separating force, to each of the scroll members, and introducing a fluid into the compression chamber. In a scroll compressor having a suction system and a discharge system that leads a fluid pressurized in the compression chamber to the outside, the orbiting scroll member At least a part of the attraction force applying means is a suction pressure, which is a pressure in the suction chamber, on the orbiting back surface, which is a surface of the end plate of the orbiting scroll member on the anti-compression chamber side, and a pressure in the discharge system. This is realized by providing a back-over-intermediate-pressure area for applying a pressure that is larger than the intermediate pressure between the discharge pressures by a fixed value within an error of about 20% of the intermediate pressure, and the pressure of the compression chamber is reduced within the discharge system. A scroll compressor comprising a pressure control means for suppressing a pressure higher than a discharge pressure.