JPH0598901A - Rotational type scroll fluid machine - Google Patents

Abstract

(57) [Abstract] [Purpose] Among scroll fluid machines, a rotary type in which a rotatably supported first scroll member and a second scroll member eccentrically combined therewith rotate in the same direction at the same speed. In a scroll fluid machine, an object is to eliminate an inappropriate clearance between two scroll wrap members. A first scroll member (1) and a second scroll member (2) each have means for suppressing displacement of the two scroll members (1, 2) away from each other in the thrust direction, and in the thrust direction. Among the means for restraining the displacement of the two scroll members 1, 2 in the direction of approaching each other, there is provided means other than means by means of sliding contact between the tip ends of the scroll wraps 1b, 2b and the end plates 1a, 2a facing them. did. [Effect] Since the clearance between the two scroll members can always be maintained appropriately, the rotational speed range in which operation can be performed with high energy efficiency can be greatly expanded to the low-speed and high-speed rotation sides.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary scroll fluid machine, and more particularly, to maintaining a clearance between two scroll members arranged such that the respective geometric centers of rotation of scroll wraps are displaced from each other. The present invention relates to a rotary scroll fluid machine suitable for.

[0002]

2. Description of the Related Art A conventional rotary scroll fluid machine is fixed to the end plate of a second scroll member on the opposite surface of the end plate of the first scroll member, as described in Japanese Patent Laid-Open No. 64-302. The first scroll member is arranged so as to slide, but the end surface of the first scroll member opposite to the end plate is the type in which nothing other than the scroll wrap is erected.
As described in JP-A-267379, a member fixed to the end plate of the second scroll member is arranged so as to slide on the facing surface of the end plate of the first scroll member in addition to the scroll wrap. In the scroll member, the end face of the end plate of the scroll member was a type in which nothing other than the rotating shaft was erected.

[0003]

However, the above-mentioned prior art has not taken into consideration that the clearance in the thrust direction between two meshing scroll members is appropriately maintained. As a result, if the clearance becomes too small, the precision of parts or assembly is reduced, and the state of zero clearance where the tip of one scroll wrap and the front surface of the other end plate contact due to vibration or deformation is temporary. However, there is a problem that friction loss occurs or scroll wrap is damaged there. On the contrary, when the clearance becomes too large, the working fluid leaks from the high pressure compression chamber or expansion chamber to the low pressure compression chamber or expansion chamber adjacent thereto.

In order to solve the above problems, a first object of the present invention is to provide a rotary scroll fluid machine capable of suitably maintaining a thrust clearance between two meshing scroll members.

A second object of the present invention is to solve the above-mentioned problems and to suppress the deformation of the end plate, so that the clearance in the thrust direction between the scroll members and the space between the side surfaces of the scroll laps are generated. An object of the present invention is to provide a rotary scroll fluid machine capable of suppressing the deviation of the clearance from the appropriate value.

A third object of the present invention is, in addition to the second object, is to provide a rotary scroll fluid machine having scroll member approach suppressing means with a small friction loss.

In addition to the third object, the fourth object of the present invention is to increase the bending rigidity of the end plate so that the clearance between the scroll members in the thrust direction and the clearance between the side surfaces of the scroll wrap deviate from appropriate values. To provide a rotary scroll fluid machine that suppresses

In addition to the third object, a fifth object of the present invention is to suppress the deformation of the end plate as much as possible from the viewpoint of the position of the action point of the centrifugal force applied to the scroll member approaching suppression means.
It is an object of the present invention to provide a rotary scroll fluid machine that further suppresses deviations of the clearance between the scroll members in the thrust direction and the clearance between the side surfaces of the scroll wrap from appropriate values.

In addition to the fifth object, the sixth object of the present invention is to increase the bending rigidity of the end plate so that the clearance in the thrust direction between the scroll members and the clearance between the side surfaces of the scroll lap deviate from the appropriate values. A further object of the present invention is to provide a rotary scroll fluid machine that further suppresses this.

A seventh object of the present invention is, in addition to the fifth or sixth object, is to provide a rotary scroll fluid machine suitable for rotor balancing of a scroll wrap portion.

An eighth object of the present invention is, in addition to the second object, is to provide a rotary scroll fluid machine having scroll member approaching restraining means with a smaller friction loss.

A ninth object of the present invention is, in addition to the third to eighth objects, a scroll wrap for a mirror plate caused by a centrifugal force applied to the scroll wrap causing a moment on the mirror plate at the root of the scroll wrap. It is an object of the present invention to provide a rotary scroll fluid machine capable of suppressing a deviation from an appropriate value of a clearance in a thrust direction between scroll members and a clearance between side surfaces of a scroll lap, which are mainly caused by a deformation having a side as a convex surface.

The tenth object of the present invention is, in addition to the third to ninth objects, a thrust direction between scroll members caused by a dimensional change of a scroll wrap due to a temperature change accompanying a volume change of a working fluid. An object of the present invention is to provide a rotary scroll fluid machine capable of suppressing the deviation of the clearance and the clearance between the side surfaces of the scroll wrap from an appropriate value.

An eleventh object of the present invention is, in addition to the first to tenth objects, is to provide a rotary scroll fluid machine having a simplified rotational force transmission system.

A twelfth object of the present invention is, in addition to the eleventh object, a clearance between the side surfaces of the scroll wrap due to a deviation of the rotation between the first scroll member and the second scroll member. Another object of the present invention is to provide a rotary scroll fluid machine that suppresses a deviation from the appropriate value of.

A thirteenth object of the present invention is, in addition to the twelfth object, to provide a rotary scroll fluid machine having a small number of parts.

[0017]

In order to achieve the above first object, the present invention comprises a first end plate and a first scroll wrap standing on the first end plate and rotatably supported by a bearing element. A first scroll member supplied with a rotation driving force from a rotation driving unit, a second end plate and a second scroll wrap standing on the second end plate, and the bearing being eccentric from the rotation axis of the first scroll member. The second scroll member rotatably supported by the element and supplied with the rotational driving force from the rotational driving unit maintains a minute clearance between the scroll wraps and between the tip of the scroll wrap and the end plate facing it. Formed by their scroll wraps and their end plates by rotating them in the same direction at approximately the same speed. To reduce the volume of the substantially closed space, or is formed by the first end plate and the first scroll wrap standing upright on the first end plate and rotatably supported by the bearing element to rotate to the rotary passive part. It is formed of a first scroll member that supplies force, a second end plate and a second scroll wrap that stands upright, and is rotatably supported by a bearing element that is eccentric from the rotation axis of the first scroll member. The second scroll member for supplying a rotational force to the rotary passive portion is arranged between the scroll wraps and between the tip of the scroll wrap and the end plate facing the scroll wrap while maintaining a minute clearance. Volume of a nearly closed space formed by their scroll wraps and their end plates by rotating in the same direction at about the same speed In a rotary scroll fluid machine that performs an expanding operation, each of the first and second scroll members has a means for suppressing a displacement in a thrust direction in which two scroll members separate from each other, and It is characterized in that it has means for suppressing displacement in a direction in which the two scroll members approach each other in the thrust direction.

In order to achieve the above second object, the present invention provides means for suppressing the displacement in the two thrust directions,
At least the surface of the first and second end plates where the scroll wrap does not stand (back side of the end plate) or the surface where the scroll wrap stands (end surface of the end plate).

In order to achieve the third object, the present invention provides a means for suppressing the displacement of the two scroll members in a direction in which they approach each other, on the front surface of the first end plate. Either one of the protruding portion and the second protruding portion is erected on the front surface of the second end plate, and the tip of the protruding portion and the end face of the end plate facing it. It is realized by means for bringing the surfaces into sliding contact.

Further, in order to achieve the above-mentioned fourth object, the present invention is such that the protrusion is formed in an annular shape.

In order to achieve the fifth object, the present invention provides a means for suppressing the displacement in the direction in which the two scroll members approach each other. This is realized by vertically arranging the second protrusion on the protrusion and the front surface of the second end plate, and sliding the tip surfaces of the protrusions against each other.

In order to achieve the sixth object, the present invention is such that at least the first or second protrusion is formed in an annular shape.

Further, in order to achieve the seventh object, according to the present invention, the first and second protrusions have substantially the same height.

In order to achieve the eighth object, according to the present invention, the means for suppressing the displacement in the direction in which the two scroll members approach each other has a surface on the front surface side of the first end plate. Further, it is realized by providing a surface on the front surface side of the second end plate and a movable member sandwiched in a state capable of sliding contact with these surfaces.

In order to achieve the ninth object, according to the present invention, at least a part of the protrusion or the sliding contact portion of the movable member suppresses displacement in a direction in which the two scroll members separate from each other. The means provided on the rear surface side of one end plate is located inside the outermost periphery of the installation range at each of those two locations.

Further, in order to achieve the tenth object, according to the present invention, at least one of the protrusions of the scroll member or all of the movable members have a coefficient of thermal expansion larger than that of the material forming the scroll wrap. It is formed of a material having a different composition or a different tissue.

In order to achieve the eleventh object, according to the present invention, the rotary drive unit supplies a rotary drive force to the first scroll member and the second rotary drive unit. The first rotary member is composed of two rotary drive parts of a second rotary drive part for supplying the rotary drive force to the scroll member, or the rotary passive part is supplied with the rotary force from the first scroll member. The rotary passive part and the second rotary passive part supplied with the rotational force from the second scroll member are two rotary passive parts.

In order to achieve the twelfth object, the present invention provides a rotational phase difference regulating means for keeping the rotational phase difference between the first scroll member and the second scroll member within a certain range. Is provided.

In order to achieve the above thirteenth object, according to the present invention, all or part of the rotational phase difference restricting means is a means for suppressing displacement of at least the two scroll members away from each other, or It also serves as a means for suppressing the displacement of the two scroll members toward each other.

[0030]

According to the first structure, the relative positional relationship between the two scroll members in the thrust direction does not change. As a result, the clearance in the thrust direction between the scroll members is always maintained at a suitable size.

Further, according to the above-mentioned second structure, since the deformation of the end plate at the same time as the displacement can be suppressed, the clearance in the thrust direction between the scroll members can be more preferably maintained and the two members are engaged with each other. The clearance between the two scroll wrap side surfaces can be suitably maintained. That is, since the scroll member is not a rigid body, it is deformed, and because the end plate is plate-shaped, the part with the front surface of the end plate is mainly bulged (the part on the back side of the end plate is just dented) or dented ( Just the back side of the end plate is protruding) will be a modification of the form. Due to the deformation of the end plate, the clearance between the scroll members in the thrust direction deviates from the proper value, and at the same time, the clearance between the scroll wrap side surfaces deviates from the proper value due to the scroll wrap falling. According to this structure, this can be prevented.

Further, according to the third structure, the sliding speed at the sliding contact portion of the protruding portion can be greatly reduced to the relative speed of these two scroll members. It is possible to realize a scroll member approach suppressing means with a small friction loss.

Further, according to the fourth structure, since the annular protrusion acts as a rib of the end plate, the bending rigidity of the end plate with respect to various axes is increased. As a result, the clearance in the thrust direction between the scroll members and the clearance between the meshed scroll wrap side surfaces can be more preferably maintained.

Further, according to the fifth structure, since the protrusions are provided on both of the two scroll members, the protrusion itself can be lowered. Therefore, the clearance in the thrust direction between the scroll members and the clearance between the meshed scroll wrap side surfaces can be more preferably maintained. That is, due to the rotation of the scroll member, a centrifugal force is applied to the protruding portion, so that at the root of the protruding portion, the end plate receives a bending moment such that the front surface is convex. Considering the case where the cross-sectional shape of the protrusion is almost the same at the root and the tip, this centrifugal force is
Since it is proportional to the volume of the protrusion, it is approximately proportional to its height. Further, the point of action of the resultant force of the centrifugal force is approximately the center of the projecting portion. Therefore, the moment is approximately proportional to the square of the height of the protrusion. By the way, since the bending amount and the bending angle of the end plate are approximately proportional to the moment, the bending amount and the bending angle of the end plate are almost proportional to the deviation amount from the appropriate value of the clearance between the scroll members caused by the bending amount and the bending angle. From these, it can be seen that the amount of deviation of the clearance between the scroll members from the appropriate value due to the centrifugal force applied to the protrusion is approximately proportional to the square of the height of the protrusion. That is, as the height of the protrusion is increased, the deviation of the clearance due to the increase is accelerated. According to this configuration, it is possible to prevent such a deviation of the clearance from increasing.

Further, according to the sixth structure, since the annular projecting portion acts as a rib of the mirror plate, the bending rigidity of these mirror plates with respect to various axes is increased. As a result, the clearance in the thrust direction between the scroll members and the clearance between the meshed scroll wrap side surfaces can be more preferably maintained.

Further, according to the seventh construction, the tip surfaces of the two protruding portions are substantially the center surface in the height direction of the scroll wrap. As a result, by forming the tip end surface of the projecting portion as a balance surface, it is possible to suppress the generated even imbalance as much as possible, so that the rotor balance of the scroll member can be easily performed. That is, most of the unbalanced amount of the scroll member around the rotation axis is caused by the deviation of the cross-section of the scroll wrap standing on the end plate from the rotation axis of the centroid. Therefore, except for the case of a trapezoidal scroll tooth profile with a large inclination angle, the total amount of the unbalanced amounts of the scroll members comes to almost the center plane in the height direction of the scroll wrap, which can be suppressed as much as possible. it can.

Further, according to the eighth structure, the sliding contact portions of the protrusion are increased to two places between the first end plate and the movable member and between the second end plate and the movable member. As a result, during operation, sliding contact occurs at a portion of the sliding contact that has a low resistance, so that it is possible to realize a scroll member approaching restraining means with even smaller friction loss.

Further, according to the ninth construction, the following operation is brought about. Normally, when a substance changes in volume, its temperature also changes so as to satisfy the thermodynamic conditions in which it is placed (except for isothermal conditions). Since the volume change of the working fluid in the scroll fluid machine is usually a rapid change, it is close to an adiabatic change and cannot be regarded as an isothermal change. Therefore, the temperature of the portion of the scroll member that is in contact with the volume-changed working fluid and the temperature of the portion that is not in contact are different. Therefore, if the coefficient of thermal expansion of the part that is in contact with the working fluid whose volume has changed is the same as that of the part that is not in contact, the amount of thermal expansion will differ. The scroll wrap comes into contact with the volume-changed working fluid, but the protrusion does not come into contact with the volume-changed working fluid, so if they have the same coefficient of thermal expansion, the clearance between the two scroll members in the direction of the rotation axis will be affected by the temperature difference. However, it is difficult to always keep it properly. Here, according to the ninth configuration, the difference in the dimensional change in the thrust direction of the scroll wrap and the protrusion due to the temperature change accompanying the volume change of the gas can be constantly reduced, so that the clearance in the thrust direction between the scroll members is further reduced. It can be held more preferably.

Further, according to the above tenth structure, there are the following effects. Among the deformations of the end plates having the convex surface on the front side of the end plates caused by the centrifugal force applied to the scroll wrap, the displacement components in the directions in which the end plates are separated from each other are means for suppressing the displacement in the directions in which the two scroll members are separated from each other. However, in the direction in which those end plates approach each other, the displacement tends to increase on the contrary to the inside of the outermost periphery of the installation area of the means for suppressing the displacement in the direction in which the two scroll members approach each other. To do. According to this configuration, since there is always a sliding contact portion at a position where the two end plates try to approach each other, it is possible to suppress the deformation of the end plate caused by the centrifugal force applied to the scroll wrap, so The clearance can be preferably maintained.

Further, according to the eleventh structure, since the scroll member and the rotary drive portion or the rotary passive portion can be brought close to direct connection, the rotational force transmission system is simplified.

Further, according to the twelfth structure, it is possible to suppress the synchronization deviation of the rotation of the first scroll member and the rotation of the second scroll member, so that the clearance between the side surfaces of the scroll wrap is preferably maintained. can do.

Further, according to the thirteenth structure, it is possible to reduce the number of parts.

[0043]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) A first embodiment of the present invention will be described with reference to FIGS. 1, 2 and 3. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 1 is a vertical sectional view thereof, and FIGS. 2 and 3 are perspective views of a first scroll member and a second scroll member, respectively. ..

First, as a description of the configuration of this embodiment, each component will be described first. First, the components on the first scroll member side will be described. The first scroll member 1 is mainly composed of a disk-shaped end plate 1a and a scroll wrap 1b provided upright on the end plate 1a. There is an end plate groove 1y on the side surface of the end plate 1a, which is formed by screwing two discs of a front end plate 1a ₁ with a cut-out side corner and a back end plate 1a ₂ with a cut-out side corner. It is formed by stopping. In addition, a pin base (A) 1c and a pin (A) 1d inserted and fixed to the pin base (A) 1c are provided on the scroll lap standing surface (end surface of the mirror plate) of the end plate 1a, and further the pin base (B) 1
e and a pin (B) 1f inserted and fixed therein are provided. An outlet 1t is open near the center of the end plate 1a.

The rotary shaft 11 is erected on the surface opposite to the front surface of the mirror plate 1a (the rear surface of the mirror plate). The rotating shaft 11
The balance ring (A) 11a is integrally formed with the rotor 7, and the rotor 7b and the balance ring (B) 11b are press-fitted therein. And these two balance rings 11a,
The scroll member 1 which is a rotating portion and the rotating shaft 11 are balanced on two sides by 11b. Further, a through hole 11d passes through the center of the rotating shaft 11. In this embodiment, the rotary shaft 11 and the scroll member 1 are integrated, but they may be processed separately and then joined by shrink fitting or cold fitting.

The cylindrical casing 3 is mainly composed of a guide 3o, a suction chamber forming portion (scroll chamber forming portion) 3a and a motor chamber forming portion 3d on both sides of the guide 3o. A suction port 3b is provided on the side surface of the scroll chamber forming portion 3a, and a flange (A) 3c is provided at one end of the scroll chamber forming portion 3a. On the other hand, on the outer side surface of the motor chamber forming portion 3d, the discharge port 3e, the flange (B) 3f, the flange (C) 3g, and the flange (B) 3f and the flange (C) 3g.
A fin 3h is provided between them. Also, the motor chamber forming portion 3d
A stator 7a is press-fitted to the inner surface of the.

A flange (D) 3i is provided at one end of the motor chamber forming portion 3d. Further, the outer peripheral surface is covered with a cooling water inflow port 5a, a cooling water outflow port 5b, and a cylinder 5 provided with a flange 5c at one end, and the flange (B) 3f is screwed to the flange 5c with the O-rings 5d and 5e sandwiched therebetween. A water jacket 5f is formed.

A rolling bearing 9a is fixedly arranged at the center of the support plate 9 by a bearing retainer 9d. Also,
The side wall 13 is provided with a terminal 13b. In this embodiment, the terminal 13b is provided on the side wall 13, but it may be provided on the casing 3 into which the stator 7a is press fitted.

Next, the components on the second scroll member side will be described. The second scroll member 2 is configured as described below, in substantially the same manner as the first scroll member 1. It is mainly composed of a disk-shaped end plate 2a and a scroll wrap 2b which is erected on the end plate 2a. There is a mirror plate groove 2y on the side surface of the mirror plate 2a.
It is formed by screwing two discs, a ₁ and a back mirror plate 2a ₂ which is also cut out at the side corners. Further, a pin hole (A) 2p and a pin hole (B) 2q are provided on the scroll wrap standing surface (end surface of the mirror plate) of the mirror plate 2a.

On the other hand, a rotary shaft 12 is erected on the surface of the mirror plate 2a opposite to the mirror plate front surface (the mirror plate rear surface). An outlet 2t is open near the center of the end plate 2a. The rotary shaft 12 is erected on the opposite surface (back surface of the mirror plate) of the mirror plate front surface of the mirror plate 2a. The rotary shaft 12 has
The balance ring (A) 12a is integrally formed, and further,
The rotor 8b and the balance ring (B) 12b are press-fitted. Then, these two balance rings 12a, 12
b, the scroll member 2 and the rotating shaft 12 that are rotating parts.
The two sides are balanced.

A through hole 12d is formed in the center of the rotary shaft 12.
Is passing. In this embodiment, the rotary shaft 12 and the scroll member 2 are integrated, but they may be processed separately and then joined together by shrinkage fitting or cold fitting. In addition, the cylindrical casing 4
Is mainly composed of a guide 4o, a scroll chamber forming portion 4a and a motor chamber forming portion 4d on both sides thereof. A suction port 4b is provided on the side surface of the scroll chamber forming portion 4a, and a flange (A) 4c is provided at one end of the scroll chamber forming portion 4a.
On the other hand, on the outer surface of the motor chamber forming portion 4d, a discharge port 4e, a flange (B) 4f, a flange (C) 4g, and a fin 4h between the flange (B) 4f and the flange (C) 4g. To provide.

On the inner side surface of the motor chamber forming portion 4d,
The stator 8a is press-fitted. Also, the motor chamber forming portion 4d
Is provided with a flange (D) 4i at one end thereof. Further, the outer peripheral surface is covered with a cooling water inlet 6a and a cooling water outlet 6b, and a cylinder 6 provided with a flange 6c at one end is covered, and O-rings 6d and 6e are provided.
Flange (B) at flange 6c with sandwiching
4f is screwed to form a water jacket 6f.

A rolling bearing 10a is fixedly arranged at the center of the support plate 10 by a bearing retainer 10d.
The side wall 14 is provided with a terminal 14b. In this embodiment, the terminal 14b is provided on the side wall 14, but it is also possible to provide the terminal 8b on the casing 4 into which the stator 8a is press fitted.

Above, the description of each component is completed, and then the combination of these components will be described. Front panel 1a
₁ is once separated from the back end plate 1a ₂ and the front end plate 1a ₁ is inserted into the casing 3 from the scroll chamber forming portion 3a side of the casing 3 and the back end plate 1a ₂ is inserted into the casing 3 from the motor chamber forming portion 3d side. and, the end plate grooves 1y is in a state of fitted into the guide 3o, ₁ mag et and end plate 1a ₂ Table end plate 1a is screwed again. Here, the gap between the end plate groove 1y and the guide 3o is set to such a size that the lubricating oil enters and functions as a slide bearing when the scroll compressor is in an operating state. Further, as a result of the stator 7a and the rotor 7b facing each other across the gap 7d, the motor 7 which is the rotation driving portion of the scroll member 1 is formed. On the other hand, the end of the rotary shaft 11 is loosely press-fitted into the rolling bearing 9a, the support plate 9 is screwed to the flange (D) 3i with the O-ring 9b interposed therebetween, and the first scroll member side is assembled.

Similarly, the other second scroll member side is assembled. The front end plate 2a ₁ is once separated from the back end plate 2a _2, and the scroll chamber forming portion 4a of the casing 4 is separated.
Table end plate 2a ₁ from the side, motor - from data chamber forming portion 4d side the back of the end plate 2a ₂ Ke - inserted into single 4, the end plate grooves 2y with the guide 4o is mate, and Table end plate 2a ₁ The back end plate 2a ₂ is screwed again. Here, end plate groove 2y
The clearance between the guide 4o and the guide 4o is set to such a size that the lubricating oil enters and functions as a plain bearing when the scroll compressor is in operation. Also, the stator 8a and the rotor 8b
As a result of being opposed to each other across the gap 8d, a motor 8 which is a rotation driving portion of the scroll member 2 is formed. on the other hand,
The end of the rotary shaft 12 is loosely press-fitted into the rolling bearing 10a, the support plate 10 is screwed to the flange (D) 4i with the O-ring 10b interposed therebetween, and the second scroll member side is assembled.

The two parts on the first scroll member side and the second scroll member side thus configured are sandwiched by the O-ring 4o to form the flange (A) 3c and the flange (A).
4c are screwed together to connect the suction chamber 19
To form. At this time, the scroll wrap 1b and the scroll wrap 2b mesh with each other, and further, the pin hole (A) 2p
Pin (A) 1d, Pin hole (B) 2q Pin (B) 1f
The rotary shaft 11 or the rotary shaft 12 is turned by turning those ends which are exposed to the outside so that the rotary shaft 11 or the rotary shaft 12 comes in contact with each other to form a gas compression chamber and a rotation phase difference regulation mechanism in the suction chamber 19. To do. Here, a gap is formed between the tip of the scroll wrap and the front surface of the end plate facing it. The clearance is set to a size that allows the lubricating oil to enter and keep the compression chamber substantially closed when the scroll compressor is in operation.

In this embodiment, the rotation phase difference restricting means is formed by a combination of two pin holes and pins, but it may be more than two. Next, the side wall 13 with the hole 9c opened is
A discharge chamber 15 is formed by sandwiching the O-ring 13a and screwing the flange (D) 3i. At this time,
An electric wire 7c for supplying a current to the motor 7 is connected to an external power source (not shown) via a terminal 13b set on the side wall 13. Similarly, the side wall 14 having the hole 10c is attached to the O-ring 1
The discharge chamber 16 is formed by screwing the flange (D) 4i with 4a sandwiched therebetween. Also at this time, the side wall 14
An electric wire 8c for supplying a current to the motor 8 is connected to an external power source (not shown) via the terminal 14b set to the above. Finally, the lubricating oil 17 is put into the discharge chamber 15 from the discharge port 3e, and the lubricating oil 18 is put into the discharge chamber 16 from the discharge port 4e.

Next, the operation of this embodiment will be described. An electric current is applied to the electric wires 7c and 8c so that the two motors 7 and 8 rotate in the same direction at substantially the same speed. Since the scroll members 1 and 2 are directly connected to those motors, the scroll members 1 and 2 can be rotated by a very simple drive force transmission system. Since the end plate grooves 1y and 2y are fitted in the guides 3o and 4o, the displacement of the end plate in the thrust direction is suppressed by the amount of backlash there. Therefore, the displacement of the scroll members 1 and 2 in the thrust direction can be suppressed to the extent of the play between the end plate groove and the guide. Actually, as the scroll members 1 and 2 rotate, the lubricating oils 17 and 18 enter between the end plate grooves 1y and 2y and the guides 3o and 4o, so that the amount of backlash is further suppressed. ..
At the same time, it also plays the role of supporting the rotation of the scroll members 1 and 2. Further, thereby, the friction loss there and the gas leakage from the discharge chambers 15 and 16 to the suction chamber 19 are suppressed.

Here, the rotational phase difference between the two scroll members is forcibly suppressed to the level of backlash between the pin hole and the pin because there is a rotational phase difference regulation means by the pin hole and the pin. .. Thereby, the clearance between the side surfaces of the scroll wraps 1b and 2b can always be favorably maintained. As a result, the gas is sucked into the suction port 3 from outside the compressor.
b into the suction chamber 19 and scroll members 1, 2
Enter the compression chamber formed by. Since the compression chamber moves to the center of rotation while reducing its volume, the gas is compressed and guided to the outlets 1t and 2t. And the gas is
Through holes 11d and 12d while cooling the rotors 7b and 8b.
Through the discharge chambers 15 and 16. In addition, the gas is
While cooling the stators 7b, 8b and the stators 7a, 8a, they pass through the gaps 7d, 8d and exit from the discharge ports 3e, 4e to the outside of the compressor. Further, for cooling the stators 7a and 8a, cooling water or cooling gas is supplied to the water jackets 5f and 6f.

According to this embodiment, the balance ring 11
Since the a and 12a are formed integrally with the end plates 1a and 2a, the bending rigidity of the end plates 1a and 2a is increased, and the bending of the end plates is suppressed, so that the clearance between the scroll members can be more preferably maintained. Has the effect of. Further, since the means for suppressing the displacement of the scroll member in the thrust direction and the rotation supporting means are commonly used, there is a peculiar effect that the number of parts can be reduced. Further, since the means for suppressing the displacement of the scroll member in the thrust direction is provided over the entire outer periphery of the end plate, there is also a unique effect that the deformation of the end plate can be suppressed and the clearance between the scroll members can be held more preferably.

In this embodiment, the mirror plate grooves 1y and 2y, which are means for suppressing the displacement of the scroll member in the thrust direction, are provided on the outermost circumference of the mirror plate, but they may be provided on the rotary shafts 11 and 12 having a low peripheral speed. In this case, there is a unique effect that the friction loss at that position can be significantly reduced.

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. This embodiment is a case where the present invention is applied to a hermetic scroll type compressor.
[FIG. 4] is a vertical cross-sectional view of the first scroll member side of this embodiment.

First, the configuration of this embodiment will be described. The deep groove ball bearing 1z is a means for rotatably supporting the scroll member 1 and suppressing displacement of the scroll member 1 in the thrust direction. Also, the gas blocking wall 3p,
A pump-in type groove plate 3q is fixed to it. The groove plate 3q is held at the minimum level where the clearance between the mirror plate 1a and the rear surface of the mirror plate 1a does not contact. The hole 9c which was in the support plate 9 of the first embodiment is eliminated,
Further, the terminal 13b on the terminal plate (side wall) 13 is
It is provided on the side surface of Thing 3. Further, the discharge port 3e that was in the casing 3 is provided in the terminal plate 13. Further, a pump-in type groove plate 9d having a hole through which discharge gas passes is screwed to the support plate 9. The groove plate 9d is held at the minimum level where the clearance with the end face of the rotating shaft 11 does not come into contact.

Similarly, on the second scroll side,
A deep groove ball bearing 2z, a gas blocking wall 4p, and a pump-in type groove plate 4q are provided. Although not shown, the hole 10c in the support plate 10 of the first embodiment is eliminated, and the terminal 14b in the terminal plate 14 is provided on the side surface of the casing 4. Further, the discharge port 4e that was in the casing 4 is provided in the terminal plate 14. Further, a pump-in type groove plate 10d having a hole through which the discharge gas passes is screwed to the support plate 10. Since the configuration of the other parts is the same as that of the first embodiment, the configuration description will be omitted below.

Next, the operation of this embodiment will be described. An electric current is applied to the electric wires 7c and 8c so that the two motors 7 and 8 rotate in the same direction at substantially the same speed. Since the scroll members 1 and 2 are directly connected to those motors, the scroll members 1 and 2 can be rotated by a very simple drive force transmission system. On the side of the first scroll, the deep groove ball bearing 1z axially supports the scroll member 1 and suppresses displacement in the thrust direction. Similarly, on the second scroll side, the deep groove ball bearing 2z axially supports the scroll member 2 and suppresses displacement in the thrust direction.

When the scroll member 1 is rotating, the discharge chamber 15 and the motor chamber 3r are substantially shut off by the gas compression action of the groove plate 3q, and the motor is activated by the gas compression action of the groove plate 9d. As a result of the chamber 3r and the suction chamber 19 being substantially shut off, the discharge chamber 15 and the suction chamber 19 are shut off almost completely. Similarly, when the scroll member 2 is rotating, the discharge chamber 16 and the motor chamber 4r are substantially shut off by the gas compression action of the groove plate 4q, and the motor is activated by the gas compression action of the groove plate 10d. As a result of the chamber 4r and the suction chamber 19 being substantially cut off, the discharge chamber 16 and the suction chamber 19 are almost completely cut off.

Further, since the gas flows from the discharge chambers 15 and 16 through the discharge ports 3e and 4e of the side walls 13 and 14 directly to the outside of the compressor, the motor chambers 3r and 4r are not gas passages. As a result, the cooling of the motors 7 and 8 accompanying the passage of the gas gaps 7d and 8d in the operation of the first embodiment is eliminated. Since the operation of the other parts is the same as that of the first embodiment,
Omitted below.

According to this embodiment, the balance ring 11
Since a and 12a are formed integrally with the end plates 1a and 2a, the bending rigidity of the end plates 1a and 2a is increased, and the bending of the end plates is suppressed, so that the clearance between the scroll members can be more appropriately maintained. effective. Further, since the means for suppressing the displacement of the scroll member in the thrust direction and the rotation supporting means are commonly used, there is a peculiar effect that the number of parts can be reduced. Further, since the means for suppressing the displacement of the scroll member in the thrust direction is provided over the entire outer periphery of the end plate, there is also a unique effect that the deformation of the end plate can be suppressed and the clearance between the scroll members can be held more preferably.

Since no lubricating oil is required, there is a unique effect that a clean compressed gas without oil can be supplied. Further, when the current for driving the motors 7, 8 is cut off due to an unforeseen cause, a torque that can cause a very high speed reverse rotation is generated due to the pressure difference between the gas in the suction chamber 19 and the gas in the discharge chambers 15, 16. Even if it is slow, when the rotation speed at which the forward rotation changes to the reverse rotation is zero, the groove plates 3p, 9d, 4p, and 10d
Since the gas shutoff effect in the above is lost, the suction chamber 19 and the discharge chambers 15 and 16 communicate with each other, and the pressure difference of the gas is almost eliminated, the torque of the reverse rotation is rapidly reduced, and the risk of high-speed reverse rotation is greatly increased. There is also a unique effect of reducing to.

In the present embodiment, the deep groove ball bearings 1z, 2z, which are means for suppressing the displacement of the scroll member in the thrust direction, are provided on the outermost periphery of the end plate, but the rotating shafts 11, 12 having a low peripheral speed are provided.
It may be provided in. In this case, there is a unique effect that the friction loss at that position can be significantly reduced.

(Third Embodiment) Next, a third embodiment of the present invention will be described with reference to FIG. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, and FIG.
It is a longitudinal cross-sectional view of the first scroll member side of this embodiment.

First, as a description of the configuration of this embodiment, each component will be described first. First, the components on the first scroll member side will be described. The first scroll member 1 is mainly composed of a disk-shaped end plate 1a and a scroll wrap 1b which is erected on the end plate 1a. A pin base (A) 1c and a pin (A) 1d inserted and fixed thereto are provided on the front surface of the end plate 1a, and further a pin base (B) 1e and a pin (B) inserted and fixed therein. 1f is provided. Further, on the rear surface of the end plate 1a, there is an intermediate pressure hole 1o communicating with the end surface of the end plate near the middle of the scroll wrap 1b.
A thrust surface 1j having an opening, and a bottom surface projecting portion 1k are provided on the outermost periphery of an end plate 1a surrounding the thrust surface 1j. In addition, the inner peripheral surface of the female side spline shaft coupling 1
m, the outer peripheral surface is a journal bearing facing surface 1n, and a shaft coupling portion 1l having an outlet 1t communicating with the end surface of the end plate is also provided near the center.

The rotary shaft 11 is provided with a through hole 11d at its center. Further, the rotor 7b is press-fitted on the outer periphery thereof, and the balance ring (A) 11a and the balance ring (B) 11b are fixedly arranged on both sides thereof. Further, the male side spline shaft coupling 11c is provided at one end of the rotary shaft 11.
Is provided. The rolling bearing 9a is press-fitted into the other end. Then, the two balance rings 11a and 11b balance the two surfaces of the rotary shaft 11.

Here, the rotary shaft 11 and the scroll member 1
It is more preferable to insert the male side spline shaft coupling 11c into the female side spline shaft coupling 1m so as to be integrated, and perform double-faced balance in that state. Further, the cylindrical casing 3 is mainly composed of the motor chamber forming portion 3d and the partition wall 3
j. A discharge port 3e, a flange (B) 3f, a flange (C) 3g, and a fin 3h are provided between the flange (B) 3f and the flange (C) 3g on the outer surface of the motor chamber forming portion 3d. .. A stator 7a is press-fitted on the inner side surface of the motor chamber forming portion 3d.

A flange (D) 3i is provided at one end of the motor chamber forming portion 3d. Further, the motor chamber forming section 3
On the outer peripheral surface of d, the cooling water inlet 5a and the cooling water outlet 5
b, the cylinder 5 having a flange 5c at one end is covered, and the flange (B) 3f is screwed to the flange 5c while the O-rings 5d and 5e are sandwiched between the water jacket 5 and
form f. Further, the support plate 9 has a hole at the center thereof into which the rolling bearing 9a is inserted. A plurality of holes 9c connecting the motor chamber and the discharge chamber 15 are formed in the periphery thereof.

On the other hand, at the central portion of the partition wall 3j, a journal plain bearing 3k is provided so that the central axis of the motor chamber forming portion 3d is the central axis. Further, an oil hole 3l is provided between the lower part of the surface of the partition wall 3j on the motor chamber forming portion 3d side and the journal slide bearing 3k to connect them. further,
An intermediate pressure chamber recess 3m and a cylindrical groove 3n are provided on the surface of the partition wall 3j opposite to the motor chamber forming portion 3d. Further, the side wall 13 is provided with a terminal 13b.

Since the second scroll member 2 is composed of the same constituent parts as the first scroll member 1, the description of the constituent parts of the second scroll member 2 is omitted. The remaining component is the spacer 19a. It is a plate having a large hole near the center, and is provided with a discharge port 19d that connects the hole with the side surface.

Above, the explanation of each constituent part is completed, and then the combination of those constituent parts will be explained. Scroll member 1 to casing 3, motor chamber forming portion 3d of partition wall 3j
From the surface on the opposite side, the shaft coupling portion 1l is inserted into the journal slide bearing 3k, and the lower surface projecting portion 1k is inserted into the cylindrical groove 3n. As a result, the intermediate pressure chamber 1s is formed.
Next, the rotary shaft 11 into which the rotor 7b is press-fitted is inserted into the casing 3 from the surface of the partition wall 3j on the motor chamber forming portion 3d side to the female side spline shaft coupling 2m and the male side spline shaft coupling 1.
Install so that 1c is inserted. Further, the rolling bearing 9a is inserted into the central hole of the support plate 9, and the support plate 9 is screwed to the casing 3 with the O-ring 9b interposed therebetween. Then, by screwing the bearing retainer 9d to the support plate 9, displacement of the outer ring of the rolling bearing 9a in the thrust direction is regulated, and finally displacement of the rotary shaft 11 in the thrust direction is regulated. As a result, the motor 7 which is the rotation driving portion of the scroll member 1 is formed by the stator 7a and the rotor 7b. In this way, the first scroll member side is assembled. Since the other second scroll member side is assembled in exactly the same manner, its explanation is omitted.

The two parts on the first scroll member side and the second scroll member side configured as described above are engaged with the scroll wrap 1b and the scroll wrap 2b in a predetermined relationship to form the spacer 19a. Connect them by inserting them with screws. At this time, the spacer 19
The clearance between both surfaces of a and the front surfaces of the end plates 1a and 2a is kept at a minimum level where they do not contact each other. Here, the facing portion is installed within the range of the intermediate pressure chambers 1s and 2s. Further, the O-rings 19b and 19c are sandwiched to secure the sealing property. Further, the pin (A) 1d is inserted into the pin hole (A) 2p and the pin (B) 1f is inserted into the pin hole (B) 2q to form a rotational phase difference regulation mechanism.

In this embodiment, the rotational phase difference restricting means is formed by a combination of two pin holes and pins, but the number may be two or more. As a result, the suction chamber 19 is formed. A suction port 19d is provided on the side surface of the spacer 19a. Further, the discharge chamber 15 is formed by screwing the side wall 13 to the flange (D) 3i by sandwiching the O-ring 13a. At this time, the electric wire 7c for supplying a current to the motor 7 is connected to an external power source (not shown) through the terminal 13b set on the side wall 13, and the lubricating oil 17 is put into the discharge chamber 15. Similarly, the discharge chamber 16 is also formed on the second scroll member side.

Next, the operation of this embodiment will be described. The operation of this embodiment is the same as that of the first embodiment except the operation of the scroll member in the thrust direction displacement suppressing means, so only the operation of the scroll member in the thrust direction displacement suppressing means will be described.

The intermediate pressure chambers 1s and 2s are provided with lower surface protrusions 1k and 2s.
Since there is an intermediate pressure hole 1o, 2o while being substantially cut off from the suction chamber 19 by k and the spacer 19a, the pressure there is intermediate between the suction pressure and the discharge pressure. Here, during the actual operation, the lubricating oils 17 and 18 are
Since the oil flows from the oil holes 3l, 4l through the intermediate pressure chambers 1s, 2s into the two cutoff portions, the cutoff there is almost complete. The thrust surfaces 1j, 2j are sized so that a thrust force is generated to suppress the displacement of the end plates 1a, 2a away from each other.

As a result, it is possible to suppress the displacement of the scroll members 1 and 2 away from each other. Also, the spacer 19a
Is opposed to the two end plates 1a, 2a with a slight clearance, so that the displacement in the direction in which the scroll members 1, 2 approach each other can be suppressed to the size of the clearance there. Here, during the actual operation, as described above, the lubricating oils 17 and 18 are flowing therein, so that the displacement in the direction in which the scroll members 1 and 2 approach each other is further suppressed than the size of the clearance. To be done. Further, the space between the spacer 19a that prevents the scroll members from approaching each other and the facing portion of the front surface of the end plate is within the installation range of the intermediate pressure chambers 1s and 2s, so that the end plate 1a generated by the centrifugal force of the scroll wrap is present. Since the deformation of 2a can be suppressed, the clearance between the scroll members can be preferably maintained.

According to this embodiment, the lower surface protrusions 1k, 2k
This increases the bending rigidity of the end plates 1a, 2a, and
Due to the centrifugal force applied to the lower surface protrusions 1k and 2k, it is possible to cancel the moment generated at the base of the scroll wraps 1b and 2b caused by the centrifugal force applied to the scroll wraps 1b and 2b. It has the unique effect of being suppressed. Further, since the scroll portions 1 and 2 and the drive shafts 11 and 12 are connected to each other by the spline shaft coupling, the allowable amount of the eccentricity error between the scroll portions 1 and 2 can be increased, so that the parts can be easily machined and the scroll Drive shaft 1 after wrapping wraps 1b and 2b
Since 1 and 12 can be connected, there is a unique effect that it is easy to assemble.

(Fourth Embodiment) Next, a fourth embodiment of the present invention will be described with reference to FIGS. 6 and 7. This embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 6 is a vertical cross-sectional view of the first scroll member side of this embodiment, and FIG. 7 is a perspective view of the first scroll member. ..

In this embodiment, the scroll members 1, 2
Are the same as those in the third embodiment except the means for suppressing the displacement in the directions toward each other, and therefore only the description relating to the means for suppressing the displacement in the directions in which the scroll members 1 and 2 approach each other will be described below. To do.

On the outer peripheral portion of the front surface of the end plate 1a of the end plate 1a, there is provided an upper surface projecting portion 1g which is not present in the third embodiment. The upper surface protruding portion 1g is slightly higher than the height of the scroll wrap 1b and the scroll wrap 2b. Here, in order to introduce gas into the scroll wrap portion, the upper surface protrusion 1
Gas channel groove (A) 1h and gas channel groove (B) 1i are provided in g.

As a result, when the scroll members 1 and 2 try to approach each other, immediately before the tips of the scroll wraps 1b and 2b slide on the respective facing end surfaces of the end plates, the tips of the upper surface protrusions 1g move to the first position. Since the scroll member slides on the front surface of the end plate of the two scroll members, it is possible to suppress the displacement in which the scroll members 1 and 2 approach each other. Since the relative movement of the tip of the upper surface protruding portion 1g and the end surface of the end plate of the second scroll member is a turning movement having a turning radius of an eccentric distance between the two rotary shafts 11 and 12, a relative speed is set. Becomes very small. Therefore, the friction loss generated there is extremely small. At the time of actual operation, since the lubricating oil is contained in the sliding portion, the friction loss becomes even smaller.

(Fifth Embodiment) Next, a fifth embodiment of the present invention will be described with reference to FIG. This embodiment is a case where the present invention is applied to a hermetic scroll compressor, and FIG. 8 is a perspective view of a first scroll member of this embodiment. In this embodiment, in order to introduce the gas into the scroll wrap portion, the upper surface protruding portion 1g is not cut out, and the gas flow passage holes 1u and 1u are provided.
v. As a result, since the bending rigidity of the end plate 1a is increased, it is possible to suppress the deviation of the clearance in the thrust direction between the scroll members and the clearance between the side surfaces of the scroll wrap, which are caused by the bending rigidity, from appropriate values. The configuration and operation of the other parts are the same as those in the fourth embodiment, and therefore the description of the configuration and operation will be omitted.

(Sixth Embodiment) Next, a sixth embodiment of the present invention will be described with reference to FIG. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, and FIG. 9 is a vertical cross-sectional view of the first scroll member side of the present embodiment. In the present embodiment, a cylindrical portion 12c higher than half the height of the scroll wrap 2b is provided on the outer peripheral portion of the front surface of the end plate 2a of the second scroll member 2. The configuration and operation of the other parts are the same as those in the fifth embodiment, and therefore the description of the configuration and operation will be omitted.

According to this embodiment, the rotor of the scroll wrap 1b can be counterbalanced at the center of the height of the scroll wrap 1b on the outer peripheral surface of the top projection 1g.
Since the rotor wrap of the scroll wrap 2b on the outer peripheral surface of the cylindrical portion 12c can be balanced, there is a unique effect that the accuracy of the rotor balance of the scroll members 1 and 2 is improved. Further, due to the effect of the rib of the cylindrical portion 12c, the end plate 2a
Since the bending rigidity of the scroll is increased, it is possible to suppress the deviation of the clearance between the scroll members in the thrust direction and the clearance between the side surfaces of the scroll wrap from the proper values, which is a unique effect.

(Seventh Embodiment) Next, a seventh embodiment of the present invention will be described with reference to FIGS. This embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 10 is a vertical cross-sectional view of the first scroll member side of this embodiment, and FIG. 11 is a perspective view of the first scroll member 1. is there. In this embodiment, in the fifth embodiment, the upper surface projecting portion provided only on the first scroll member 1 is also provided on the second scroll member 2, and the two upper surface projecting portions 1g, 2
The height of g is almost the same. As a result, the tip surfaces of the two upper surface projecting portions 1g and 2g become substantially the center surfaces of the scroll wraps 1b and 2b in the height direction. Therefore, by using this surface as a balancing surface, the rotor balancing of the scroll members 1 and 2 becomes easy.

In this embodiment, the balance ring is not fixedly arranged on the rotary shaft, and the rotor balance of the rotating portion composed of the scroll member and the rotary shaft is adjusted only by the tip surfaces of the upper surface projecting portions 1g and 2g. The balance ring is fixed on the rotating shaft, but the balance may be fixed on the rotary shaft. The configuration and operation of the other parts are the same as those in the fifth embodiment, and therefore the description of the configuration and operation will be omitted.

(Eighth Embodiment) Next, an eighth embodiment of the present invention will be described with reference to FIGS. 12, 13 and 14. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 12 is a vertical cross-sectional view of the first scroll member side of the present embodiment, FIG. 13 is a perspective view of the first scroll member 1, FIG. 14 is a plan view of the first scroll member 1.

The groove plates 1w and 2w face the thrust surfaces 1j and 2j, respectively, to form a dynamic pressure thrust bearing.
In this embodiment, the pin bases 1c and 1e of the sixth embodiment are removed, the pins 1d and 1f are inserted and fixed in the upper surface protruding portion 1g, and the pin holes 2p and 2q are provided in the upper surface protruding portion 2g. Room 1
The above dynamic pressure thrust bearing was formed instead of s and 2s.

As a result, the number of parts can be reduced.
In addition, the present embodiment has a peculiar effect that the scroll portion becomes small and the diameter of the suction chamber can be made small. Further, since the gas flow passage holes 1u and 1v have openings in the direction of rotation, a supercharging action occurs, which has a unique effect of increasing the mass flow rate of gas. The configuration and operation of the other parts are the same as those of the sixth embodiment, and therefore the description of the configuration and operation will be omitted.

(Ninth Embodiment) Next, a ninth embodiment of the present invention will be described with reference to FIGS. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 15 is a vertical cross-sectional view of the first scroll member side of the present embodiment, and FIG. 16 is a perspective view of a back surface holding portion. Gas introduction hole 12 for introducing gas into the crawl wrap portion
The back surface holding portion 12y provided with z is inserted from the first scroll member 1 side in a state where the first scroll member 1 and the second scroll member 2 are engaged with each other, and the second scroll member 2 is inserted.
Screw on. At this time, the surface of the rear surface holding portion 12y facing the rear surface of the mirror plate 1a and the rear surface of the mirror plate are in contact with each other.

This embodiment is the pin hole 2 of the eighth embodiment.
p, 2q and pins 1d, 1f are removed, pins 2d, 2f are inserted and fixed to the end plate 1a side of the back surface holding portion 12y, pin holes 1p, 1q are provided on the end plate of the end plate 1a, and the dynamic pressure thrust bearing 1w is provided. lost. Further, the thrust force that pushes the scroll members 1 and 2 against the dynamic pressure thrust bearing 1w is given by a magnet pull generated by displacing the rotor 7b toward the discharge chamber 15 side and press-fitting it into the rotating shaft 11. As a result, the back surface holding portion 12y can suppress the displacement in which the scroll members 1 and 2 are separated from each other.

In this embodiment, since only one dynamic pressure thrust bearing is required, there is a peculiar effect that the cost can be reduced.
In this embodiment, the pin holes are provided on the first scroll member 1 side and the pins are provided on the second scroll member 2 side, but they may be reversed. Further, the rotation phase difference regulating means is formed by combining two pin holes and pins, but the number may be two or more. The configuration and operation of the other parts are the same as those of the eighth embodiment, and therefore their explanations are omitted.

(Tenth Embodiment) Next, a tenth embodiment of the present invention will be described with reference to FIG. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor.
7 is a vertical cross-sectional view of the first scroll member side of the present embodiment. In this embodiment, the two end plates 1a and 2a in the seventh embodiment are used.
The upper surface projecting portions 1g and 2g that are integrally provided upright are made into separate upper surface projecting members 21 and 22 using a material having a thermal expansion coefficient higher than that of the material forming the scroll wrap. As a result, even if thermal expansion of the scroll wrap portion occurs due to gas compression, the clearance in the thrust direction between the scroll members can be appropriately maintained. The configuration and operation of the other parts are the same as those of the seventh embodiment, and therefore their explanations are omitted.

(Eleventh Embodiment) Finally, an eleventh embodiment of the present invention will be described with reference to FIGS. The present embodiment is a case where the present invention is applied to a hermetic scroll compressor, FIG. 18 is a horizontal sectional view of a scroll member of the present embodiment, and FIG. 19 is a vertical sectional view of a scroll member of the present embodiment. ..

In FIG. 18, the solid line indicates the second scroll member 2,
The broken line indicates the first scroll member 1. This embodiment, of the seventh embodiment, the upper surface protrusion 1g, discharge the 2 g, 12 pieces of ball - le hole _{1x 1, 1x 2, 1x 3} , 1x 4, 1x 5, 1x 6, 1
x _7, 1x _8, Bo has a 1x _9, 1x _10, 1x _11, 1x ₁₂ - fixedly arranged Le stand 1x end plate 1a, furthermore, 12 ball - Le holes _{2x 1, 2x 2, 2x 3} , 2x ₄ , 2x ₅ , 2
_{x 6, 2x 7, 2x 8} , 2x 9, 2x 10, 2x 11, Bo has a 2x ₁₂ - is obtained by fixedly disposed Le stand 2x end plate 2a. Then, the ball 20a is provided in each of these ball holes,
20b, 20c, 20d, 20e, 20f, 20g, 2
The scroll members 1 and 2 are opposed to each other so that 0h, 20i, 20j, 20k, and 20l are inserted therein.

As a result, this portion has the function of restricting the rotational phase difference and suppressing the displacement in the direction in which the end plate approaches. In addition, the twelve boxes in this embodiment are
The barrel may be replaced by a cylinder whose height is equal to the diameter of the ball and whose diameter is equal to the diameter of a small circle whose height contacts the side of the ball hole. As a result, it is possible to reduce the friction of the sliding portion that occurs when the displacement of the scroll members in the directions toward each other is suppressed.

[0105]

Since the present invention is constructed as described above, it has the following effects.

Since the clearance in the thrust direction between the two scroll members and the clearance between the two scroll wrap side surfaces are always kept at a suitable size,
The operating range of high volume efficiency, low vibration, low noise, and high energy efficiency can be greatly expanded to the low speed rotation side and the high speed rotation side. Therefore, there is an effect that it is possible to operate a high-quality scroll fluid machine according to the situation.

Further, since the rotor balance of the scroll member can be easily performed, there is an effect that the operation reliability at the time of high speed operation is improved.

Further, since the rotational force transmission system is simplified, there is an effect that the energy efficiency and the operational reliability in the entire operating range are improved.

Furthermore, since the number of parts can be reduced, there is an effect that the size and cost can be reduced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a first embodiment when the present invention is applied to a compressor.

FIG. 2 is a perspective view of a first scroll member of the first embodiment when the present invention is applied to a compressor.

FIG. 3 is a perspective view of a second scroll member of the first embodiment when the present invention is applied to a compressor.

FIG. 4 is a vertical cross-sectional view of the first scroll member side of the second embodiment when the present invention is applied to a compressor.

FIG. 5 is a vertical cross-sectional view of the first scroll member side of the third embodiment when the present invention is applied to a compressor.

FIG. 6 is a vertical sectional view of a first scroll member side of a fourth embodiment when the present invention is applied to a compressor.

FIG. 7 is a perspective view of a first scroll member of a fourth embodiment when the present invention is applied to a compressor.

FIG. 8 is a perspective view of a first scroll member of a fifth embodiment when the present invention is applied to a compressor.

FIG. 9 is a vertical cross-sectional view of a first scroll member side of a sixth embodiment when the present invention is applied to a compressor.

FIG. 10 is a vertical cross-sectional view of the first scroll member side of the seventh embodiment when the present invention is applied to a compressor.

FIG. 11 is a perspective view of a first scroll member of a seventh embodiment when the present invention is applied to a compressor.

FIG. 12 is a vertical cross-sectional view of the first scroll member side of the eighth embodiment when the present invention is applied to a compressor.

FIG. 13 is a perspective view of a first scroll member of an eighth embodiment when the present invention is applied to a compressor.

FIG. 14 is a plan view of a first scroll member of an eighth embodiment when the present invention is applied to a compressor.

FIG. 15 is a vertical cross-sectional view of the first scroll member side of the ninth embodiment when the present invention is applied to a compressor.

FIG. 16 is a perspective view of a back surface holding portion of the ninth embodiment when the present invention is applied to a compressor.

FIG. 17 is a vertical cross-sectional view of the first scroll member side of the tenth embodiment when the present invention is applied to a compressor.

FIG. 18 is a transverse sectional view of a scroll member of an eleventh embodiment when the present invention is applied to a compressor.

FIG. 19 is a vertical sectional view of a scroll member of an eleventh embodiment when the present invention is applied to a compressor.

[Explanation of symbols]

1 1st scroll member 2 2nd scroll member 1a, 2a End plate 1b, 2b Scroll wrap 1c, 1e Pin stand 1d, 1f Pin 1g, 2g Upper surface protrusion part 1h, 1i Gas channel groove 1j, 2j Thrust Surface 1k, 2k Lower surface protruding portion 1l Shaft coupling portion 1m, 2m Female side spline shaft coupling 1n Journal bearing facing surface 1o, 2o Intermediate pressure hole 1r, 2r Lap balance recessed portion 1s, 2s Intermediate pressure chamber 1t, 2t Outlet outlet 1u , 1v gas passage holes 1w, 2w, 3q, 4q, 9d, 10d Group - Bed plate 1x, 2x ball - Le stand _{1x 1 ~1x 12, 2x 1 ~2x} 12 ball - Le holes 1y, 2y end plate groove 1z, 2z Deep groove ball bearing 2p, 2q Pin hole 3, 4 casing 3a, 4a Scroll chamber forming part 3b, 4b Suction port 3c, 3f, 3g, 3i, 4c, 4f, 4g, 4i Flange 3 4d Motor chamber forming part 3e, 4e Discharge port 3h, 4h Fin 3j Partition wall 3k Journal sliding bearing 3l, 4l Oil hole 3m Intermediate pressure chamber recess 3n Cylindrical groove 3o, 3s, 4s, 4o Guide 3p, 4p Gas blocking wall 3r, 4r Motor chamber 5, 6 Cylinders 5a, 6a Cooling water inlet 5b, 6b Cooling water outlet 5c, 6c Flange 5d, 5e, 6d, 6e O-ring 5f, 6f Water jacket 7, 8 Motor 7a, 8a Stater 7b, 8b Rotor 7c, 8c Electric wire 7d, 8d Gap 9,10 Support plate 9a, 10a Rolling bearing 9b, 10b, 13a, 14a, 19b, 19c O-ring 9c, 10c Hole 11, 12 Rotating shaft 11a, 11b, 12a, 12b Balance ring 11c Male side spline shaft coupling 11d, 12d Through hole 12c Cylindrical part 1 y Rear surface holding portion 12z Gas introduction hole 13, 14 Side wall 13b, 14b Terminal 15, 16 Discharge chamber 17, 18 Lubricating oil 19 Suction chamber 19a Spacer 19d Discharge port Suction port 19d 20a to 20l Ball 21, 22 Top surface protrusion Element

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazutaka Sudo, 502 Kintatemachi, Tsuchiura City, Ibaraki Prefecture Inside the Hiritsu Seisakusho Co., Ltd.

Claims (13)

[Claims] 1. A first scroll member formed by a first end plate and a first scroll wrap standing upright on the first end plate, and a second scroll formed by a second end plate and a second scroll wrap standing upright on the second end plate. And a scroll member, and the first and second scroll members are eccentrically and axially supported, while maintaining a minute clearance between the scroll wraps and between the tip of the scroll wraps and the end plate facing it. The first and second scroll members are arranged so that the first and second scroll members rotate in the same direction and at substantially the same speed to reduce or expand the volume of the substantially closed space formed by the scroll wrap and the end plate. In the scroll fluid machine, the two scroll members of the first and second scroll members are mutually arranged in a thrust direction. Rotary scroll fluid machine characterized in that it comprises a means for suppressing displacement away and approach. 2. A thrust direction displacement restraining means for the two scroll members is provided on at least a front surface side where the scroll wraps of the first and second end plates are erected, or a back surface side where they are not erected. Item 1. A rotary scroll fluid machine according to Item 1. 3. The displacement restraint means in a direction in which the two scroll members approach each other has a protrusion provided upright on one surface of the first or second end plate, and a tip portion of the protrusion is provided. The rotary scroll fluid machine according to claim 2, wherein the end plate is slidably contactable with the other surface. 4. The rotary scroll fluid machine according to claim 3, wherein the protrusion is formed in an annular shape. 5. The displacement restraint means in the direction in which the two scroll members approach each other has projections provided upright on both surfaces of the first and second end plates, and the tip surfaces of the projections are mutually opposed. The rotary scroll fluid machine according to claim 2, which is capable of sliding contact. 6. The rotary scroll fluid machine according to claim 5, wherein at least one of the protrusions is formed in an annular shape. 7. The rotary scroll fluid machine according to claim 5, wherein the protrusions have substantially the same height. 8. The displacement restraint means in a direction in which the two scroll members approach each other is rollable in a state capable of sliding contact with the front surfaces of the first and second end plates. The rotary scroll fluid machine according to claim 2, further comprising a rolling member. 9. The displacement restraint means in a direction in which the two scroll members approach each other, at least a part of which is a displacement restraint in a direction in which the two scroll members provided on the back side of the two end plates are separated from each other. 9. The rotary scroll fluid machine according to claim 3, wherein the rotary scroll fluid machine is located inside the outermost periphery of the installation range of the means. 10. All of at least one of the protrusions of the scroll member or all of the rolling members are made of a different composition or different structure material having a coefficient of thermal expansion larger than that of the material forming the scroll wrap. Item 10. The rotary scroll fluid machine according to any one of Items 3 to 9. 11. A rotary drive unit that supplies a rotational force to each of the first and second scroll members, or a rotational force supplied from each of the first and second scroll members, respectively. The rotary scroll fluid machine according to claim 1, wherein the rotary scroll fluid machine has a separate rotary passive portion. 12. The rotary scroll fluid machine according to claim 11, further comprising rotation phase difference regulating means for keeping the rotation phase difference between the first scroll member and the second scroll member within a certain range. 13. The rotation phase difference restricting device, in whole or in part, also serves as at least one of a displacement suppressing device in a direction in which the two scroll members are separated from each other or a displacement suppressing device in a direction in which they approach each other. Claim 1
2. The rotary scroll fluid machine described in 2.