JPH11125189A - Fluid compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid compressor which shortens the whole length of the compressor by relatively overlapping the respective end parts of an electric motor part and a compression mechanism part, thereby makes miniaturization effective, and concurrently, enhance its assembling properties. SOLUTION: This fluid compressor possesses a helical plate type compression mechanism part 3 provided with a cylinder 5, a roller 10 disposed in the inside of the cylinder 5, and with a spiral shaped blade 12 interposed between the roller and the cylinder 5, and also possesses an electric motor part 4 formed out of a rotor 23, and of a stator 24, which are connected by way of the compression mechanism part 3 and a rotating shaft 2, and drivingly rotates the roller of the compression mechanism part 3. And the cylinder 5 consisting of the compression mechanism part, has its one end part inserted and fitted in the inner diameter part of the stator 24, so that the cylinder is thereby supported by the aforesaid stator.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor provided with a helical blade type compression mechanism and used for, for example, a refrigeration cycle apparatus to compress a refrigerant gas as a gas to be compressed.

[0002]

2. Description of the Related Art A fluid compressor called a helical blade type compressor has been proposed. In this case, a cylinder constituting a compression mechanism is disposed in a closed case, and rollers are eccentrically disposed in the cylinder, and revolve or rotate. A spiral groove is provided on the peripheral surface of the roller or the inner surface of the cylinder, and the blade is housed in a freely accessible manner.

A plurality of compression chambers are formed between the cylinder, rollers and blades, and refrigerant gas is sucked into one end of the compression chamber and compressed while being gradually transferred to the other end. .

According to this type of compressor, it is possible to eliminate the poor sealing performance of the conventional reciprocating or rotary type compressor, and to improve the sealing performance with a relatively simple structure to achieve efficient compression. While possible, the manufacture and assembly of the parts is facilitated.

[0005]

The helical blade type compression mechanism is connected to an electric motor via a rotary shaft, and the compression mechanism is driven by the electric motor rotating the rotary shaft. Works.

That is, in this type of compressor, as in the case of a reciprocating type or rotary type compressor, a compression mechanism section and an electric motor section are connected in series via a rotating shaft. The total length becomes longer.

[0007] If the vertical type, the height is high, if the horizontal type, the required arrangement space becomes large, the assemblability of piping parts connected to this compressor is impaired, the unit is large It will lead to conversion.

The present invention has been made based on the above circumstances, and an object of the present invention is to reduce the overall length by wrapping the ends of a motor section and a compression mechanism section.
Accordingly, it is an object of the present invention to provide a fluid compressor which can be reduced in size and improved in assemblability.

[0009]

According to a first aspect of the present invention, there is provided a fluid compressor comprising: a cylinder;
A rotator disposed in the cylinder, a helical blade type compression mechanism including a helical blade and the like interposed between the rotator and the cylinder, and a compression mechanism and a rotary shaft. One end of the compression mechanism is connected to a fluid compressor including a motor unit including a rotor and a stator that rotationally drives a rotating body of the compression mechanism.
It is characterized in that it is supported by being inserted into an inner diameter part of the stator constituting the motor part.

According to a second aspect of the present invention, in the fluid compressor according to the first aspect, one end of the compression mechanism is inserted into and supported by the inner diameter of the stator. According to a third aspect of the present invention, in the fluid compressor according to the second aspect, the compression mechanism portion includes a main bearing that pivotally supports the rotary shaft, and an outer diameter of the main bearing is the same as an inner diameter of the cylinder. The main bearing is disposed at one end, and one end of the cylinder on the main bearing side is inserted into and supported by the inner diameter of the stator.

According to a fourth aspect of the present invention, in the fluid compressor according to the second or third aspect, insulating means is provided between the compression mechanism and the coil end of the stator.

According to a fifth aspect, in the fluid compressor according to the fourth aspect, the insulating means is an insulating film attached to an outer peripheral surface of the cylinder. Claim 6
According to a second aspect of the present invention, in the fluid compressor according to the second aspect, the rotor constituting the electric motor unit is provided so as to be displaced in the axial direction from the stator to the side opposite to the compression mechanism unit, and one end of the compression mechanism unit is provided at the position shifted. Is inserted.

According to a seventh aspect of the present invention, in the fluid compressor according to the first or second aspect, the rotary shaft is pivotally supported by a sub bearing together with the main bearing, and the rotary shaft projects from the sub bearing and pivots. A balance weight is provided on the protruding portion of the rotating shaft.

According to an eighth aspect of the present invention, in the fluid compressor according to the second aspect, a portion of the compression mechanism, which is supported on a peripheral surface of the inner diameter portion of the stator, is made of a non-magnetic material. According to a ninth aspect of the present invention, in the fluid compressor according to the second aspect, a portion of the compression mechanism, which is supported on a peripheral surface of the inner diameter portion of the stator, is made of a non-conductive material.

According to a tenth aspect of the present invention, in the fluid compressor according to the second aspect, the compression mechanism portion includes a main bearing that pivotally supports the rotating shaft, and the main bearing includes a flange portion inserted into the cylinder. And a mounting portion protruding from the cylinder and supported on the peripheral surface of the inner diameter portion of the stator.

According to an eleventh aspect, in the fluid compressor according to the tenth aspect, an end plate is provided on the flange portion of the main bearing, and the end plate is supported on a peripheral surface of the inner diameter portion of the stator. .

According to a twelfth aspect, in the fluid compressor according to the second or third aspect, the inner peripheral portion of the stator has a stepped notch, and one end of the compression mechanism portion is supported by the stepped portion. It is characterized by that.

According to a thirteenth aspect, in the fluid compressor according to the first aspect, in the rotor constituting the electric motor portion, end rings provided at both ends thereof are formed to be asymmetric with respect to each other, so that the rotor has a structure similar to the compression mechanism portion. The thickness of the end ring is formed to be smaller than the thickness of the end ring on the side opposite to the compression mechanism.

According to a fourteenth aspect, in the fluid compressor according to the second, third or seventh aspect, a semi-hermetic cover having a gas hole is provided at an end of the stator on the side opposite to the compression mechanism. It is characterized by.

According to a fifteenth aspect, in the fluid compressor according to the second, third, or tenth aspect, the compression mechanism and the electric motor are housed in a closed case, and the other end of the compression mechanism is It is characterized in that it is supported on the bottom of the sealed case. By providing the means for solving such a problem, the electric motor unit and the compression mechanism unit are in a wrapped state, so that the overall length is reduced and the size is reduced.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, in the fluid compressor A, a discharge side refrigerant pipe Pa is connected to an upper surface part, and a suction side refrigerant pipe Pb is connected to a side part. This discharge side refrigerant pipe Pa
, A condenser B, an expansion valve C forming a pressure reducing mechanism, and an evaporator D are sequentially communicated from each other to a suction side refrigerant pipe Pb, thereby constituting, for example, a refrigeration cycle of an air conditioner.

The fluid compressor A has a so-called helical blade type compressor. The compressor A has a helical blade type compressor connected via a rotating shaft 2 in a sealed case 1. The mechanism unit 3 and the electric motor unit 4 are housed.

The compression mechanism 3 is provided with a cylinder 5 which is a thin hollow cylindrical body whose both ends are open. A flange 6 is fixed to the outer peripheral surface of the cylinder 5, and the flange 6 is also fixed to the inner peripheral portion of the closed case 1, so that the cylinder 5 is supported by the closed case 1 via the flange 6. Will be.

Actually, there is a slight dimensional difference between the outer diameter of the flange 6 and the inner diameter of the sealed case 1, and the flange 6 is fixed by a laser welding means from outside the sealed case 1 while the flange 6 is temporarily held by a jig (not shown). Is what is done.

A predetermined portion of the flange 6 is provided with a lubricating oil return hole 6a described later. An insulating film 7 as an insulating means is adhered to an outer peripheral surface of the cylinder 5 projecting upward from the flange 6, and the portion is covered over the entire surface.

The flange 8a of the main bearing 8 is inserted into the upper end of the cylinder 6. The main bearing 8 has a flange portion 8a.
And a bearing portion 8b having a smaller diameter than the flange portion 8a are integrally connected to each other, and respectively rotatably support the rotary shaft 2.

The flange 9a of the auxiliary bearing 9 is inserted into the lower end of the cylinder 5. This auxiliary bearing 9 has a flange portion 9a.
And a bearing portion 9b having a smaller diameter than the flange portion 9a are integrally connected to each other, and rotatably support the end of the rotating shaft 2 respectively.

In the cylinder 5 between the main bearing 8 and the sub-bearing 9 and around the rotating shaft 2, the roller 1 as a rotating body is provided.
0 is interposed. The lower surface of the roller 10 receives the thrust force applied from the upper side to the lower side of the roller 10 by the upper surface of the sub bearing flange portion 9a.

The outer diameter of the roller 10 and the inner diameter of the cylinder 5 have a predetermined dimensional difference, and a crank portion 2a eccentric by the dimensional difference is provided integrally with the rotary shaft 2 at an intermediate position. That is, the crank portion 2a is inserted into a lumen pivotal support portion 10a provided on the roller 10, and a part of the outer peripheral wall of the roller 10 is dimensioned so as to roll along an axial direction with a part of the inner peripheral wall of the cylinder 2. I have.

The roller 10 has an upper portion and a lower portion of a lumen pivot portion 10a, and an upper concave portion 10a.
The bearing 8b of the main bearing 8 is inserted into the lower bearing b, and the bearing 9b of the auxiliary bearing 9 is inserted into the lower recess 10c.

A spiral groove 11 is formed on the outer peripheral surface of the roller 10 so as to gradually decrease the pitch from the end on the side where the auxiliary bearing 9 is attached to the end on the side where the main bearing 8 is attached.
A helical blade 12 is wound around the helical groove 11 so as to freely enter and exit.

The blade 12 is formed of a fluororesin material, and has an inner diameter larger than the outer diameter of the roller 10. That is, the blade 12 is forcibly fitted in the spiral groove 11 in a state where the diameter thereof is reduced, and as a result, the outer peripheral surface of the blade 12 is always Bulging and deforming so as to elastically abut against the surface.

When the rotary shaft 2 rotates, the crank 2a
Make an eccentric rotation, and the roller 10 pivotally supported on the outer peripheral surface of the crank portion 2a makes an orbital movement that is an eccentric movement. With the revolving motion, the rolling contact portion of the outer peripheral wall of the roller 10 with the inner peripheral wall of the cylinder 5 gradually moves along the circumferential direction of the cylinder 5.

When the roller 10 revolves and the rolling contact position with respect to the cylinder 5 moves, the blade 12 sinks into the spiral groove as the rolling contact portion approaches, and the outer peripheral surface of the blade 12 at the rolling contact position It is completely identical to the outer peripheral surface of the roller 10.

Conversely, when the rolling contact portion passes, the blade 12 projects from the spiral groove 11 according to the distance from the rolling contact portion,
The rolling contact portion is a portion that faces 180 ° via the axis, and the protruding length of the blade 12 is maximized. After this, the above-described operation is repeated because the vehicle approaches the rolling contact portion again.

When the cylinder 5 and the roller 10 are sectioned along the radial direction, the roller 10 is accommodated eccentrically with respect to the cylinder 5 and a part of the peripheral surface of the roller 10 is in rolling contact with the cylinder 5. From a certain point, a crescent-shaped space is formed between the cylinder 5 and the roller 10.

When this space is viewed along the axial direction, the blade 12 is wound around the spiral groove 11 and the outer peripheral surface of the roller 10 is in rolling contact with the inner peripheral wall of the cylinder 5. Is partitioned into a plurality of spaces by the blade 12.

The space divided into a plurality of the compression chambers 1
Called 3. From the setting of the spiral groove 11, each compression chamber 13
The volume from the side end of the auxiliary bearing 9 to the end of the main bearing 8 is
The volume gradually decreases.

The suction side refrigerant pipe Pb penetrates through the closed casing 1 and has an end attached to a suction hole 14 provided at the lower part of the cylinder 5 so that the open end faces the lowermost compression chamber 13. I can't.

The position of the suction side refrigerant pipe Pb and the spiral groove 1
From the setting of the pitch of 1, the lowermost compression chamber 13 becomes the suction part e, and the uppermost compression chamber 13 becomes the discharge part f. The discharge portion f and the inside of the sealed case 1 are provided on the flange portion 8a of the main bearing 8 and have a concave portion 15 whose upper surface is opened,
The gas discharge hole 16 penetrates through the bottom of the recess 15 and the bottom of the flange 8a.

A roller anti-rotation member 17 protruding from the end face of the roller 10 is inserted into the recess 15 and the gas discharge hole 16. Due to the presence of the roller rotation preventing member 17, the roller 10 performs only the revolving motion and regulates the rotating motion.

A single groove 18 is provided along the peripheral surface of the lower concave portion 10c of the roller 10, and the seal ring 1
9 is inserted. The seal ring 19 has a function of sealing the pressure of the inner diameter of the roller 10 on the high pressure side and the cylinder suction hole 14 on the low pressure side to prevent gas leakage.

The lower end of the rotary shaft 2 projects downward from the auxiliary bearing flange 9a, and the first balance weight 20 is fitted thereto. Further, the balance 8 and the lower end of the rotating shaft 2 are covered by a thrust plate 21 attached to the lower end of the cylinder 5. That is, the thrust plate 21 closes the lower end opening of the cylinder 5.

On the other hand, an oil reservoir 22 for collecting lubricating oil is formed on the inner bottom of the sealed case 1. This oil sump 2
Part of the compression mechanism 3 is immersed in the lubricating oil 2. The thrust plate 21 prevents lubricating oil from entering the enclosed space where the first balance weight 20 is mounted.

The rotating shaft 2 is provided with lubricating oil in the oil reservoir 22, the rotating shaft 2 and the auxiliary bearing 9, the crank portion 2a and the roller bore pivotal support 10a, the rotating shaft 2 and the main bearing 8, the roller 10 and the cylinder. 5, and an oil supply passage (not shown) for guiding each sliding portion such as the blade 12 and the spiral groove 11 are provided.

The electric motor unit 4 is sealed with respect to such a helical blade type compression mechanism unit 3 with a rotor 23 fitted on the rotating shaft 2 and a predetermined gap from the peripheral surface of the rotor 23. And a stator 24 fitted to the case 1.

Although the rotor 23 and the stator 24 have the same axial length, the rotor 23 is attached to the stator 24 with its position shifted to the upper side. That is, the rotor 23 protrudes toward the anti-compression mechanism 3 side.

A plurality of gas guide holes 25 penetrate the rotor 23 along the axial direction. A disk 26 is provided at the upper end of the rotor 23 so as to face the gas guide holes 25 at a predetermined interval.

The second balance weight 27 is mounted on the upper end surface of the rotor 23. This second balance weight 2
Numeral 7 cancels the unbalanced mass of the roller 10 together with the first balance weight 20 provided at the lower end of the rotating shaft 2.

A plurality of oil return notches 28 are provided on the outer peripheral surface of the stator 24 along the axial direction to form a gap with the inner peripheral wall of the closed case 1.
One end of the compression mechanism 3 is inserted into the lower end of the inner diameter of the stator 24. That is, the upper end of the cylinder 5 that forms the compression mechanism 3 is inserted into the inner peripheral surface of the stator 24 via the coil end 24a. In addition, as described above, since the rotor 23 is displaced upward with respect to the stator 24, the cylinder 5 is inserted into this blank portion.

Then, together with the cylinder 5, the flange 6
The components of the compression mechanism 3 on the upper side from the mounting part are inserted into the stator coil end 24a, but the insulating film 7 adhered to the upper outer peripheral surface of the cylinder 5 is the compression mechanism 3 of the stator 24 and the stator coil 24a. Provides electrical insulation for

This is a helical blade type fluid compressor constructed as described above, and energizes the electric motor unit 4 to rotate the rotary shaft 2 together with the rotor 23 integrally. Rotary axis 2
Is transmitted to the roller 10 via the crank portion 2a, and the roller 10 makes a revolving motion by the roller rotation preventing member 17.

With the revolving motion of the roller 10, the rolling contact position of the roller 10 with respect to the inner peripheral surface of the cylinder 5 gradually moves in the circumferential direction, and the blade 12 moves in and out of the spiral groove 11. That is, the blade 12 moves in the radial direction of the roller 10.

By these series of operations, the suction side refrigerant pipe P
Low pressure refrigerant gas is sucked from b and directly led to the lower compression chamber 13 which is the suction portion e in the cylinder 5. After the blade 12 is formed in a spiral shape, the blade 12 is sequentially transferred to the compression chamber 13 in the upper direction according to the revolving motion of the roller 10.

Since the volume of the compression chamber 13 is sequentially reduced from the lower side to the upper side due to the pitch shape of the blades 12, the refrigerant gas is compressed while being sequentially transferred through each compression chamber 13, and becomes the uppermost side. The pressure rises to a predetermined pressure in the compression chamber 13 and becomes higher.

The high-pressure gas is discharged from the compression chamber 13 as the discharge portion f, discharged from the gas discharge holes 16 provided in the main bearing 8 into the sealed case 1, and further flows through the gas guide holes 25 provided in the rotor 23. The lubricating oil contained in the high pressure gas is once separated by colliding with the disk 26.

In particular, the rotor 2 rotating the gas guide hole 25
3, the high-pressure gas and the lubricating oil contained therein can be accelerated to collide with the disk 26. Therefore, the disk 26 reliably separates the heavy oil. Moreover, since the discharge-side refrigerant pipe Pa is mounted directly above the disk 26, the suction of oil into the refrigerant pipe Pa is reliably prevented.

The lubricating oil separated by the disk 26 is returned to the oil reservoir at the bottom of the closed case 1 via an oil return notch 28 provided in the stator 24. The high-pressure gas is discharged from the discharge-side refrigerant pipe Pa, guided to the condenser B, and is further sucked into the compressor A via the expansion valve C and the evaporator D, thereby forming a known refrigeration cycle.

As described above, the cylinder 5 constituting the compression mechanism 3 and a part of the insulating film 7 are interposed in the stator 24 constituting the electric motor 4, and a part of the cylinder 5 and an upper end thereof are provided. The provided main bearing 8, a part of the roller 10 and the blade 12, and the insulating film 7 are all inserted into a stator coil end 24 a constituting the electric motor unit 4.

That is, since the compression mechanism 3 and the electric mechanism 4 connected via the rotation shaft 2 are assembled in a state of being wrapped along the rotation shaft 2, the compression mechanism 3 and the electric mechanism 4 are different from the conventional fluid compressor. Compared to a structure in which the compression mechanism and the electric mechanism are simply arranged in series along the axial direction of the rotating shaft, the length in the axial direction is reduced, and the sealed case 1 for accommodating them is reduced.
Can be downsized. This leads to downsizing of the air conditioner unit accommodating the compressor A, which contributes to reduction of the space in which the units are arranged.

The concentricity of the cylinder 5 and the inner diameter of the stator 24 can be ensured with high accuracy, and the cylinder 5 is connected to the stator 24 via the main bearing 8, the sub-bearing 9 and the rotary shaft 2.
There is an advantage that the concentricity between the rotor and the rotor 23 can be ensured with high accuracy.

Since the cylinder 5 guides the inner diameter of the stator 24, the air gap between the stator 24 and the rotor 23 is made uniform, so that the assembling accuracy can be improved.

The outer diameters of the main bearing 8 and the sub bearing 9 are formed to be the same as the inner diameter of the cylinder 5, and these main bearings 8
And the auxiliary bearing 9 are arranged, so that the overall length of the compression mechanism 3 itself can be reduced.

In practice, the main bearing 8 and the sub-bearing 9 are fixed by laser welding from the peripheral surface of the cylinder 5, so that heat input during welding can be minimized, and the deformation of the cylinder 5 can be reduced. Can be prevented.

In other words, even if the cylinder 5 is thin, sufficient rigidity can be maintained, and bolts are not required for assembling. Simplification and cost reduction.

Since the upper end of the cylinder 5 is inserted into the inner diameter of the stator 24, all the high-pressure gas discharged from the compression chamber 13 can be reliably supplied to the gas guide holes 25 provided in the rotor 23 through the gas discharge holes 16. Can be led to.

At this time, the inner diameter of the stator 24 becomes a rotor cover, and the inner diameter of the stator 24, the main bearing 8 and the rotor 2
3, a predetermined space is formed, and noise generated by discharge of the refrigerant gas can be reduced by the muffler effect of this space.

Further, when a large amount of refrigerant is mixed into the lubricating oil in the oil sump 22, the oil level becomes lower than the stator 24.
Even if it rises to the lower end, the suction of oil from the gas discharge holes 16 into the cylinder 5 can be prevented by the rotor cover effect.

An insulating film 7 made of a non-conductive material is wound around the cylinder 5, and the compression mechanism 3 and the motor 4
Are electrically insulated from each other, so that the compression mechanism section 3 and the electric motor section 4 can be arranged as close as possible.

Since the seal ring 21 is assembled so as to allow a slight leak, the lubricating oil staying in the inner diameter of the roller 10 and the lubricating oil leaking from the auxiliary bearing 9 to the space for mounting the first balance weight 20 are not removed. It leaks to the compression chamber 13 on the suction part e side via the lower end surface of the roller 10.

Accordingly, the lubricating oil seals and lubricates the clearance between the outer diameter of the blade 12 and the roller 10 in the cylinder 5 and the inner diameter of the cylinder 5, thereby preventing gas leakage and wear in the cylinder 5.

The lower end of the rotary shaft 2 is connected to the auxiliary bearing flange 9a.
From the first balance weight 20
Is more effective means for canceling the eccentric mass of the roller 10.

Hereinafter, a modified example of the above-described embodiment will be described with reference to FIG. 2 and the following drawings. Components other than those described below are the same as those described above, and thus the same reference numerals are given and a new description is omitted. I do.

As shown in FIG. 2, by replacing the portion of the cylinder 5 supported by the stator 24 with a ring 30 of a non-magnetic material such as stainless steel or aluminum, the compression mechanism 3 is replaced with the electric motor 4. An adverse effect on the electromagnetic characteristics of the motor unit 4 when inserted can be minimized.

As shown in FIG. 3, the stator 24A has a step 31 formed along the inner diameter of the lower end thereof, and a cylinder 5C in which a similar step 32 is formed may be fitted. In this case, since the inner diameter of each of the stator 24A and the cylinder 5C is set to be the same, the position of the rotor 23 can be correctly opposed to the stator 24A without bringing the rotor 23 and the cylinder 5C into contact with each other. The drop can be prevented.

The stepped portions 31 and 32 between the stator 24A and the cylinder 5C form the stator 24 of the cylinder 5C.
The insertion depth into A is determined uniformly, and the insertion accuracy and manufacturability are improved.

The compressor Aa shown in FIG. 4 is a compressor A shown in FIG. 1 which is a high-pressure type in a case where a high-pressure gas is filled in a closed case 1. The low pressure type in the case where the low pressure gas introduced from is filled.

That is, the refrigerant gas introduced from the evaporator D is supplied to the suction side refrigerant pipe Pb connected to the upper end of the closed case 1.
From the gap between the disk 26 and the rotor 23 in the case 1, the gas is guided to a gas guide hole 25 provided in the rotor 23.

Then, the gas is sucked from a gas hole 16 provided in a main bearing 8A, which will be described later, into a compression chamber 13 formed in a cylinder 5A having a structure different from that of FIG. 1, and is sequentially transferred and compressed. Since the pitch of the spiral groove 11 provided in the roller 10 is formed so as to gradually decrease from the upper side to the lower side, the compression capacity of the compression chamber 13 also gradually decreases from the upper side to the lower side.

Therefore, when the gas is discharged from the lower compression chamber 13, the pressure rises to a predetermined pressure, and this high-pressure gas is discharged from the discharge side refrigerant pipe Pa provided on the lower side surface of the closed case 1 to the condenser B to be cooled. Make up the cycle.

Here, the main bearing 8 is connected to the cylinder 5
A is composed of a flange portion 8a and a bearing portion 8b inserted into A, and a mounting portion 8c protruding from the upper end edge of the cylinder 5A and inserted into the inner diameter portion of the stator 24.

Accordingly, since the rigid main bearing 8 is inserted into the inner diameter portion of the stator 24, deformation during insertion of the cylinder 5A can be prevented as much as possible.
The pivotal support length of b with respect to the rotation shaft 2 is extended, and the rotation shaft 2 can be pivotally supported with higher accuracy.

On the other hand, the lower end 5b of the cylinder 5A is extended downward as it is and is brought into contact with the bottom surface of the closed case 1. The end of the rotating shaft 2 protrudes from the lower surface of the auxiliary bearing 9 and the first end
The balance weight 20 is fitted. Therefore, the balance weight 20 is located in a closed space formed by the cylinder 5A, the closed case 1 and the auxiliary bearing 9.

The lower end of the cylinder 5A, which is in contact with the bottom surface of the closed case 1, is welded from the outside of the closed case 1 all around. The compression mechanism 3 includes an inner diameter of the stator 24 via the upper end of the cylinder 5A, a sealed case 1 via the mounting flange 6, and a sealed case 1 via the lower end of the cylinder 5A.
Since it is supported at three places with the bottom surface, the alignment work becomes easy.

Such a low-pressure compressor in the case is effective for preventing the liquid from being sucked into the cylinder 5A. That is, when the refrigerant introduced from the suction side refrigerant pipe Pb connected directly above the disk 26 contains a liquid component, the mass of the liquid refrigerant is large, so that the rotating disk 26 and the rotor 2
It is difficult to pass between 3.

On the other hand, the dry gas having a small mass easily flows through the gas guide hole 25 provided in the rotor 23 and is sucked into the compression chamber 13 in the cylinder 5A. Here, the so-called liquid separation effect is ensured, and the liquid hammering phenomenon does not occur in the cylinder 5A, so that the reliability can be improved.

As shown in FIG. 5, the main bearing 8B comprises a flange portion 8e inserted into the cylinder 5B, and a mounting portion 8f integrally connected to the flange portion 8e and protruding from the peripheral edge of the flange portion 8e. Is done. That is, here, the cylinder 5B is fitted to the main bearing 8B, and the mounting portion 8f of the main bearing 8B is inserted and supported by the stator 24.

As described above, the mounting portion 8f of the main bearing 8B serves as a rotor cover, and the inside of the mounting portion 8f and the rotor 2
A predetermined space is formed between the rotor 2 and the rotor 2.
Since the suctioned refrigerant is guided through the passage 3, a sufficient suction amount can be secured, and the refrigeration capacity and the compression capacity can be improved by improving the suction efficiency.

When the structure shown in FIG. 5 is applied to a high-pressure type in a case, the mounting portion 8f serves as a rotor cover, and the inside of the mounting portion 8f of the main bearing 8B and the rotor 23
And a predetermined space is formed between them, and the noise generated by the discharge of the refrigerant gas is reduced by the muffler effect of this space.

Furthermore, even if a large amount of refrigerant is mixed into the lubricating oil in the oil reservoir, the oil level may rise to the lower end of the stator 24, but even if the oil level rises to the lower end of the stator 24, the gas suction hole (in the case In the case of a high-pressure type, it is possible to prevent oil from being sucked into the cylinder 5B from the discharge hole).

As shown in FIG. 6, as the motor section 4A,
When an AC motor is used, end rings 33 a and 33 b are formed on both upper and lower end surfaces of the rotor 23. here,
The thickness H1 of the upper and lower rotor end rings 33a, 33b,
The lower end ring 33b facing the compression mechanism (not shown) is made thin (H1> H2) so that a sufficient space for inserting the compression mechanism into the stator 24 is secured. The thickness of the upper rotor end ring 33a is increased.

As shown in FIG. 7, a helical blade type compressor of a high pressure type in a case may be used. The auxiliary bearing 9A fitted to the lower end opening of the cylinder 5 has its flange 9c side end protruding from the opening end of the cylinder 5 and is supported by the bottom of the closed case 1. The auxiliary bearing flange portion 9c is fixed to the closed case 1 by laser welding means applied from the outer surface of the closed case 1.

Therefore, the compression mechanism 3 is supported by the bottom of the sealed case 1 via the auxiliary bearing 9A. In particular, the cylinder 5 is prevented from being inclined with respect to the sealed case 1 by the auxiliary bearing 9A.

The end face of the auxiliary bearing 9A on the contact side of the sealed case 1 is formed with a recess except for the peripheral portion, and the recess 9d is formed.
A thrust plate 35 is attached to the bottom surface, and a general positive displacement oil pump 36 is provided. An oil pipe 37 is connected to the peripheral surface of the lower end of the cylinder 5,
Rotary shaft 2 from cylinder 5 and outer peripheral surface of auxiliary bearing flange 9c
It is communicated with an oil guide hole 38 provided over the inner peripheral surface on the pivot side.

A rotor cover 39 is attached to the upper end surface of the stator 24. The rotor cover 39 has a bowl shape that is closed at a predetermined interval from the upper end surface of the rotor 23, and forms a semi-hermetic cover from the place where the gas vent hole 40 is provided on the peripheral surface.

With such a configuration, in addition to being used as a so-called vertical compressor in which the V surface is an installation surface and the discharge side refrigerant pipe Pa is on the upper part, the H surface is an installation surface and the suction side is It can also be used as a so-called horizontal compressor with the refrigerant pipe Pb at the top.

That is, in both the vertical type and the horizontal type, when the low-pressure gas is sucked from the suction side refrigerant pipe Pb and compressed to a predetermined pressure in the compression chamber 13, the main bearing 8
Are discharged from the gas discharge holes 16.

Then, it is led to the upper end of the rotor 23 through a gas guide hole 25 a provided in the rotor 23, exits from the gas vent hole 40 of the rotor cover 39 to the upper end space of the sealed case 1, and is connected to the discharge side refrigerant pipe Pa. Will be led.

On the other hand, when the compressor is of a horizontal type, the oil pipe 37 side is the inner bottom of the sealed case 1 to form the oil reservoir 22, and the oil pipe 37 and the stator 2
4 Part is immersed in lubricating oil. The oil pump 36 operates with the rotation of the rotating shaft 2, sucks lubricating oil from the oil pipe 37, and supplies the oil to an oil supply passage (not shown) formed on the peripheral surface of the rotating shaft 2. This refueling configuration is the same even in the case of the vertical type.

A problem particularly in the case of the horizontal type is interference of the lubricating oil with the oil level due to the rotation of the rotor 23. That is, when the liquid back phenomenon of the refrigerant occurs at the time of starting the compressor or the like, the oil level rises due to the influence of the liquid refrigerant, and a part of the rotor 23 is immersed. May be caused.

However, in the configuration shown in the figure, the compression mechanism 3 is directly fixed to the inner diameter of the stator 24, and the rotor cover 39 is provided at the upper end of the stator 24 to close the upper end surface of the rotor 23. Interference with the oil level can be prevented, and there is no lubrication oil discharge.

The rotor 23 has a gas guide hole 25a having a diameter larger than that of the gas guide hole 25 of FIG.
And the gas guide hole 25a is provided in the same radial direction as the eccentric portion to which the roller 10 of the rotating shaft 2 is attached.

Since the mass of the rotor 23 is increased at a portion on the opposite side of the gas guide hole 25a in the radial direction, it is substantially the same as having a balance weight with respect to the eccentric portion of the rotating shaft 2.

That is, there is no need to separately provide a balance weight (part) in the rotor 23, and the rotor 23 itself has the effect of canceling the eccentric mass of the roller 10 together with the first balance weight 20 located in the concave portion 10a at the lower end of the roller 10. Have.

Next, an assembling process of the compressor configured as described above will be described. As shown in FIG. 8, the rotor 23 and the rotating shaft 2 are integrated beforehand by means such as shrink fitting. After the gap gauge 40 is attached to the lower portion of the rotor 23 and inserted into the inner diameter of the stator 24 supported by the jig 41, the compression mechanism 3 is inserted into the opposite end of the stator 24. The thickness of the gap gauge 40 is substantially equal to a gap between the outer diameter of the rotor 23 and the inner diameter of the stator 24, that is, a so-called air gap.

The inner diameter of the closed case 1 is made slightly smaller in diameter than the outer diameter of the stator 24. At this time, at least the periphery is heated and the diameter is enlarged. Then, the sealed case 1 is fitted to the outer diameter of the stator 24, and so-called shrink fitting is performed.

When left for a predetermined time, the temperature of the sealed case 1 decreases, and the stator 24 is fixed to the sealed case 1. In this state, the auxiliary bearing 9 described above is used for the closed case 1.
Since it is in contact with the end face, laser welding is performed on this contact portion.

Next, the integrated assembly is removed from the jig 41 and the gap gauge 40 is extracted. After that, the pipe is inserted into and joined to the sealed case 1 and the upper case of the sealed case is attached, and the assembling operation is completed.

After the shrink-fitting of the stator 24 in the sealed case 1 is completed, the sealed case 1 is left at room temperature to be cooled, and the inner diameter of the stator 24 is reduced by the tightening force of the sealed case 1. In particular, since both ends of the stator 24 have low rigidity, the shrinkage thereof is large, and it is known that when the inner diameter of the sealed case 1 is 100 mm, the inner diameter of the stator is reduced by about 0.05 to 0.15 mm.

Due to this characteristic, the compression mechanism 3 is fixed to the inner diameter of the stator 24, that is, a so-called stop fit,
The compression mechanism 3 and the stator 4 can be easily fixed without using any means such as welding that may cause the influence of thermal deformation.

At this time, since the gap gauge 40 is inserted into the air gap of the motor section 4 on the opposite side of the rotor 23, the outer diameter of the rotor 23 and the inner diameter of the stator 24 remain aligned.

The compression mechanism 3 is fixed on the closed case 1 side at a bottom which is separated from the shrink-fitting portion and hardly receives a change in the case inner diameter due to shrink-fitting, and is fixed after the shrinkage is completed. Therefore, it is hardly affected by the change due to the case accuracy and shrink fitting.

As shown in FIG. 9, a thick end plate 42 having a central portion opening may be attached to the lower end surface of the stator 24, and the cylinder 5 may be inserted into the opening of the end plate 42. In this case, if the inner diameter accuracy of the end plate 42 is increased, the concentricity of the stator 24 and the rotor 23 after assembly can be more accurately secured, and the rigidity of the end plate 42 can be increased. The supporting force for the compression mechanism 3 is further strengthened.

[0114] As shown in FIG.
D or the main bearing 8C need not be inserted into the inner diameter of the stator 24. At least the coil end 2 of the stator 24
The end of the cylinder 5D may be inserted into 4a.

By providing a concave portion at the lower end of the rotor 23 and providing a boss 8g integrally projecting from the flange portion 8a of the main bearing 8C, the pivotal support length of the main bearing 8C with respect to the rotary shaft 2 is provided. Can be extended.

[0116]

As described above, according to the present invention, the ends of the electric motor section and the compression mechanism section are wrapped with each other to reduce the overall length, and thus the size can be reduced. This simplifies and improves the assemblability, and at the same time contributes to the improvement of reliability and productivity.

[Brief description of the drawings]

FIG. 1 is a sectional view of a helical blade type compressor showing an embodiment of the present invention.

FIG. 2 is a partial cross-sectional view of a compression mechanism according to another embodiment.

FIG. 3 is a partial cross-sectional view of a compression mechanism, showing still another embodiment.

FIG. 4 is a cross-sectional view of a helical blade compressor showing still another embodiment.

FIG. 5 is a partial cross-sectional view of a compression mechanism, showing still another embodiment.

FIG. 6 is a cross-sectional view of a compression mechanism showing still another embodiment.

FIG. 7 is a cross-sectional view of a helical blade type compressor, showing still another embodiment.

FIG. 8 is a view for explaining a compressor assembling step of the embodiment.

FIG. 9 is a partial cross-sectional view of a compression mechanism, showing still another embodiment.

FIG. 10 is a partial cross-sectional view of a compression mechanism, showing still another embodiment.

[Explanation of symbols]

 5 ... Cylinder, 10 ... Rotating body (roller), 12 ... Blade, 3 ... Compression mechanism part, 2 ... Rotating shaft, 23 ... Rotor, 24 ... Stator, 4 ... Electric motor part, 8 ... Main bearing, 24a ... ) Coil end portion, 7: insulating film, 9: auxiliary bearing, 20: first balance weight, 30: non-magnetic ring, 8a: guide portion, 8c: mounting portion.

Claims (15)

[Claims] 1. A helical blade type compression mechanism comprising a cylinder, a rotating body disposed in the cylinder, a helical blade interposed between the rotating body and the cylinder, A fluid compressor comprising a motor unit including a rotor and a stator, which is connected to a mechanism unit via a rotating shaft and rotationally drives a rotating body of the compression mechanism unit, wherein one end of the compression mechanism unit is the motor unit A fluid compressor, wherein the fluid compressor is supported by being inserted into an inner diameter portion of the stator. 2. An apparatus according to claim 1, wherein one end of said compression mechanism is inserted into and supported by the inner diameter of said stator.
A fluid compressor as described. 3. The compression mechanism includes a main bearing that pivotally supports the rotating shaft. The outer diameter of the main bearing is the same as the inner diameter of the cylinder, and the main bearing is disposed in the cylinder. 3. The fluid compressor according to claim 2, wherein one end of the cylinder on the bearing side is inserted into and supported by the inner diameter of the stator. 4. The fluid compressor according to claim 2, wherein insulating means is interposed between the compression mechanism and a coil end of the stator. 5. The fluid compressor according to claim 4, wherein said insulating means is an insulating film attached to an outer peripheral surface of a cylinder. 6. The rotor constituting the electric motor section is provided so as to be axially displaced from the stator in the direction opposite to the compression mechanism section, and one end of the compression mechanism section is inserted into the displaced portion. The fluid compressor according to claim 2, wherein: 7. The rotary shaft is pivotally supported by a sub bearing together with the main bearing, the rotary shaft is protruded from the sub bearing and pivotally supported, and a balance weight is provided at a protruding portion of the rotary shaft. The fluid compressor according to claim 1 or 2, wherein 8. The fluid compressor according to claim 2, wherein a portion of the compression mechanism portion supported on the peripheral surface of the inner diameter portion of the stator is made of a non-magnetic material. 9. The fluid compressor according to claim 2, wherein a portion of said compression mechanism portion supported on a peripheral surface of the inner diameter portion of the stator is made of a non-conductive material. 10. The compression mechanism comprises a main bearing for pivotally supporting the rotary shaft. The main bearing is supported by a flange inserted into the cylinder and a peripheral surface of a stator inner diameter protruding from the cylinder. 3. The fluid compressor according to claim 2, further comprising a mounting portion. 11. The fluid compressor according to claim 10, wherein an end plate is provided on a flange portion of the main bearing, and the end plate is supported on a peripheral surface of an inner diameter portion of the stator. 12. The fluid compression as claimed in claim 2, wherein said stator has a stepped notch in its inner peripheral portion, and one end of said compression mechanism portion is supported in said stepped portion. Machine. 13. The rotor constituting the electric motor section, the end rings provided at both ends thereof are formed asymmetrically with each other, and the thickness of the end ring on the compression mechanism section side is opposite to the end ring on the anti-compression mechanism section side. The fluid compressor according to claim 1, wherein the fluid compressor is formed to have a thickness smaller than a thickness of the ring. 14. The fluid compressor according to claim 2, wherein a semi-hermetic cover having gas holes is provided at an end of the stator on the side opposite to the compression mechanism. 15. The compression mechanism section and the electric motor section are housed in a closed case, and the other end of the compression mechanism section is supported by a closed case bottom surface. Item 11. The fluid compressor according to Item 10.