JP3377800B2 - Fluid compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a helical blade type fluid compressor suitable for compressing refrigerant gas in a refrigeration cycle, for example.

[0002]

2. Description of the Related Art Conventionally, as a general compressor, a reciprocating type compressor, a rotary type compressor, and the like are known. In addition, a refrigerant flowing from a blow end side of a cylinder into a working chamber is discharged from a cylinder. There is provided a helical blade type fluid compressor in which the fluid is compressed while being sequentially transferred to the working chamber and discharged to the outside.

The outline of the helical blade type compressor is as follows.
For example, as shown in FIG. 28, the stator 101 and the rotor 1
Cylinder 105 rotated by drive means consisting of 03
And a rotating rod 109 which is arranged eccentrically by e in the cylinder 105 and is rotatable relative to the cylinder 105 via the Oldham ring 107.
A spiral groove 111 is formed on the outer peripheral surface of the rod 9 over substantially the entire length of the rod 109, and a spiral blade 113 is fitted in the groove 111 so as to be able to move in and out. The outer peripheral surface of the blade 113 is in close contact with the inner peripheral surface of the cylinder 105, and the blade 113 pivots integrally with the rotating rod 109. The rotating rod 109 with respect to the cylinder 105 eccentrically rotates. The volume of the working chamber 115 formed in the space between the rotary rod 109 and the cylinder 105 is determined by the pitch P of the spiral groove 111 into which the blade 113 is fitted as shown in FIG.
The pitch P of the groove 111 is gradually reduced from one end of the rotating rod 109 to the other end thereof. Therefore, the volume of the working chamber 111 formed by the blade 113 is gradually reduced from the suction end side of the rotating rod 109 on the suction pipe 117 side toward the discharge end side on the discharge pipe 119 side, so that the refrigerant is discharged. It is structured such that it is gradually compressed and discharged to the outside while being transported toward the end side.

[0004]

As described above, in the fluid compression of the helical blade system, the blade 113 for compressing the refrigerant gas has a flexible property because it is assembled in the spiral groove 111 so as to be able to move in and out. It has been considered to use a synthetic resin material having properties such as low resistance to bending, low heat resistance, and low coefficient of friction, in addition to having a low flexural modulus so as to be secured. Specifically, tetrafluoroethylene resin (hereinafter referred to as PTFE resin), tetrafluoroethylene
Perfluoroalkoxyethylene copolymer resin (hereinafter PFA
It is adopted as a resin).

Since injection molding is difficult with the former PTFE resin, for example, as shown in FIG. 30 and FIG. 31, a spiral blade 113 is formed by cutting from a cylindrical base material 121, and a pitch is formed. Different spiral groove 111
On the other hand, the blade 113 is stretched and fitted.

By the way, the blade 113 in operation is pushed from the side of the discharge side working chamber a having a high pressure toward the side of the suction side working chamber b having a low pressure due to the pressure difference as shown in FIG. To do. At the same time, the up and down movements are repeated. At this time, the force acting on the blade 113, F1,
In F2 and F3, the strongest force acts on F2, corner 1
There is a problem in that the side surface of the blade 113 is quickly worn by being strongly pressed against the blade 23.

For this reason, in order to prevent the blade 113 from collapsing, for example, the flexural modulus of elasticity is increased, or the wear resistance is improved by using a composite material to which a particulate filler is added. However, if the bending elastic modulus is increased, the blade 113 lacks flexibility, and as a result, the blade 113 is unreasonably assembled to the spiral groove 111. In particular, in the region of the groove 111 having a large pitch, strong twisting occurs from the place where the blade 113 is greatly stretched. The twist of the blade 113 acts as a contact pressure to the groove wall, which causes sliding resistance at the time of moving in and out, and lacks smooth operation. For this reason, the outer peripheral surface of the blade 113 is not properly brought into close contact with the inner peripheral surface 125 of the cylinder 105, and there is a risk that the sealing function will deteriorate and operating efficiency will deteriorate. Further, as shown in FIG. 32, in the blade 113 in which a particulate filler is added to improve wear resistance,
Although an excellent wear resistance effect is exerted on the inner peripheral wall surface of the cylinder 105, the side surface of the blade 113 is strongly rubbed by the corner 123, which causes a problem of rapid wear. That is, since the PTFE resin has a high melt viscosity, it has a high content of voids (pores) during compression molding and firing, and this void impairs the particle retention effect, so that the filler easily falls off due to the corner 123. , Blade 1
Regarding the side surface of No. 13, it was difficult to obtain a remarkable effect of abrasion resistance.

On the other hand, in the latter PFA resin, since the injection molding process along the spiral groove 111 is possible, the blade 113 is properly fitted into the spiral groove 111 without difficulty. be able to. On the other hand, the melt viscosity at 380 ° C. is 10 ⁴ to 10 ⁵ poises, which is low as compared with 10 ¹⁰ to 10 ¹¹ poises of the PTFE resin. Therefore, there is a problem that the fatigue characteristics are deteriorated, and in some cases, fatigue fracture is caused.

Therefore, the present invention provides a fluid compressor that solves the above problems.

[0010]

To achieve the above object, according to the present invention, a cylinder and an eccentric arrangement are provided along the axial direction of the cylinder, a part of which is the inner peripheral surface of the cylinder. And a spiral groove formed on the outer periphery of the rotary body, the spiral groove being formed on the outer circumference of the rotary body and gradually decreasing from the suction side to the discharge side of the cylinder. And a spiral shape that has an outer peripheral surface that fits freely in and out of the groove and that is in close contact with the inner surface of the cylinder, and that divides the space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotating body into a plurality of working chambers. In the fluid compressor, the blade comprises a tetrafluoroethylene / perfluoroalkoxyethylene copolymer resin composited with glass fiber or carbon fiber having a length of 50 to 300 microns. Made injection-molded body is constituted by a tensile elongation at break of 100% or more materials. A preferred embodiment of the blade is made of a tetrafluoroethylene resin compounding 5 to 20% by weight of glass fiber or 3 to 17% by weight of carbon fiber, and has a bending elastic modulus of 8000 to 18000 Kg / cm ^2.
It is composed of a material having. Alternatively, 5 to 20% by weight of glass fiber or carbon fiber in tetrafluoroethylene / perfluoroalkoxyethylene copolymer resin in which injection molding is impossible, in which tetrafluoroethylene resin is partially copolymerized with perfluoroalkyl group It is composed of a material having a bending elastic modulus of 8000 to 18000 Kg / cm ² in combination with 3 to 17% by weight .

[0011]

According to such a fluid compressor, when the blade tilts and is repeatedly moved in and out due to the pressing force due to the pressure difference during operation, the side surfaces of the blade come into strong contact with the corners. It is not easily scraped off by fibers or carbon fibers, and wear resistance is secured. Also, fatigue failure does not occur.

[0012] On the other hand, the blade can be installed in the spiral groove without difficulty, and a smooth blade movement can be obtained. As a result, the sealing property can be improved and high operation efficiency can be obtained.

[0013]

Embodiments of the present invention will be described in detail below with reference to the drawings of FIGS. In FIG. 1, 1
Shows a closed case of a closed type fluid compressor 3 used in a refrigeration cycle. One side of the closed case 1 is provided with a suction pipe 5 of the refrigeration cycle and the other side is provided with a discharge pipe 7. An electric element 9 as a driving means and a compression element 11 as a compression means are arranged in the closed case 1.

The electric element 9 has a stator 13 fixed to the inner surface of the closed case 1 and a rotatable rotor 15 provided inside thereof.

The compression element 11 has a cylinder 17 whose both ends are open, and the cylinder 17 is rotatably supported at both ends by bearings 19 and 20 fixed to the inner surface of the closed case 1. The bearings 19 and 20 include boss portions 19a and 20a in which the ends of the cylinder 17 are rotatably fitted, and base portions 19b and 20b having a diameter larger than those of the boss portions 19a and 20a and fixed to the inner surface of the sealed case 1. The cylinder 17 is airtightly closed at both ends.

Inside the cylinder 17, a cylindrical rotating body 21 having a diameter smaller than the inner diameter of the cylinder 17 is arranged along the axial direction of the cylinder 17. The rotating body 21 is made of iron or another material, and its central axis A is eccentrically arranged downward in FIG. 1 by a distance e with respect to the central axis B of the cylinder 17, and a part of the rotating body 21 makes line contact with the inner peripheral surface. is doing.

Spindle portions 21a and 21b having a small diameter are provided at both ends of the rotary body 21, respectively.
a and 21b are boss portions 19 of the bearings 19 and 20, respectively.
It is rotatably inserted and supported in bearing holes 19c and 20c formed in a and 20a.

On one of the support shaft portions 21a of the rotating body 21, there is formed a square column portion 25 having a square cross section which functions as a power transmission surface for transmitting the rotary power from the cylinder 17 side via the Oldham ring 23. . The prismatic portion 25 fits with the rectangular elongated hole 26 formed in the Oldham ring 23 with play, and the prismatic portion 25 is slidable within the play range. On the outer peripheral surface of the Oldham ring 23, one end portions of a pair of transmission pins 27, 27 are slidably fitted in the radial direction orthogonal to the longitudinal direction of the elongated hole 26. The end is a fitting hole 2 formed in the peripheral wall of the cylinder 17.
It is fitted and fixed to 9. Thereby, the rotating body 21
Is securely attached at a position eccentric to the cylinder 17, and the rotational force of the cylinder 17 is transmitted to the rotating body 21 via the Oldham ring 23.

Therefore, when the electric element 9 is actuated, the cylinder 17 rotates integrally with the rotor 15, so that the rotary body 21 is eccentrically rotated with respect to the cylinder 17 via the Oldham ring 23.

On the other hand, a spiral groove 31 is provided on the outer peripheral surface of the rotating body 21, and the spiral groove 31 has the largest pitch P on the suction end side (right side in FIG. 1). , The pitch is set to decrease gradually toward the discharge end side (left side in the drawing).

A spiral blade 33 is fitted in the spiral groove 31 so as to be able to move in and out by utilizing elastic force. As a result, each working chamber 35 is formed and the working chamber 35 on the suction end side has the largest volume.
Hereinafter, the volumes of the respective working chambers 35 are set to gradually decrease toward the discharge end side, and the final working chamber 35 on the discharge side is set.
Is connected and communicates with the discharge hole 37 opened in the closed case 1 formed in the bearing 20. Further, each working chamber 35 is a substantially crescent-shaped region extending from the contact portion between the rotor 21 and the inner peripheral surface 17a of the cylinder 17 along the blade 33 to the next contact portion as shown in FIG. The first working chamber 35 on the suction end side is provided with a first suction hole 39 for communication provided in the shaft end of the rotating body 21 and a second suction hole 41 provided in the bearing 19. Is connected to the suction pipe 5 of the refrigeration cycle. This allows the suction pipe 5
The refrigerant sucked into the cylinder 17 from is reliably introduced into the first working chamber 35 without interruption.

The blade 33 is formed by cutting or injection molding. That is, the blade 33 of the first embodiment is made of an injection molded body of tetrafluoroethylene / perfluoroalkoxyethylene co-heavy resin (hereinafter referred to as PFA resin) in which glass fibers or carbon fibers are compounded, and is stretched. It is made of a material having a breaking elongation of 100% or more.

FIG. 4 shows concrete experimental results of various blades 33. In the figure, PI resin means an average particle size of 3
It is a 0 micron polyimide resin (hereinafter the same). In addition, MI is a scale indicating the fluidity of a thermoplastic resin when melted (ASTM standard, D-3307 and below).
The larger the value, the higher the fluidity, which is a measure of the molecular weight that affects the fatigue properties.

5 to 10 are characteristic diagrams for demonstrating the experimental results of FIG. In this experiment, "Freon 12" was used as the refrigerant gas, and "3,000" was used.
r. p. The rotation speed is "m" and the measurement time is 500 hours.

Here, FIG. 5 shows the results of the relative index of the refrigerating capacity where the initial performance is 100% in Example 1 and Comparative Example 1 in comparison, and in FIG. 6, Example 2 and Comparative Example 2 are shown. The results of the relative index of the refrigerating capacity are shown in comparison with the initial performance of 100% as 100%. Further, FIG. 7 shows the initial performance of Comparative Example 3 as 1
The relative index of the refrigerating capacity at 00% is shown, and FIG. 10 shows an example of the fatigue fracture state after the end of the test for Comparative Examples 1 and 2 and Comparative Example 3. FIG. 8 shows the relationship between the tensile elongation at break and the time when the refrigerating capacity is reduced to 60%, and FIG. 9 shows the wear amount of the blades 33 of Examples 1 and 2 and Comparative Example 3 which did not lead to fatigue failure. Are shown in contrast.

That is, as shown in FIG. 5, in Comparative Example 1, a sharp decrease in the refrigerating capacity was observed, and the refrigerating capacity / relative index decreased to 50 to 55% after 500 hours. However, in Example 1, no decrease in the refrigerating capacity / relative index was observed, and the initial performance was maintained.

Further, referring to FIG. 6, Example 2 is Comparative Example 2
At the same time, the same data as the refrigerating capacity / relative index of Example 1 and Comparative Example 1 shown in FIG. 5 were obtained. However, referring to FIG. 7, Comparative Example 3 (filling with 10% by weight of PI resin)
In this case, the refrigerating capacity / relative index gradually decreases, whereas in Comparative Example 3 (filling 15% by weight of PI resin), the rapid refrigerating capacity is the same as in Comparative Examples 1 and 2. -A decrease in the relative index was observed, and a gradual decrease was observed even after 400 hours.

When the test results after the end of 500 hours were examined, the breakage shown in FIG. 10 was observed in Comparative Examples 1 and 2 and Comparative Example 3. The fractured portion 42 is the portion where the pitch of the spiral is the largest and the region where the elastic deformation amount is also the largest is determined to be the fracture due to fatigue. That is, FIG.
It can be seen that the sharp decrease in the refrigerating capacity / relative index in FIG. 7 is due to the destruction of the blade 33. Figure 8
As shown in (4), the smaller the tensile fracture elongation, the lower the refrigerating capacity in a shorter time and the fatigue fracture occurs, and therefore it is desirable that the tensile fracture elongation is at least 100% or more. In addition, since the smaller the melt flow index of PFA resin, the more advantageous the effect on fatigue, it is about 20-40g / 10mi.
A range of n is preferred.

As for the amount of wear, as shown in FIG. 9, it can be seen that the amount of wear of Comparative Example 3 is as large as 0.95 mm, while that of Examples 1 and 2 is 0.02 to 0.05 mm. As a result, the refrigerating capacity / relative index shown in FIG. 7 decreases with time, indicating that the progress of the wear of the blade 33 causes the sealing property of the refrigerant gas to become poor. In addition, Comparative Examples 1 and 2 are stable at 50 to 55%, though there is a rapid decrease in the refrigerating capacity and the relative index due to the fatigue fracture of the blade 33, but Comparative Example 3 is gradually post fatigue fracture. A decline is seen. This indicates that the corners cause the particulate filler to fall off due to the corners, which increases wear. On the other hand, Examples 1-2 and Comparative Example 1
As can be seen from the data of ~ 2, even if the filled glass fiber and carbon fiber are rubbed against the corner of the suction side working chamber 35,
It can be seen that it has the effect of suppressing the dropout, and can maximize the reinforcing effect.

The tensile elongation at break depends on the lengths of the glass fiber and carbon fiber, and the one having a length of 50 to 300 μm, which is called “milled fiber”, is preferable. It is also possible to use a solid lubricant together for improving the sliding characteristics. As the solid lubricant, there are molybdenum disulfide, graphite, molybdenum, bronze powder and the like, and the compounding amount thereof is preferably 2 to 10% by weight. However, it is necessary to be 100% or more because there is a decrease in tensile elongation at break.

Next, the blade 33 of the second embodiment is made of a tetrafluoroethylene resin compounding glass fiber or carbon fiber, and has a flexural modulus of 8000 to 18000.
It is composed of a material having kg / cm.

FIG. 11 shows concrete experimental results of various blades 33, and characteristic diagrams demonstrating the experimental results of FIG. 11 are shown in FIGS. 12 to 17. In this experiment,
"Freon 12" is used as the refrigerant gas, and "3,000" is used.
r. p. The rotation speed is "m" and the measurement time is 500 hours.

Here, FIG. 12 shows the results of relative operating efficiency of Example 1 and Comparative Example 1 in comparison, and FIG. 13 shows Example 2
And the results of the relative operation efficiency of Comparative Example 2 are shown in contrast. Further, FIG. 14 shows the result of the relative operating efficiency of Comparative Example 3, and FIG. 15 shows the wear amounts of the blades 33 of Examples 1 and 2 and Comparative Examples 1 to 3 in comparison. 16 and 17
Shows the measurement results of the wear amount and the dynamic friction coefficient using the thrust color type testers of Examples 1 and 2 and Comparative Examples 1 to 3 in comparison with each other.

That is, looking at the characteristics obtained from the blade 33 constructed in Comparative Example 1 from FIG. 12, the relative operating efficiency decreased to 80% or less after 500 hours. However, Example 1
Looking at the characteristics obtained with the blade 33 composed of
It can be seen that the relative operating efficiency decreased by 1 to 2% at 5 and 20% by weight, but the operating efficiency did not decrease at 15% by weight, and the initial characteristics at 1 hour were maintained.

Further, as shown in FIG. 13, the blade 33 constructed in Comparative Example 2 had a relative operating efficiency lowered to 80% or less after 500 hours as in Comparative Example 1, but the blade constructed in Example 2 was used. No. 33, as in Example 1, showed almost no decrease in relative operating efficiency.

As can be seen from FIG. 14, Comparative Example 3 has an operating efficiency of 500 hours for all. It decreased to less than half of the operating efficiency for one hour.

On the other hand, looking at the amount of wear of each blade 33 of Examples 1-2 and Comparative Examples 1-3, as shown in FIG. 15, Examples 1-2 show a wear amount of 15-30 microns. On the other hand, in Comparative Examples 1 and 2, wear of 50 to 80 microns was observed. Further, it can be seen that Comparative Example 3 has a significantly large wear of 140 to 150 microns. That is, the decrease in operating efficiency of Comparative Examples 1 to 3 shown in FIGS.
It can be seen that the blades 33 shown in FIG. 15 are worn. It is judged that the worn blade 33 impairs the sealing property of the refrigerant gas, and as a result, the refrigerating capacity is reduced and the operating efficiency is reduced.

Next, looking at the amount of wear by the thrust color type tester shown in FIG. 16, the glass fiber 3 of Comparative Example 1 was examined.
Although the amount of wear is large in the case of the filling amount of 2% by weight of carbon fiber of Comparative Example 2 and the filling amount of 2% by weight of Comparative Example 2 being large, 23% by weight of glass fiber of Comparative Example 1 and 20% by weight of carbon fiber of Comparative Example 2 As for the large amount, the data which is almost the same as the wear of Examples 1 and 2 was obtained. It is understood that the wear of the blade 33 is caused by the sliding peculiar to the helical blade type compressor.

Further, as can be seen from FIG. 11, it is shown that there is a close relationship between the bending elastic modulus and the relative operating efficiency of the compressor in one hour. The higher the bending elastic modulus, the larger the load power relative index, and the result. As a result, the relative operating efficiency also decreases. That is, when the blade 33 elastically deforms and moves in and out of the spiral groove 31, the bending elastic modulus of the blade 33 increases, resulting in a large loss. As can be seen from the kinetic friction coefficient of FIG. 17, the glass fiber of Comparative Examples 1 and 2 is small in a small filling amount of carbon fiber, but the filling amount of Examples 1 and 2 and Comparative Examples 1 and 2 is large. There is no difference between them, and in Comparative Example 3, there is almost no effect of the filling amount. This means that the difference in operating efficiency due to the difference in the filling amount is due to the bending elastic modulus.

In this case, 23% by weight of glass fiber and 20% by weight of carbon fiber of Comparative Example 1 had a flexural modulus of 19000 kg.
It can be seen that the wear increases when the value is / cm ² . Also,
3% by weight of the glass fiber of Comparative Example 1 and 2% by weight of the carbon fiber of Comparative Example 2 both have a small reinforcing effect on the filler and a small bending elastic modulus of 7,000, so that the pressure difference in the working chamber 35 causes the collapse. It is judged that the wear is likely to occur due to the easy occurrence.

However, in the case of "tetrafluoroethylene resin + PI resin 5,15,25% by weight" of Comparative Example 3, the abrasion of the blade 33 was extremely large irrespective of the bending elastic modulus. Also,
It was found that the wear amount obtained as shown in FIG. 16 was smaller than that in Example 1 depending on the filling rate. PI resin is
Since it has a particle shape and the PI resin easily falls off due to a child rubbing against the corner of the suction side working chamber 35, the reinforcing effect is lost.
It shows increased wear. That is, Example 1
2 and the glass fibers and carbon fibers filled in Comparative Examples 1 and 2,
It can be understood that even if it is rubbed against the corner of the suction side working chamber 35, it has the effect of suppressing the falling off, and can maximize the reinforcing effect.

The tetrafluoroethylene resin, which is a composite of glass fiber and carbon fiber, may be used in combination with a solid lubricant for further improving the sliding characteristics. As this solid lubricant,
Molybdenum disulfide, graphite, molybdenum, bronze powder and the like are suitable, and the compounding amount thereof is preferably 2 to 10% by weight. However, the flexural modulus is 8000-
It should be in the range of 18,000 kg / cm ² .

Next, in the blade 33 of the third embodiment, a tetrafluoroethylene perfluoropolymer in which injection molding is impossible is obtained by partially copolymerizing a tetrafluoroethylene resin with a perfluoroalkyl group. Alkoxyethylene copolymer resin compounded with glass fiber or carbon fiber, and flexural modulus of 800
It is composed of a material having a weight of 0 to 18,000 kg / cm ² .

FIG. 18 shows the concrete experimental results of various blades 33, and FIGS. 19 to 27 are characteristic diagrams demonstrating the experimental results of FIG. In this experiment,
Use "Freon 12" as the refrigerant gas and select "3,000".
r. p. m "rotation speed is given. Then, the load power and the refrigerating capacity at that time were measured to obtain the operation efficiency (refrigerating capacity / load power). The measurement time was 1000 hours, and the performance at 1 hour was also measured in order to compare changes in compressor performance. The amount of wear of the blade 33 after 1000 hours was also measured. Further, under the same conditions, the compressor performance and the wear amount of the blade 33 when different blades were applied were measured.

Here, FIG. 19 shows the results of the relative operating efficiency of Example 1 and Comparative Example 1 and Comparative Example 3 in comparison, and FIG.
0 indicates the results of relative operation efficiency of Example 2 and Comparative Example 2 and Comparative Example 4 in comparison. Further, FIG. 21 shows Comparative Example 5.
And the results of the relative operating efficiency of Comparative Example 6 are shown.

FIG. 22 shows the amounts of wear of the blades 21 of Example 1 and Comparative Examples 1 and 3 in comparison, and FIG.
The wear amounts of the blades 21 of Example 2, Comparative Example 2 and Comparative Example 4 are compared with each other. In FIG. 24, the wear amounts of the blades of Comparative Example 5 and Comparative Example 6 are compared.

FIG. 25 shows Example 1, Example 2 and Comparative Example 2.
26 and 27 of Comparative Example 5 and Comparative Example 5, the measurement results of the wear amount and the dynamic friction coefficient using the thrust color type testers of Comparative Example 2, Comparative Example 3 and Comparative Example 6 are shown in comparison. There is.

That is, looking at the characteristics obtained with the blade 33 constructed in Comparative Example 1 from FIG. 19, the relative operating efficiency dropped to 80% or less after 1000 hours. However, looking at the characteristics obtained with the blade 33 constructed in Example 1,
It can be seen that the relative operating efficiency decreased by 1 to 2% at 5 and 20% by weight, but the operating efficiency did not decrease at 15% by weight, and the initial characteristics at 1 hour were maintained.

Further, as shown in FIG. 20, the relative operating efficiency of the blade 33 constructed in Comparative Example 2 was reduced to 80% or less after 1000 hours as in Comparative Example 1, but the blade constructed in Example 2 was used. No. 33, as in Example 1, showed almost no decrease in relative operating efficiency.

In this case, in Comparative Example 6, as can be seen from FIG. 21, the operating efficiency for 1000 hours was reduced to less than half the operating efficiency for 1 hour.

On the other hand, looking at the amount of wear of each blade 21 of Examples 1 and 2 and Comparative Examples 1 to 6, as shown in FIGS. 22 and 23, Examples 1 and 2 have wear of 15 to 30 microns. In contrast to the amount, Comparative Examples 1 and 2 show wear of 50 to 70 microns. Further, in Comparative Examples 3 to 4, the wear amount is 40 to 60 μm, which is larger than that in Examples 1 and 2.
However, in Comparative Example 5, the wear was remarkably large at 80 to 90 μm, and in Comparative Example 6, it was even larger and 100 to 120 μm.
It was micron. That is, the decrease in operating efficiency of Comparative Examples 1 to 6 shown in FIGS.
It can be seen that the blades 33 are worn as shown in FIG.
The blades 33 of Comparative Examples 1 to 6 show no change in the relative index of load power after 1000 hours, but the fact that the relative index of refrigerating capacity is reduced means that the blade 33 is worn as shown in FIGS. 22 to 24. As a result, it is considered that the sealability of the refrigerant gas was impaired, the refrigerating capacity was lowered as a result, and the operating efficiency was lowered.

Next, looking at the amount of wear by the thrust color type tester shown in FIG. 25, the glass fiber 3 of Comparative Example 1 was examined.
The amount of the carbon fiber 2 of the comparative example 2 and the amount of the carbon fiber 2 of the comparative example 2 are small, the wear amount is large.
In the case of the one having a large filling amount of 0% by weight, Examples 1-2
The result was almost the same as that of the wear. Further, the wear amount of Comparative Example 5 is between that of Example 1 and Example 2,
In particular, no bad result was obtained with respect to wear characteristics. Further, looking at the wear amount shown in FIG. 26, Comparative Examples 2 to 3,
A similar tendency is observed in Comparative Example 6, and it can be seen that the result does not match the result of the wear amount of the blade 33 shown in FIG. It can be seen that the wear amount in FIG. 22 is caused by sliding peculiar to the helical blade compressor.

On the other hand, when comparing the wear amounts of the tetrafluoroethylene resin and 70-J, as shown in FIG.
2 was 10 to 30 μm, but Comparative Example 3 shown in FIG.
Nos. 4 to 30 have a slightly large wear of 30 to 50 μm, which is in agreement with the results of the wear amount shown in FIG.

That is, it shows that when the blade 33 moves in and out of the groove 31 while elastically changing, the bending elastic modulus of the blade 33 increases and the loss increases. As a proof of this, as can be seen by looking at the dynamic friction coefficient shown in FIG. 27, the glass fibers of Comparative Examples 1 and 2 are small in the small filling amount of carbon fibers, but Examples 1-2
It is also proved by the fact that there is no difference between the large filling amount of Comparative Examples 1 and 2 and the comparative example. Further, in Comparative Example 5, there is almost no effect of the filling amount. That is, it can be seen that the difference in operation efficiency due to the difference in the filling amount is the influence of the bending elastic modulus.

However, "70-J + PI resin 5, 15, 25% by weight" in Comparative Example 5 and "70-J + PI resin in Comparative Example 6"
Resin 5, 15, 20% by weight ”showed significant wear of the blade 21 regardless of the flexural modulus. This is PI
It is shown that the resin is in the form of particles, and the PI resin is easily dropped by rubbing against the corner of the suction side working chamber 35, and the reinforcing effect is lost, so that the wear is increased. That is, it can be seen that the glass fibers and carbon fibers filled in Examples 1 and 2 and Comparative Examples 1 and 2 have the effect of suppressing the falling even if they are rubbed against the corners of the suction side working chamber 35.

22 to 24, Example 1 and Comparative Example 3 different in base resin, Example 2 and Comparative Example 4
Looking at the amount of wear of the blade 21 of Example 1,
The wear of 35 to 50 microns is confirmed in Comparative Examples 3 to 4 with respect to -30 microns. 70-J of Examples 1 to 2 has a lower void content than the tetrafluoroethylene resins of Comparative Examples 3 to 4 and is a dense molding material, so that it has the effect of further suppressing the loss of glass fibers and carbon fibers, and is reinforced. It turns out that the effect is maximized.

The tetrafluoroethylene / perfluoroalkoxyethylene copolymer resin, which is a composite of glass fiber and carbon fiber, may be used in combination with a solid lubricant for further improving the sliding characteristics. Suitable as the solid lubricant are molybdenum disulfide, graphite, molybdenum, bronze powder and the like, and the compounding amount thereof is preferably 2 to 10% by weight.
However, the flexural modulus is 8000 to 18000 kg /
Must be in the cm ² range.

In FIG. 1, reference numeral 55 denotes an oil introducing passage provided in the rotating body 21, one end of the oil introducing passage 55 communicates with the spiral groove 31, and the other end thereof is on the suction end side. Through a communication hole 57 formed in the bearing 19 of the above-mentioned bearing 19 is connected and communicated with the introduction pipe 59 whose suction port 59a faces the bottom of the closed case 1. Therefore, when the pressure in the closed case 1 rises, the lubricating oil stored in the bottom of the closed case 1 is sent into the groove 31 through the introduction pipe 59, the communication hole 57 and the oil introduction path 55, so that the blade 31 Lubrication at the time of entry and exit of 33 is ensured.

Next, the operation of the fluid compressor thus constructed will be described.

First, when the electric element 9 is energized, the rotor 15
Rotates, and the cylinder 17 also rotates integrally with the rotor 15. If the cylinder 17 rotates, the Oldham ring 23
The rotating body 21 also rotates via the. The rotating body 21 with respect to the cylinder 17 is eccentrically rotated. As a result, the fluid such as the refrigerant sent into the working chamber 35 on the suction end side is compressed while being sequentially sent toward the working chamber 35 on the discharge end side, and discharged from the discharge pipe 7.

During this operation, when the blade 33 is repeatedly moved in and out due to the pressing force due to the pressure difference, the side surfaces of the blade 33 come into strong contact with the corners. It will not be easily shaved off by the carbon fiber, and the wear resistance will be secured.

Furthermore, the spiral groove 31 can be assembled smoothly and the blade 33 can be smoothly moved in and out. As a result, the sealing property can be improved and high operation efficiency can be obtained.

[0063]

As described above, according to the fluid compressor of the present invention, in addition to the conventional characteristics such as cooling resistance, heat resistance and small coefficient of friction of the blade, the sealing property and durability are improved. Therefore, it becomes possible to achieve high operating efficiency.

[Brief description of drawings]

FIG. 1 is a sectional view of a fluid compressor according to the present invention.

FIG. 2 is a perspective view in which a blade is attached to a rotating body.

FIG. 3 is a sectional view of an Oldham ring.

FIG. 4 is an explanatory diagram of the first embodiment according to the present invention, showing the respective filling amounts of glass fiber and carbon fiber and the tensile elongation at break.

5 is a refrigerating capacity of Example 1 and Comparative Example 1 shown in FIG.
It is a characteristic view of a relative index.

6 is a refrigeration capacity of Example 2 and Comparative Example 2 shown in FIG.
It is a characteristic view of a relative index.

FIG. 7 is a characteristic diagram of a refrigerating capacity and a relative index of Comparative Example 3 shown in FIG.

FIG. 8 is a characteristic diagram of tensile breaking elongation of each example and each comparative example shown in FIG.

9 is a characteristic diagram of the wear amount of each of the examples and the comparative examples shown in FIG.

FIG. 10 is a perspective view showing a fatigue fracture portion of a blade.

FIG. 11 is an explanatory diagram of a second embodiment according to the present invention, which shows the load power, the refrigerating capacity, and the relative operating efficiency at the filling amounts of glass fiber and carbon fiber and the bending elastic modulus.

FIG. 12 is a characteristic diagram of relative operating efficiency of Example 1 and Comparative Example 1 shown in FIG. 11.

13 is a characteristic diagram of relative operating efficiency of Example 2 and Comparative Example 2 shown in FIG.

14 is a characteristic diagram of relative operating efficiency of Comparative Example 3 shown in FIG.

15 is a characteristic diagram showing the amount of wear of Examples 1 and 2 and Comparative Example 3 shown in FIG.

16 is a characteristic diagram of the amount of wear performed by the thrust color type testers of Example 1, Example 2 and Comparative Example 3 shown in FIG.

FIG. 17 is a characteristic diagram of a dynamic friction coefficient performed by the thrust color type tester of Example 1, Example 2 and Comparative example 3 shown in FIG. 11.

FIG. 18 is an explanatory diagram of a third embodiment according to the present invention, which shows the load power, the refrigerating capacity, and the relative operation efficiency in the filling amount and bending elastic modulus of glass fiber and carbon fiber.

19 is a characteristic diagram of relative operating efficiency of Example 1 and Comparative Example 3 shown in FIG.

20 is a characteristic diagram of relative operating efficiency of Example 2 and Comparative Example 4 shown in FIG.

FIG. 21 is a characteristic diagram of relative operating efficiency of Comparative Example 5 and Comparative Example 6 shown in FIG. 18.

22 is a characteristic diagram of the amount of wear of Example 1 and Comparative Example 3 shown in FIG.

23 is a characteristic diagram of the amount of wear of Example 2 and Comparative Example 4 shown in FIG.

FIG. 24 is a characteristic diagram of the amount of wear of Comparative Example 5 and Comparative Example 6 shown in FIG. 18.

FIG. 25 is a characteristic diagram of the amount of wear performed by the thrust color type testers of Example 1, Example 2 and Comparative example 5 shown in FIG. 18.

FIG. 26 is a characteristic diagram of the amount of wear performed by the thrust color type testers of Comparative Example 3, Comparative Example 4 and Comparative Example 6 shown in FIG. 18.

FIG. 27 is a characteristic diagram of the amount of wear performed by the thrust color type testers of Example 1, Example 2 and Comparative Example 5 shown in FIG. 18.

28 is a sectional view similar to FIG. 1 showing a conventional example.

FIG. 29 is a perspective view similar to FIG. 2 showing a conventional example.

FIG. 30 is a perspective view of a cylindrical base material of a blade.

FIG. 31 is a side view of a blade machined from a cylindrical base material.

FIG. 32 is an explanatory diagram of the operation of the blade.

FIG. 33 is an explanatory diagram of the operation of the blade.

[Explanation of symbols]

9 Drive means 17 cylinders 21 rotating body 31 spiral groove 33 spiral blade 35 working chamber

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Noriko Watanabe               8 Shinsugita-cho, Isogo-ku, Yokohama-shi, Kanagawa               Toshiba Corporation Living Space System Technology Research               In-house                (56) References JP-A-3-88993 (JP, A)                 JP-A-3-88992 (JP, A)                 JP 62-174262 (JP, A)

Claims (3)

(57) [Claims] 1. A cylinder, a rotary body which is eccentrically arranged along the axial direction of the cylinder, and is rotatable relative to the cylinder while a part of the cylinder is in contact with the inner peripheral surface of the cylinder, and It is provided on the outer circumference of the rotating body
A helical groove formed in gradually becomes smaller pitch toward the suction write side to the discharge side, the inner peripheral surface of the cylinder has an outer peripheral surface in close contact with the inner surface of the cylinder with fitted freely enter and exit the groove In a fluid compressor including a spiral blade that divides a space between the outer peripheral surface of the rotating body and a plurality of working chambers, the blade has a length of 50 to 50.
A fluid compressor comprising an injection-molded product of tetrafluoroethylene / perfluoroalkoxyethylene copolymer resin compounded with 300 micron glass fiber or carbon fiber, and made of a material having a tensile breaking elongation of 100% or more. . 2. A cylinder, an eccentric arrangement arranged along the axial direction of the cylinder, and a rotating body rotatable relative to the cylinder while a part of the cylinder is in contact with an inner peripheral surface of the cylinder. A spiral groove provided on the outer circumference of the rotating body and formed at a pitch that gradually decreases from the suction side to the discharge side of the cylinder, and an outer peripheral surface that is fitted in the groove freely and is in close contact with the inner surface of the cylinder. And a spiral blade that divides the space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotating body into a plurality of working chambers, wherein the blade is made of glass fiber 5
It consists to 20% by weight or carbon fiber 3 to 17 wt% tetrafluoroethylene resin composite of a flexural modulus 8000
A fluid compressor comprising a material having 18000 Kg / cm ² . 3. A cylinder, an eccentric arrangement along the axial direction of the cylinder, and a rotating body which is relatively rotatable with respect to the cylinder while a part of the cylinder is in contact with the inner peripheral surface of the cylinder. A spiral groove provided on the outer circumference of the rotating body and formed at a pitch that gradually decreases from the suction side to the discharge side of the cylinder, and an outer peripheral surface that is fitted in the groove freely and is in close contact with the inner surface of the cylinder. In a fluid compressor having a spiral blade that divides a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotating body into a plurality of working chambers, the blade is tetrafluoroethylene. 5-20% by weight of glass fiber or carbon fiber 3 in tetrafluoroethylene / perfluoroalkoxyethylene copolymer resin in which injection molding is impossible, which is obtained by partially copolymerizing resin with perfluoroalkyl group A fluid compressor characterized by being composed of a material having a bending elastic modulus of 8000 to 18000 Kg / cm ² in a combined amount of -17% by weight .