JP2005002901A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas compressor capable of achieving high efficiency and long period of durability by taking balance of thrust load applied to a rotor shaft. <P>SOLUTION: A circular ring part 35 is formed like a circular ring in an end part of the rotor shaft 10. Oil pressure P3 pressured by compression gas acts on an end face S3 of the circular ring part 35. On the other hand, oil pressure P2 whose pressure is reduced by passing through a bearing part 6a acts on an end face S2 opposing to the end face S3. High oil pressure P3 acts on the end face S3 of the circular ring part 35 so that force going toward a high pressure side acts on the rotor shaft 10. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gas compressor, for example, a gas compressor that compresses refrigerant gas in an air conditioner system of an automobile.
[0002]
[Prior art]
FIG. 8 is an axial sectional view of a conventional vane rotary type gas compressor 99. The gas compressor 99 is a device that sucks low-pressure gas and discharges high-pressure gas. For example, the gas compressor 99 is used to compress refrigerant gas in an air conditioner system of an automobile.
The gas compressor 99 is roughly divided into a driving force transmission unit 50 that obtains a rotational driving force from an automobile engine or the like, a suction port 16 that sucks the gas before compression, a rotor 9 that compresses the gas sucked by the rotational driving force, and is compressed. The discharge chamber 18 from which the high-pressure gas is discharged, and the discharge port 19 for sending the high-pressure gas in the discharge chamber 18 to the heat exchanger of the air conditioner.
[0003]
The rotor 9 includes a rotor shaft 10 and is rotatably supported by a bearing portion 6a formed on the discharge chamber 18 side and a bearing portion 5a formed on the driving force transmission portion 50 side.
An oil reservoir 30 is formed at the bottom of the discharge chamber 18, and oil in which the pressure in the discharge chamber 18 acts is stored.
[0004]
An oil passage 106 and an oil passage 105 are formed from the oil reservoir 30 to the bearing portion 6a and the bearing portion 5a, respectively, so that the oil pressurized in the discharge chamber 18 is supplied to the bearing portion 6a and the bearing portion 5a. It has become.
The oil supplied to the bearing portion 6a and the bearing portion 5a acts as lubricating oil, and also supplies hydraulic pressure for pressing the vane disposed in the rotor 9 so as to be able to protrude and retract against the inner wall of the cylinder.
[0005]
By the way, in the gas compressor configured as described above, the oil supplied to the bearing portion 6a is transmitted through the bearing portion 6a and reaches the end of the rotor shaft 10 on the discharge chamber 18 side. The pressure in the direction toward the driving force transmission unit 50 is generated.
In the gas compressor 99, in order to eliminate the thrust load imbalance generated in the rotor shaft 10 in this way, a plate spring 56 is provided in the driving force transmission portion 50 of the rotor shaft 10, and the rotor shaft 10 has a discharge chamber 18 side. The force toward is applied.
[0006]
In general, in a gas compressor called an open type in which one end of the rotor shaft is exposed to the atmosphere side, a thrust load imbalance occurs on the rotor shaft due to the difference between the pressure in the gas compressor and the atmospheric pressure. A mechanism for balancing is provided.
As an invention relating to such a vane rotary type gas compressor, there is the following gas compressor.
[0007]
[Patent Document 1] Japanese Unexamined Patent Application Publication No. 2002-174190
[0008]
In the present invention, in order to reduce the thrust imbalance of the rotor, the area where the hydraulic pressure acts on the rotor and the value of the hydraulic pressure are set to appropriate values.
[0009]
[Problems to be solved by the invention]
However, in recent years, for example, the pressure in the discharge chamber 18 tends to be increased by using, for example, CO 2 as a refrigerant gas, and the elastic force of the leaf spring 56 can appropriately eliminate the thrust load imbalance applied to the rotor shaft 10. It has become difficult.
If the thrust load applied to the rotor shaft 10 is not balanced and the rotor shaft 10 is pressed toward the driving force transmission unit 50, the friction generated when the rotor 9 rotates increases or the compressed gas leaks. Therefore, it is conceivable that the efficiency of the gas compressor is reduced or the service life is reduced.
[0010]
Accordingly, an object of the present invention is to provide a gas compressor having high efficiency and a long service life by correcting an imbalance in thrust load applied to the rotor shaft.
[0011]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides an intake port for sucking compressed gas, a cylinder in which a discharge port for discharging compressed gas is formed, and a bearing fixed to the cylinder. , A rotor shaft that is rotatably supported by the bearing, has a hydraulic pressure pressurized at one end using the pressure of the compressed gas, and an atmospheric pressure at the other end, and is coaxial with the axis of the rotor shaft, A flange-shaped protrusion formed on the rotor shaft, a rotor fixed to the rotor shaft and housed in the cylinder, an inner peripheral surface of the cylinder and an outer periphery of the rotor A vane that divides a space formed between the surface and forms a compression chamber, an oil storage chamber that stores oil pressurized by compressed gas discharged from the cylinder, and the oil storage in the protrusion. Oil stored in the chamber Force acting means for acting on the rotor shaft a force in a direction from the other end side where the atmospheric pressure acts to one end side where the hydraulic pressure acts. A gas compressor is provided (first configuration).
Here, the force application means of the first configuration is configured such that the hydraulic pressure acting on the end face on the other end side of the protrusion is larger than the hydraulic pressure acting on the end face on the one end side, so that the rotor shaft It can comprise so that the force of the direction which goes to the said one end side may be applied from the other end side (2nd structure).
In addition, a cylindrical inner peripheral surface is formed around the protruding portion of the first configuration or the second configuration with a predetermined gap therebetween, and the hydraulic pressure acting on the end surface on the other end side is formed. The pressure can be reduced in the gap so as to act on the end surface on the one end side (third configuration).
Furthermore, an oil passage is provided in the axial direction of the rotor shaft in at least one of the projections of the first configuration, the second configuration, or the third configuration, and the joints between the projections and the rotor shaft. The oil pressure acting on the end face on the other end side can be reduced in pressure in the oil passage and act on the end face on the one end side (fourth structure).
The force acting means of each configuration from the first configuration to the fourth configuration can be configured to be formed in the bearing and supply lubricating oil pressure to the bearing (fifth configuration).
For the rotor shaft of each configuration from the first configuration to the fifth configuration, the magnitude of the resultant force acting from the one end side to the other end side and the other end side acting on the one end side The resultant force can be configured to be equal in magnitude (sixth configuration).
[0012]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described in detail with reference to the drawings.
(1) Outline of Embodiment In an open type gas compressor that obtains rotational driving force from the outside, one end of the rotor shaft is located inside the gas compressor and the other end is exposed to the atmosphere. Due to the pressure difference between the pressure and the atmospheric pressure, the rotor shaft is biased in the thrust direction (axial direction).
In this embodiment, in order to correct this bias of thrust load, a force acting from the atmospheric pressure side to the compressor internal pressure side is applied to the rotor shaft using the pressure of the compressed gas.
As the pressure of the compressed gas increases, the force acting on the rotor shaft from the atmospheric pressure side to the compressor internal pressure side also increases accordingly, so that the unbalance of the force acting on the rotor shaft can be effectively reduced even in the high pressure region, The gas can be compressed to a high pressure.
[0013]
FIG. 3A is a view showing a mechanism for generating such a force, and shows an end portion of the rotor shaft 10 on the compressor internal pressure side.
An annular portion 35 is formed in an annular shape at the end of the rotor shaft 10. A hydraulic pressure P3 pressurized by compressed gas is acting on the end surface S3 of the annular portion 35.
On the other hand, the hydraulic pressure P2 reduced in pressure by passing through the bearing portion 6a acts on the end surface S2 facing the end surface S3.
When the high pressure oil pressure P3 acts on the end surface S3 of the annular portion 35, a force toward the compressor internal pressure side can be applied to the rotor shaft 10.
[0014]
(2) Details of Embodiment FIG. 1 is a diagram showing an axial sectional view of a gas compressor 95 according to the present embodiment. The same components as those in FIG. 8 (conventional example) are denoted by the same reference numerals.
The gas compressor 95 is configured by storing the gas compressor body 3 in a cylindrical casing 1 having one end closed and the other end sealed by the front head 2.
A suction port 16 for sucking compressed gas is formed on the opening end side of the casing 1, and a discharge port 19 is formed on the closed side.
The gas is sucked from the suction port 16, compressed by the gas compressor body 3, and then discharged from the discharge port 19.
[0015]
The gas compressor body 3 includes a cylinder 7 in which a rotor 9 is housed, a front side block 5 that closes an end surface on the suction port 16 side of the cylinder 7, and a rear side block 6 that closes an end surface on the discharge port 19 side of the cylinder 7. Has been.
The front side block 5 is provided with a suction port for sucking gas, and the rear side block 6 is provided with a discharge port for discharging compressed gas.
At the center in the radial direction of the front side block 5 and the rear side block 6, a bearing part 5a and a bearing part 6a for rotatably supporting a rotor shaft 10 formed on the rotor 9 are provided.
[0016]
Here, the structure of the gas compressor main body 3 is demonstrated using FIG.
FIG. 2 is a cross-sectional view showing the AA cross section of FIG. 1 as viewed from the driving force transmission unit 50 side.
The gas compressor body 3 is configured such that a cylinder 7 is stored on the inner periphery of the casing 1, and a rotor 9 is further stored on the inner periphery side of the cylinder 7.
[0017]
A plurality of vanes 13 are arranged in the rotor 9 so as to be able to appear and retract in a substantially radial direction. A cylinder chamber 8 is formed by partitioning the inner periphery of the cylinder 7, the outer periphery of the rotor 9, and the space surrounded by the end surfaces of the front side block 5 and the rear side block 6 shown in FIG. .
The cylinder 7 has a substantially elliptical cross section, and when the rotor 9 rotates, the tip of the vane 13 slides along the inner peripheral surface of the cylinder 7 and the volume of the cylinder chamber 8 changes mechanically. .
[0018]
The gas compressor main body 3 sucks the gas to be compressed by the time when the volume of the cylinder chamber 8 is approximately maximized into the cylinder 7 and discharges the gas in the cylinder chamber 8 until the volume of the cylinder chamber 8 is minimized. This compresses the gas mechanically.
A back pressure chamber 4a filled with oil supplied from salai 26a and 26b, which will be described later, is provided at the bottom of the vane groove 4. When the rotor 9 rotates, the vane 13 is connected to the inner peripheral surface of the cylinder 7. It is designed to be pressed.
Further, when high-pressure gas is discharged from the cylinder chamber 8, high-pressure oil is supplied from the high-pressure hole 27 to the back pressure chamber 4 a to prevent gas leakage at the tip of the vane 13.
[0019]
Returning to FIG. 1, a discharge chamber 18 in which high-pressure gas compressed by the gas compressor body 3 is discharged is formed in the space on the discharge port 19 side in the casing 1. An oil reservoir 30 pressurized by the compressed gas in the discharge chamber 18 is formed.
An oil passage 105 and an oil passage 106 are formed from the oil reservoir 30 to the bearing portion 5a and the bearing portion 6a, and pressurized oil is supplied to the bearing portion 5a and the bearing portion 6a.
[0020]
The oil supplied to the bearing portion 5a and the bearing portion 6a acts as a lubricating oil in these bearing portions, and also, the sarays 26a and 26b formed on the rear side block 6 and the sarays 25a and 25b formed on the front side block 5. The back pressure is supplied to the back pressure chamber 4 a (FIG. 2) of the rotor 9 via.
[0021]
The sarays 26a and 26b are fan-shaped depressions recessed in the end surface of the rear side block 6 and have shapes that are axisymmetric with each other.
The salai 26a is filled with intermediate pressure oil that has been depressurized by the bearing portion 6a (oil is depressurized by passing through a gap between the inner peripheral surface of the bearing portion 6a and the outer peripheral surface of the rotor shaft 10). The salai 26b is filled with an oil passage 107 formed at the end of the rotor shaft 10 and an intermediate pressure oil that has been decompressed via the saray passage 109.
The sarays 26a and 26b communicate with the end face of the back pressure chamber 4a of the rotor 9 and supply the intermediate pressure to the back pressure chamber.
[0022]
Since the configurations of the sarays 25a and 25b are the same as those of the sarays 26a and 26b, description thereof will be omitted.
The salai 25a is filled with intermediate pressure oil decompressed by the bearing portion 5a, and the intermediate pressure oil is supplied to the salai 25b via the salai passage 110.
[0023]
A driving force transmission unit 50 for obtaining a rotational driving force for rotating the rotor 9 is formed at the tip of the rotor shaft 10 on the suction port 16 side.
The driving force transmission unit 50 constitutes an electromagnetic clutch, and includes a pulley unit including a magnet 54 and a pulley 52.
The pulley 52 is provided with a drive belt that is linked to an automobile engine or the like, so that the rotational driving force of the engine or the like is transmitted.
[0024]
While the gas compressor 95 is operating, the pulley portion is attracted in the direction of the gas compressor body 3 by the magnet 54.
A leaf spring 56 is disposed on the pulley portion, and the rotor shaft 10 is pressed toward the gas compressor main body 3 as the magnet 54 is attracted.
The elastic force of the leaf spring 56 counteracts the force by which the pressure inside the gas compressor 95 pushes the rotor shaft 10, thereby reducing the bias of thrust load generated on the rotor shaft 10. The leaf spring 56 may be an elastic body such as rubber.
[0025]
At the end of the rotor shaft 10 on the side of the gas compressor main body 3, an annular portion 35, which is a protrusion having a flange shape projecting from the rotor shaft 10 in the radial direction, is formed.
The end surface of the annular portion 35 on the driving force transmission unit 50 side is in contact with the high-pressure oil that has been transported through the oil passage 106, and hydraulic pressure in the direction from the driving force transmission unit 50 toward the discharge chamber 18 acts. Yes.
[0026]
Next, the annular portion 35 will be described in detail with reference to FIG.
The high pressure oil transported from the oil reservoir 30 acts on the end surface of the annular portion 35 on the side of the driving force transmission unit 50 (the area is referred to as S3 and the end surface S3), and the high pressure oil pressure P3 acts. .
As a result, a force of P3 × S3 acts on the annular portion 35 in the direction from the driving force transmitting portion 50 toward the discharge chamber 18.
[0027]
The oil passage 107 is filled with oil transported from the oil passage 106 via the bearing portion 6a. This oil acts on the rotor shaft 10 with a hydraulic pressure P2 that has been reduced in pressure by passing through the gap of the bearing portion 6a to an intermediate pressure.
A force of P2 × S2 acts in the direction from the discharge chamber 18 toward the driving force transmission unit 50 on the end surface of the annular portion 35 on the oil passage 107 side (the area is S2 and is described as the end surface S2). Yes.
As a result, the resultant force expressed by the following expression (1) acts on the annular portion 35 (that is, the rotor shaft 10) in the direction from the discharge chamber 18 toward the driving force transmitting portion 50.
[0028]
## EQU1 ## P2 * S2-P3 * S3 (where P2 <P3) (1)
[0029]
On the other hand, when the annular portion 35 does not exist as shown in FIG. 3B (in the case of the conventional gas compressor 59), the rotor shaft 10 has a force represented by the following expression (2). , Acting in the direction from the discharge chamber 18 toward the driving force transmission unit 50.
[0030]
## EQU2 ## P2 × (S2-S3) (2)
[0031]
Here, in order to examine the magnitude relationship between the force represented by Equation (1) and the magnitude of the force represented by Equation (2), subtracting Equation (1) from Equation (2) yields the following equation ( 3) is obtained.
[0032]
(P3−P2) × S3 (> 0) (3)
[0033]
Since the result of the subtraction is positive, it can be seen that the magnitude of the force represented by Expression (1) is smaller than the magnitude of the force represented by Expression (2).
In this way, by providing the annular portion 35, the magnitude of the force acting on the rotor shaft 10 in the direction from the discharge chamber 18 toward the driving force transmitting portion 50 can be reduced.
This is an effect due to the pressure difference between the hydraulic pressures at the end surface S3 and the end surface S2 of the annular portion 35.
In this way, the annular portion 35 constitutes a force acting means together with the outer peripheral surface around it.
[0034]
FIG. 4 is a diagram for explaining conditions for balancing (equilibrium) the force (thrust load) acting in the axial direction of the rotor shaft 10.
Since each salai communicates with the back pressure chamber 4a and the like and has a similar shape, the pressure Ps acting on the rotor 9 at the salais 25a and 25b and the salais 26a and 26b cancels out to zero. .
As shown in the figure, the axial pressure acting on the rotor shaft 10 in the direction from the driving force transmitting portion 50 to the discharge chamber 18 is applied to the end surface S1 and the end surface S3 of the annular portion 35. P3 that acts. Further, in this direction, a force FCL is applied by the electromagnetic clutch of the driving force transmission unit 50.
[0035]
On the other hand, the pressure in the direction from the discharge chamber 18 toward the driving force transmission unit 50 is P2 that acts on the end surface S2 of the annular portion 35.
For this reason, the axial force acting on the rotor shaft 10 is balanced when the following expression (4) is satisfied.
[0036]
## EQU4 ## P2 * S2- (P3 * S3 + P1 * S1 + FCL) = 0 (4)
[0037]
When the rotor shaft 10 further has an end face perpendicular to the axial direction, the area of the end face is multiplied by the acting pressure, and a sign is set according to the direction of the pressure and inserted into the equation (4).
Further, if the forces acting on the sarays 25a and 25b and the sarays 26a and 26b are not balanced, these may be included in the equation (4) in the same manner.
[0038]
By designing the gas compressor 95 to satisfy the equation (4), the axial thrust load applied to the rotor 9 can be balanced.
As a result, it is possible to prevent the compressed gas from leaking due to the thrust load bias, and the durability of the gas compressor 95 can be improved.
In addition, when the thrust load acting on the rotor 9 is biased toward the driving force transmission unit 50, a large friction is generated on the contact surface between the front side block 5 and the rotor 9, but this friction is balanced by balancing the thrust load bias. The force can be reduced and the efficiency of the gas compressor 95 can be increased.
[0039]
The rotor shaft 10 and the annular portion 35 may be integrally formed, or the ring-shaped annular portion 35 and the cylindrical rotor shaft 10 may be configured as separate members.
In the case of constituting as another member, the rotor shaft 10 is inserted into the annular portion 35 and the annular portion 35 is fixed to the rotor shaft 10 by a fixing method such as welding or caulking.
Further, in this case, a configuration may be adopted in which oil is circulated by providing a gap between the annular portion 35 and the insertion portion of the rotor shaft 10. The oil is moderately depressurized by this gap.
Alternatively, a through hole may be formed in the end surface of the annular portion 35, and the oil may be decompressed by passing through the through hole.
[0040]
FIGS. 5A and 5B are diagrams showing a modified example of the configuration of the annular portion 35.
Among these, Fig.5 (a) represents the axial direction sectional drawing, FIG.5 (b) represents the front view.
In this example, the rotor shaft 10a is inserted and fixed in the center hole of the ring-shaped annular portion 35a.
[0041]
The annular portion 35a and the rotor shaft 10a are fixed by, for example, spot welding 61, caulking, laser welding, or other fixing methods.
A gap 62 is formed over the entire circumference (excluding the spot weld 61) at the joint between the annular portion 35a and the rotor shaft 10a.
The gap 62 allows oil to pass through and forms an oil passage.
[0042]
A recess is formed along the inner periphery of the annular portion 35 along the inner periphery, and a substantially similar recess is also formed on the rear side block 6 side corresponding to the recess.
The small chamber 60 is formed by the concavity on the ring portion 35 side and the concavity on the rear side block 6 side facing each other.
The small chamber 60 is filled with oil that has been transported through the oil passage 106.
[0043]
The oil filled in the small chamber 60 passes through the gap 62 and reaches the oil passage 107. The oil that has reached the oil passage 107 is decompressed by passing through the gap 62.
[0044]
In the present modification, a pressure reducing gap 62 is provided between the annular portion 35a and the rotor shaft 10a, and optimal pressure reduction can be performed by appropriately adjusting the design value of the gap 62.
Further, since the oil is stored in the small chamber 60, the oil can be efficiently supplied to the entire bearing portion 6a, and the oil lubrication action can be effectively utilized.
[0045]
FIG. 6 is a diagram for explaining a modification of the annular portion 35a.
A groove 65 is formed along the entire circumference of the outer circumferential surface of the annular portion 35 a, and a lip seal 66 is disposed in the groove 65.
The lip seal 66 is a ring-shaped member made of a material having elasticity such as rubber, resin, or metal. The inner peripheral side of the lip seal 66 is in close contact with the bottom of the groove 65, and the outer peripheral side is pressed against the inner peripheral surface of the rear side block 6.
[0046]
With this configuration, it is possible to prevent oil from leaking into the oil passage 107 along the outer periphery of the annular portion 35a.
For this reason, oil can be supplied from the gap 62 to the oil passage 107 without passing through the outer circumference of the annular portion 35a, and the radial width or thrust direction of the gap 62 or the inner circumferential surface of the gap 62 can be reduced. By appropriately setting the surface roughness and the like, the hydraulic pressure in the oil passage 107 can be controlled more accurately.
[0047]
FIG. 7 is a view showing a gas compressor 96 which is a modification of the present embodiment.
In the gas compressor 95 described above, the annular portion 35 is formed on the rear side block 6 side. However, in the gas compressor 96 of this modification, the annular portion 35b is formed on the front side block 5 side.
In FIG. 7, the component corresponding to the gas compressor 95 is shown with the same code | symbol as FIG.
[0048]
The annular portion 35 b is formed in a portion of the rotor shaft 10 corresponding to the front side block 5.
A pressure chamber 70 in which high-pressure oil that has been transported through the oil passage 105 is stored is formed on the end surface of the annular portion 35b on the driving force transmission unit 50 side. The portion 35b is pressed toward the discharge chamber 18 side.
[0049]
The end surface on the discharge chamber 18 side of the annular portion 35b constitutes a part of the bottom surface of the sarays 25a and 25b, and the decompressed oil is stored through the side surface of the annular portion 35b.
As described above, even when the annular portion 35b is provided on the front side block 5 side, a force for pressing the rotor shaft 10 in the direction from the driving force transmitting portion 50 toward the discharge port 19 is generated as in the present embodiment. Can do.
[0050]
In this modification, the annular portion 35b is provided on the front side block 5 side. However, by providing the annular portion 35 on the rear side block 6 side and further providing the annular portion 35b on the front side block 5 side, the rotor shaft The force which presses 10 toward the discharge port 19 can be strengthened.
[0051]
The following effects can be obtained by the present embodiment and the modifications described above.
(1) Thrust load bias generated in the rotor shaft 10 can be reduced by an open type gas compressor that receives power from the outside.
(2) Thrust load bias of the rotor shaft 10 can be mitigated by using compressed gas pressure.
(3) As the pressure of the compressed gas in the discharge chamber 18 increases, the force for correcting the bias of the thrust load increases with the pressure of the compressed gas. Therefore, even in a region where the pressure of the compressed gas is high, the thrust load bias can be effectively corrected, and the pressure of the compressed gas can be increased.
Therefore, for example, refrigerant gas that needs to be compressed to a high pressure such as CO 2 can be compressed.
(4) By designing the gas compressor 95 so as to satisfy the expression (4), it is possible to eliminate the thrust load bias acting on the rotor shaft 10.
(5) By reducing the bias of the thrust load, the efficiency of the gas compressor 95 can be increased, and wear of components of the gas compressor 95 can be reduced.
[0052]
While the present embodiment and modifications have been described above, the present invention is not limited to these, and various modifications can be made within the scope described in each claim.
For example, in the embodiment described above, an annular member that applies hydraulic pressure is provided on at least one of the front side block 5 and the rear side block 6, but the location of the member that applies hydraulic pressure is not limited thereto, and the rotor shaft You may form in 10 other places.
[0053]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to this invention, the gas compressor which improved the bias of the thrust load of a rotor can be provided.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view in the axial direction of a gas compressor according to an embodiment.
FIG. 2 is a cross-sectional view showing a configuration in a direction perpendicular to the axis of the gas compressor of the present embodiment.
FIG. 3 is a diagram for explaining an annular portion.
FIG. 4 is a diagram for explaining conditions for balancing thrust load.
FIG. 5 is a diagram for explaining a modification of the annular portion.
FIG. 6 is a diagram for explaining a modification of the annular portion.
FIG. 7 is a view for explaining a modification of the gas compressor.
FIG. 8 is a view showing an axial sectional view of a conventional gas compressor.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Casing 2 Front head 3 Gas compressor main body 4 Vane groove 5 Front side block 5a Bearing part 6 Rear side block 6a Bearing part 8 Cylinder chamber 9 Rotor 10 Rotor shaft 13 Vane 16 Suction port 18 Discharge chamber 19 Discharge port 30 Oil sump 35 yen Ring portion 50 Driving force transmission portion 54 Magnet 56 Leaf spring 105 Oil passage 106 Oil passage 107 Oil passage

Claims (6)

An intake port for sucking in the gas to be compressed, a cylinder formed with a discharge port for discharging the compressed gas, and
A bearing fixed to the cylinder;
A rotor shaft that is rotatably supported by the bearing, a hydraulic pressure that is pressurized using the pressure of the compressed gas acts on one end, and an atmospheric pressure acts on the other end;
A flange-shaped protrusion formed on the rotor shaft, coaxially with the axis of the rotor shaft;
A rotor fixed to the rotor shaft and stored in the cylinder;
A vane that is formed so as to freely protrude and retract in the rotor, and that defines a space formed between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor, and forms a compression chamber;
An oil storage chamber for storing oil pressurized by compressed gas discharged from the cylinder;
The oil pressure stored in the oil storage chamber is applied to the protruding portion, and the force in the direction from the other end side where the atmospheric pressure is applied toward the one end side where the hydraulic pressure is applied is applied to the rotor shaft. Force acting means to act on,
A gas compressor characterized by comprising: The force acting means increases the hydraulic pressure acting on the end face on the other end side of the protrusion portion to be larger than the hydraulic pressure acting on the end face on the one end side, thereby causing the rotor shaft to move from the other end side to the one end side. The gas compressor according to claim 1, wherein a force in a direction of application is applied. A cylindrical inner peripheral surface is formed around the protrusion with a predetermined gap therebetween, and the hydraulic pressure acting on the end surface on the other end side is reduced in pressure to act on the end surface on the one end side. The gas compressor according to claim 1, wherein the gas compressor is provided. At least one of the protrusion and the joint between the protrusion and the rotor shaft is provided with an oil passage in the axial direction of the rotor shaft, and the oil pressure acting on the end surface on the other end side is the oil passage. The gas compressor according to claim 1, wherein the gas compressor is acted on an end face on the one end side. The gas compressor according to any one of claims 1 to 4, wherein the force acting means is formed in the bearing and supplies lubricating oil pressure to the bearing. The magnitude of the resultant force acting on the rotor shaft from the one end side to the other end side is equal to the magnitude of the resultant force acting on the one end side from the other end side. The gas compressor according to any one of claims 1 to 5.

Images