JPS6122151B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane-type gas compressor used in car coolers or other relatively small-sized refrigeration equipment.

A rotary compressor, which is generally called a rotary compressor, has a cylinder chamber that is composed of a cylindrical cylinder and both side blocks that are erected parallel to each other on both sides of the cylinder. In this structure, a rotor having vanes that can move forward and backward is rotatably horizontally mounted, and the cylinder chamber is thereby divided into a plurality of work chambers, and the desired compression work is sequentially performed by rotation of the rotor. Then, lubricating oil is pumped into the cylinder chamber by the discharge pressure from the cylinder chamber to lubricate the seals of each sliding part, and a portion of this lubricating oil is applied to the slit base of the rotor where the vane is fitted and held. The contact pressure of the vanes against the inner wall of the cylinder is obtained from the synergistic effect of the hydraulic pressure and the centrifugal force accompanying the rotation of the rotor.

However, in the above-mentioned structure, the rotor is connected to a prime mover whose rotation changes transiently, such as an automobile engine, and there is also a considerable speed difference between startup and normal operation. The rotation ranges over a wide range from relatively low speed to high speed. Therefore, as mentioned above, even if the pressure of the lubricating oil supplied into the slit of the rotor where the vane is fitted and held is constant, the centrifugal force of the vane changes directly with the rotation of the rotor. If the rotor rotates at high speed, the contact pressure of the vanes against the inner wall of the cylinder inevitably becomes excessive, and there is a risk that the vanes will wear out significantly due to the excessive frictional force, resulting in a decline in the functionality of the entire device.

This invention was made in view of the above-mentioned points, and a spiral oil feed groove is formed on either the movable side or the fixed side of the rotor shaft bearing part, and the oil feed groove is formed in the rotor shaft bearing part on either the movable side or the fixed side. The pump action actively discharges the lubricating oil in the cylinder chamber to the outside of the cylinder chamber, and the contact pressure of the vanes, which is obtained by the pressure of the lubricating oil in the cylinder chamber and centrifugal force, is independent of the rotation of the rotor. The present invention provides a gas compressor configured to perform suppression control as much as possible.

Hereinafter, one embodiment of the present invention will be described in detail based on the drawings.

FIG. 1 shows an overall outline of the gas compressor of the present invention, which is roughly divided into a compressor main body 1, a casing 2 with an open end surrounding the compressor main body 1, and an open surface of the casing 2. The front head 3 is attached to seal the front head 3.

The compressor main body 1 is composed of a cylinder 4 having an elliptical inner periphery, and a front side block 5 and a rear side block 6 fixed in parallel to each other on both end surfaces of the cylinder 4. These three members form an elliptical cylinder chamber. , rotor shafts 7a, 7 are inside this
A solid cylindrical rotor 7 integrated with the rotor b is rotatably suspended horizontally. The straight rotor 7 is set to be slightly smaller than the short diameter of the cylinder chamber and is inscribed within the cylinder chamber, and the rotor shaft 7b is fitted and held in a bearing recess 8 formed in the rear side block 6. , also the rotor shaft 7a
The base is held in the bearing hole 9 of the Freud side block 5 and sealed by a mechanical seal 10, the tip of which protrudes from the end surface of the front head 3 and is connected to the motor side via an electromagnetic clutch (not shown). , whereby the rotor 7 is rotationally driven.

Further, as shown in FIG. 2, four slits 11, 11 are formed radially in the rotor 7 with a phase of approximately 90 degrees in the radial direction. vane 1
2 and 12 are slidably held, and the tip end of each is pressed against the inner wall of the cylinder chamber to divide the cylinder chamber into a plurality of working chambers.

Reference numerals 13, 13 are fan-shaped pressure receiving recesses formed on both end surfaces of the rotor 7 so as to be inclined toward the direction of rotation thereof. They are formed radially at equal pitches from the axis, and dynamic pressure due to lubricating oil is applied to the pressure receiving recesses 13, 13 by the relative sliding motion between the rotor 7, front side block 5, and rear side block 6, as described later. The rotor 7 is generated to lubricate the end face of the rotor 7 and simultaneously position the rotor 7 in the thrust direction within the cylinder chamber, thereby ensuring rotational clearance between the side blocks 5, 6 and the rotor 7.

14, 14 are intake ports formed on the peripheral wall of the cylinder 4, and these intake ports 14, 14 are connected to the air space 15 of the cylinder 4 and the introduction groove 16 formed annularly inside the front head 3 (see FIG. 3). Further, this introduction groove 16 is communicated with a suction port 17 attached to the upper end of the front head 3 to introduce relatively low pressure refrigerant gas (hereinafter simply referred to as gas).

Reference numerals 18 and 18 designate discharge ports similarly formed on the peripheral wall of the cylinder 4, and each of the discharge ports 18 and 18 is provided with a reed valve 19 consisting of a discharge valve 19a and a valve support 19b on its discharge side, and is compressed in the cylinder chamber. The high-pressure gas is discharged from port 1.
A pair of oil separators 21 and 2 are attached to the outside of the rear side block 6 through a space 20 from 8 and 18.
The gas that has been oil-separated therein passes through a high pressure chamber in the casing 2 and is discharged from the discharge port 22.

The oil separators 21, 21 introduce the high-pressure gas discharged from the compressor main body 1 into the oil separator 1, and change the direction and speed of the movement, or increase the contact area of the gas, thereby preventing the oil from being mixed into the high-pressure gas. The lubricating oil particles are separated and returned to the lubricating oil stored at the bottom of the casing 2. still,
In the drawings, a pair of intake ports 14, 14 and discharge ports 18, 18 are shown, but it is clear from the overall configuration that in reality, another pair of intake and discharge ports are provided.

Reference numeral 23 denotes an oil hole formed in the lower half of the rear side block 6. The lower end of this oil hole 23 opens into the lubricating oil in the casing 2, while the other end connects the rear side block 6 and the rotor shaft 7b. The annular grooves 29 and 2 of the rotor 7 are connected to each other through an oil passage 24 formed between
It is connected to 9.

Therefore, when the rotor 7 is driven to rotate, low pressure gas is sucked into the cylinder chamber from the intake ports 14, 14, and high pressure gas compressed within the cylinder chamber is discharged from the discharge ports 18, 18. As a result, the inside of casing 2 becomes a high pressure chamber,
This pressure forces lubricating oil into the oil hole 23. The lubricating oil press-fitted into the oil hole 23 in this way lubricates the bearing part of the rotor shaft 7b, and further lubricates the bearing part of the rotor shaft 7b.
into the slits 11, 11 of the vanes 12,
12 is urged outward to bring it into tighter pressure contact with the inner wall of the cylinder, and at the same time acts to lubricate the seal.
Also, a part of this lubricating oil is press-fitted into the pressure receiving recesses 13, 13 formed on both end faces of the rotor 7, and performs a lubricating action on the rotational clearance between the side blocks 5, 6 and the rotor 7. Due to the relative sliding motion between the side blocks 5, 6 and the rotor 7, dynamic pressure is generated within the pressure receiving recesses 13, 13, and this positions the rotor 7 in the thrust direction within the cylinder chamber, thereby ensuring smooth rotational movement. will be carried out.

Reference numeral 25 denotes a spiral oil feed groove formed on the outer periphery of the base of the rotor shaft 7a, that is, the shaft bearing part with the front side block 5. One end of this oil feed groove 25 opens into the cylinder chamber, and the other end opens into the cylinder chamber. is a space 2 hermetically sealed by a mechanical seal 10.
6, thereby opening between the cylinder chamber and the air space 2.
6, so that a portion of the lubricating oil in the cylinder chamber is forcibly delivered into the space 26 by the pumping action of the oil feed groove 25.

That is, as the rotor 7 rotates, a pumping action is obtained by the sliding movement between the oil feed groove 25 formed on the outer periphery of the rotor and the inner periphery of the bearing hole 9 of the front side block 5. As the rotational speed of the slits 11, 11 increases, the efficiency of the pumping action increases, and the vanes 12, 12 are fitted and held in the slits 11, 11.
The lubricating oil inside is sucked, and the amount of lubricating oil discharged into the space 26 becomes large. Therefore vane 12,1
Contrary to this, as the centrifugal force of 2 increases, the lubricating oil in the slits 11, 11 is forcibly discharged outside the cylinder chamber, so the contact pressure of the vanes 12, 12 against the cylinder chamber wall is suppressed. Even when the rotor 7 rotates at high speed, the contact pressure between the vanes 12, 12 obtained by hydraulic pressure and centrifugal force is appropriately controlled without being directly related to the rotation of the rotor 7.

Reference numeral 27 denotes a communication hole formed to communicate the air gap 26 hermetically sealed by the mechanical seal 10 of the front head 3 with the introduction groove 16 also formed inside the front head 3. As shown in FIG. 3, the terminal end of this communication hole 27 opens to the intake port 14 side through a pipe 28 and an opening hole 28a protruding from the wall surface of the introduction groove 16, so that the space 26 is always kept open. The lubricating oil discharged into the space 26 is maintained as a low-pressure chamber, and is again introduced into the cylinder chamber together with the low-pressure gas through the communication hole 27 for circulation.

The communication hole 27 has a large influence on the performance of the mechanical seal 10. That is, by maintaining the air space 26 hermetically sealed by the mechanical seal 10 as a low-pressure chamber at all times, it becomes possible to significantly reduce the load on the mechanical seal 10 in the thrust direction, thereby increasing the life of the mechanical seal itself. This will greatly contribute to the

In the above embodiment, the oil feed groove 25 is formed on the outer periphery of the rotor shaft 7a, but the same effect can be obtained by forming it on the inner periphery of the bearing hole 9 instead.

As is clear from the above description, the gas compressor according to the present invention has a spiral oil feed groove communicating between the inside and outside of the cylinder on either the fixed side or the movable side of the rotor shaft bearing part, and the rotor. The lubricating oil in the cylinder chamber is discharged to the outside of the cylinder chamber by the pumping action of the bearing part as it rotates, and the oil pressure acting on the vane is suppressed, so that the oil pressure in the cylinder chamber of the vane is obtained by this oil pressure and centrifugal force. Since the contact pressure against the wall is controlled within the desired range, even if the rotational speed of the rotor changes, the contact pressure of the vanes is maintained within the specified pressure range without being directly affected. Since excessive contact pressure is not applied to the vanes, it is possible to minimize the friction and friction of the vanes themselves. Further, as described above, since the oil feed groove having the pumping action is provided integrally with the rotor, there is an advantage that the structure can be simplified and the desired purpose can be achieved without providing any special equipment.

[Brief explanation of the drawing]

FIG. 1 is a sectional view schematically showing the entire gas compressor according to the present invention, FIG. 2 is an explanatory end view of the rotor,
FIG. 3 is a front view of the front head. 1...Compressor main body, 2...Casing, 3...
Front head, 4...Cylinder, 5...Front side block, 6...Rear side block,
7... Rotor, 7a, 7b... Rotor shaft, 9...
Bearing hole, 11...slit, 12...vane, 2
5... Oil feed groove.

Claims (1)

[Claims] 1 A rotor having vanes that can be slid in the radial direction is rotatably mounted horizontally in a cylinder chamber composed of a cylindrical cylinder and side blocks attached to both sides of the cylinder, and is installed inside a compressor. Lubricating oil is supplied into this cylinder chamber by a predetermined pressure feeding means provided in the cylinder, and at the same time, a part of this lubricating oil is forced into the slit of the rotor in which the vane is held, and this oil pressure and centrifugal force are combined. In a gas compressor configured to obtain the contact pressure of the vane against the inner wall of the cylinder by,
A spiral oil feed groove communicating between the inside and outside of the cylinder chamber is formed on either the fixed side or the movable side of the rotor shaft bearing surface of the rotor, and the pump of the rotor shaft bearing portion is formed as the rotor rotates. The lubricating oil acting on the vane is discharged to the outside of the cylinder to suppress the hydraulic pressure acting on the vane, and the contact pressure of the vane against the inner wall of the cylinder obtained by this oil pressure and centrifugal force is controlled within a desired range. A gas compressor characterized in that it is configured to.