JPH04279789A - Fluid compressor - Google Patents

Abstract

PURPOSE:To enhance both refrigerating capacity and compression performance by securing the sufficient quantity of fluid sucked in with a suction leading passage enlarged in diameter as much as possible without changing a suction side bearing member and a pivotally supporting hole in diameter. CONSTITUTION:Since a suction leading passage 14 which is provided for a main bearing section 6 acting as a suction side bearing member for compressed fluid to be led into a working chamber 10 at the suction side end from the outside of a cylinder 4, is formed into plural suction ports 25 which are forcibly opened within an allowable range in the remaining cross section of a pivotally supporting hole 6a pivotally supporting the shaft section 5a of a piston 5, or is formed into a suction oblong hole 14A the cross section of which is deformed, the sufficient quantity of fluid sucked in can be secured with the suction leading passage enlarged in diameter as much as possible, both refrigerating capacity and compression performance can be enhanced with suction efficiency enhanced.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor for compressing a fluid to be compressed, such as refrigerant gas in a refrigeration cycle.

0002

[Prior Art] Conventionally, for example, the structure of the drive mechanism is simpler than the reciprocating type, rotary type, etc. used as a compressor to compress refrigerant gas in a refrigeration cycle, and there are fewer parts and no check valve is required. A fluid compressor that can improve compression efficiency has been developed.

[0003] In this type of compressor, a piston as a rotating body is arranged eccentrically inside a cylinder, and both ends of the cylinder and piston are connected to the eccentricity of a main bearing, which is a suction side bearing, and a sub bearing, which is a discharge side bearing. It is rotatably supported in the position.

A spiral groove is formed on the outer periphery of the piston, and a blade is wound around the spiral groove so as to be protrusive and retractable, and the inside of the cylinder gradually moves from the suction side end to the discharge side end. A plurality of working chambers each having a small volume are formed therein.

[0005] An electric motor is provided on the peripheral wall of the cylinder, and the cylinder and piston are rotated relatively and synchronously via a rotational force transmission mechanism provided in the cylinder and the piston.

Accordingly, the low-pressure refrigerant gas can be compressed while being gradually transferred from the suction side end of the cylinder to the working chamber at the discharge side end. When the refrigerant gas is discharged from the discharge side end, the refrigerant gas reaches a predetermined high pressure state and is discharged to the condenser, which is an external device.

By the way, in such a fluid compressor, suction pressure of refrigerant gas is applied to the suction side end of the cylinder.
Discharge pressure is applied to the discharge side end. Naturally, the discharge pressure is greater than the suction pressure.

This effect appears on the blade forming the working chamber and on the piston into which this blade is fitted. That is, a thrust force is applied to the blade and the piston from the suction end to the discharge end, and from the discharge end to the suction end.

Here, since the thrust force applied from the discharge end to the suction end is large, the piston suction side shaft is deeply inserted into the pivot hole of the main bearing, which is the suction side bearing. As a result, the piston and the main bearing end face slide against each other, causing friction loss. As an effective means to eliminate such problems, the present applicant has proposed, for example, Japanese Patent Application No. 63-333.
There is one disclosed in the specification of No. 584.

That is, the sum of the cross-sectional areas of the shaft portions at both ends of the piston is set to approximately match the cross-sectional area of the inner diameter of the cylinder, and the inside of each bearing is partitioned by the end surfaces of the shaft portions at both ends of the piston. Form a closed space.

[0011] A discharge pressure introduction means for introducing the compressed fluid increased to the discharge pressure into the bearing inner closed space of the main bearing, and a suction pressure introduction means for introducing the compressed fluid at the suction pressure into the bearing inner closed space of the auxiliary bearing. Equipped with

[0012] Therefore, the thrust force applied to the end face of the shaft portion of the piston by the discharge pressure introduction means and the suction pressure introduction means is balanced with the thrust force applied to the blade and the outer periphery of the piston, thereby eliminating the occurrence of the friction loss.

[0013]

However, even with this type of compressor, a larger displacement capacity is required and a larger refrigerating capacity must be obtained. for that purpose,
It is necessary to secure a larger amount of low-pressure compressed fluid introduced into the working chamber at least at the suction side end.

In other words, if a sufficient amount of the fluid to be compressed is sucked, the suction efficiency will be improved, resulting in a large refrigerating capacity. Specifically, since the main bearing as the suction side bearing is provided with a suction hole that introduces the compressed fluid into the working chamber at the suction side end, the diameter of the suction hole is increased.

Conventionally, as shown in FIGS. 7 and 8, the diameter Dφ of the main bearing A and the diameter dφ of the pivot hole c supporting the shaft portion of the piston are set in advance to required dimensions. The suction hole a must be provided in this remaining cross-sectional area.

As a result, in the main bearing A in which the discharge pressure introduction passage b as the discharge pressure introduction means as described above is provided, the suction hole a is provided parallel to the central axis of the pivot hole c that supports the piston. However, this cross-sectional area is not large.

[0017] Therefore, since a large cross-sectional area of the suction hole a is not ensured, the suction amount of the fluid to be compressed is small, the suction efficiency is reduced, and sufficient refrigerating capacity cannot be obtained, resulting in poor compression performance.

The present invention has been made in view of the above circumstances, and its object is to reduce the diameter of the suction conduit passage without changing the diameter of the suction side bearing member that pivotally supports the cylinder and piston, and the diameter of the pivot hole. The object of the present invention is to provide a fluid compressor that secures a sufficient suction amount by expanding the amount of water as much as possible, and that improves refrigerating capacity and compression performance by improving suction efficiency.

[0019]

[Means for Solving the Problems] In order to achieve the above object, the present invention provides a cylindrical cylinder, in which both ends of the cylinder are rotatably supported by two bearing members, and both ends of the cylinder are closed. The cylinder has a cylindrical rotating body arranged eccentrically along the axial direction of the cylinder, and the pivot holes provided at the eccentric positions of both the bearing members support the shafts at both ends of the rotating body. A spiral groove with a pitch that gradually decreases from the suction side end to the discharge side end of the cylinder is formed on the outer periphery of the rotating body, and the blade is fitted into the spiral groove so as to be able to move in and out in the radial direction of the rotating body. , the outer circumferential surface of the cylinder is brought into close contact with the inner circumferential surface of the cylinder to divide the space between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body into a plurality of working chambers, and the driving means moves the cylinder and the rotating body relative to each other. In a fluid compressor that sequentially transfers and compresses the compressed fluid that flows into the working chamber from the suction side end of the cylinder into the working chamber at the discharge side end of the cylinder by rotating the cylinder, the suction side bearing member A suction conduit is provided for introducing compressed fluid into the working chamber at the suction side end, and the suction conduit includes a plurality of suction holes that open within a strength-permissible range in the remaining cross section of the rotating body pivot hole. This is a fluid compressor characterized by comprising:

In order to achieve the above object, another invention provides a fluid compressor, wherein the suction side bearing member includes a suction conduit for introducing compressed fluid from the outside of the cylinder into the working chamber at the suction side end, This fluid compressor is characterized in that the suction conduit is an elongated suction hole whose cross section is deformed to the extent that the strength allows for the remaining cross section of the rotary body pivot hole.

[0021]

[Operation] With this configuration, the diameter of the suction conduit can be expanded as much as possible to obtain a sufficient suction amount without changing the diameter of the suction side bearing member that pivotally supports the cylinder and piston, and the diameter of the pivot hole. Can be secured.

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings, in which it is applied to a fluid compressor (hereinafter referred to as a compressor) used, for example, in a refrigeration cycle.

FIG. 1 shows a compressor according to an embodiment of the present invention,
The compressor main body 1 has a compression mechanism section 3 inside a closed case 2. The compression mechanism section 3 includes a cylinder 4 with both axial ends open and a predetermined size e inside the cylinder 4.
It consists of a piston 5 as a rotating body which is eccentrically arranged.

Both end shaft portions 5a and 5b of the piston 5 of the compression mechanism section 3 are provided in pivot holes provided at eccentric positions of a main bearing 6 as a suction side bearing member and a sub bearing 7 as a discharge side bearing member, respectively. 6a and 6b, and are rotatably supported.

Further, the outer peripheral portions of the main bearing 6 and the sub-bearing 7 are inserted into the openings at both ends of the cylinder 4, and these openings are hermetically closed. The main bearing 6 and the sub-bearing 7 are coupled and fixed to the inner wall of the sealed case 2.

A spiral groove 8 is provided on the outer periphery of the piston 5. The width of this groove 8 is set constant, and the depth direction coincides with the radial direction of the piston 5. and,
The pitch is formed to gradually become smaller from the suction side end to the discharge side end of the cylinder 4.

Blades 9 made of a synthetic resin material having appropriate flexibility, such as Teflon resin, are wound around the spiral grooves 8 so as to be protrusive and retractable, that is, to be able to move in and out.

Therefore, the inside of the cylinder 4 is partitioned by the blades 9 and arranged along the axial direction of the piston 5, and the volume becomes smaller as it goes from the middle part in the axial direction of the piston 5 to both ends. A plurality of crescent-shaped working chambers 10 are formed. In fact, the sum of the cross-sectional areas of the shaft portions 5a and 5b at both ends of the piston 5 is set to substantially match the cross-sectional area of the inner diameter of the cylinder 4.

A bearing inner closed space 1 is formed between the pivot holes 6a and 6b provided in the main bearing 6 and the sub-bearing 7, respectively, and the end surfaces 5a and 5b of the shaft portions at both ends of the piston 5 pivoted therein.
1a and 11b are formed.

A discharge pressure introduction passage 12 forming a discharge pressure introduction means is provided spanning the bearing inner space 11a of the main bearing 6 and the circumferential surface of the main bearing 6. Through this discharge pressure introduction passage 12, the bearing inner space 11a of the main bearing 6 and the inside of the sealed case 2 communicate with each other.

The shaft portion 5 on the bearing side of the secondary bearing 7 of the piston 5
A suction pressure introduction passage 13 that forms a suction pressure introduction means is provided from the b end face along this axial direction and across the working chamber 10 formed at the suction side end of the cylinder 4. This suction pressure introduction passage 13 allows the bearing internal space 11b of the sub-bearing 7 to
and the working chamber 10 at the suction side end communicate with each other.

Along the axial direction from the end surface on the pivot side of the main bearing 6, which is the end that pivots the one shaft portion 5a of the piston 5,
A suction conduit 14, which will be described later, is bored. The tip of this suction guide passage 14 opens at the suction side end within the cylinder 4 .

A suction pipe 15 is connected to one side of the sealed case 2 and communicates with an evaporator (not shown), which is an external device. The open end surface of this suction pipe 15 communicates with the suction conduit 14 via the sealed case 2.

On the other hand, a discharge hole 16 is provided at the discharge end of the cylinder 4, and the working chamber 10 at the discharge end communicates with the inside of the sealed case 2. In the figure of the sealed case 2, there is a discharge pipe 1 in the upper part that communicates with a condenser (not shown).
7 is connected.

A rotor 18 is provided on the peripheral wall of the cylinder 4, and a stator 19 is provided in the sealed case 2 with a gap on the outer peripheral surface of the rotor 18, thereby forming an electric motor section 20.

One end of the cylinder 4 and the opposing portion of the piston 5 are connected by a rotational force transmission mechanism 23 consisting of an engagement pin 21 and a locking groove 22. This rotational force transmission mechanism 23 and the electric motor section 20 connect the cylinder 4 and the piston 5.
A drive mechanism 24 is configured to rotate the two relatively and synchronously.

Next, the suction guide passage 14 provided in the main bearing 6 will be explained with reference to FIGS. 2(A) and 2(B). That is, the diameter Dφ of the peripheral portion of the main bearing 6 that closes the opening of the cylinder 4 and the diameter dφ of the pivot hole 6a that pivotally supports the shaft portion 5a of the piston 5 do not change.

In the remaining cross-sectional area, the suction passage 14 is
will be provided. This consists of a plurality of suction holes 25 provided along the axial direction of the main bearing 6. These plurality of suction holes 25 are set within a strength-permissible range and so that their total cross-sectional area becomes larger.

The main bearing 6 which is one end side of the suction hole 25
On the end surface of the sealed case 2 on the joining side, all the suction holes 2
A recessed part 26 in the shape of a long hole is provided so as to extend over the ends of the parts 5 and 5. The suction pipe 15 has a cross-sectional shape that faces part or all of the recessed portion 26.

[0040] Thus, the electric motor section 20 is energized to drive the cylinder 4 to rotate. As the cylinder 4 rotates, the cylinder 4 and the piston 5 rotate relatively and synchronously via the rotational force transmission mechanism 23.

The low-pressure refrigerant gas is guided from the suction pipe 15 through the sealed case 2 to the suction conduit 14 provided in the main bearing 6. That is, the refrigerant gas is guided along the plurality of suction holes 25, introduced into the working chamber 10 at the suction side end, and then gradually transferred toward the working chamber 10 at the discharge side end.

At this time, the suction holes 25... are connected to the main bearing 6.
Since the opening has a larger cross-sectional area within the range that is possible in terms of strength, a large amount of refrigerant gas can be conducted, and high suction efficiency can be ensured.

The working chamber 10 is set so that its volume gradually decreases from the suction side end to the discharge side end, so the refrigerant gas introduced is compressed while being sequentially transferred through the working chamber 10. be done.

When the refrigerant gas reaches the working chamber 10 at the discharge end, the pressure rises to a predetermined level and is discharged from the discharge hole 16 into the closed case 2 under high pressure. That is, the inside of the sealed case 2 is filled with high-pressure refrigerant gas.

[0045] This high-pressure refrigerant gas is led out from the discharge pipe 17 connected to the closed case 2, and led to the condenser communicating therewith. As a result, a sufficient amount of refrigerant gas is sucked in and compressed, ensuring high compression performance and sufficient refrigeration capacity.

On the other hand, a part of the low-pressure refrigerant gas guided from the suction holes 25 to the working chamber 10 at the suction side end is guided along the suction pressure introducing passage 13 provided in the piston 5, and is introduced into the sub-bearing 7. It fills the bearing inner space 11b.

A part of the refrigerant gas filling the sealed case 2 is guided along the discharge pressure introduction passage 12 provided in the main bearing 6, and fills the bearing inner space 11a of the main bearing 6. This is also because the mutual cross-sectional areas of the shaft portions 5a and 5b at both ends of the piston 5 and the inner diameter of the cylinder 4 are set, so that the thrust force accompanying the compression action is balanced, and no friction loss occurs between the piston 5 and the main bearing 6.

In the above embodiment, the suction passage 14 provided in the main bearing 6 is formed of a plurality of suction holes 25, but the invention is not limited to this, and for example, as shown in FIG. Good too.

That is, the suction guide passage 14A provided in the main bearing 6 is a long hole-shaped hole with a curved cross section that opens within a strength-permissible range in the remaining cross section where the pivot hole 6a is provided. Formed from a long suction hole.

Therefore, since the suction conduit 14A is opened to the main bearing 6 with a larger cross-sectional area within the range that is possible in terms of strength, a large amount of refrigerant gas can be conducted, and high suction efficiency is ensured. What is done is the same as in the above embodiment.

Furthermore, in such a fluid compressor, as shown in FIGS. 4 and 5, the diameter of the discharge hole 16a provided at the discharge side end of the cylinder 4 is enlarged, and a stopper discharge port body 30 is installed here. Insert. This stopper discharge port body 30 has a distal end protruding into the cylinder 4 and a piston 5.
It is inserted into a concave portion 31a provided on the circumferential surface of.

On the other hand, some models are equipped with an Oldham ring mechanism 32 as a rotational force transmission mechanism provided at the suction side end of the cylinder 4, and a blade stopper 33 is further provided integrally with this Oldham ring mechanism 32. There is something. This blade stopper 33 has a distal end protruding into the cylinder 4 and is inserted into a concave portion 34 a provided on the circumferential surface of the piston 5 .

That is, the piston 5 due to the compression action
Due to the relative movement between the blade 9 and the blade 9, a thrust force acts on the blade 9 to move the blade 9 toward the discharge side or the suction side.

Under the influence of this thrust force, even if the blade 9 moves along the spiral groove 8 and one of its ends attempts to contact the end of the groove 8, the blade stopper 30 or The stopper discharge port body 33 is the blade 9
This positioning is achieved by contacting the ends, thus preventing wear on both ends of the blade 9.

Further, a recess 31b is provided at a position symmetrical to the recess 31a at the discharge side end with respect to the horizontal center axis XX. As shown in FIG. 6(A), these are the central axis
-X and the central axis Y-Y, the positions and shapes are completely symmetrical.

As shown in FIG. 6(B), the concave portions 34a at the suction side end are arranged symmetrically with respect to the central axis XX and shifted in opposite directions relative to the central axis Y-Y. It is provided in a different shape.

Therefore, the concave portion 31 into which the stopper discharge port body 30 or the tip of the blade stopper 33 enters is formed.
By providing other concave portions 31a and 34a at positions symmetrical to a and 34a, the center of gravity of the rotating piston 5 can be brought closer to this central axis XX, and the inertial force (centrifugal force) can be reduced. the result,
In such a compressor in which the rotating system only rotates on its own axis, vibrations during operation and during startup and shutdown are significantly reduced. Further, the fluid compressor of the present invention is not limited to use in refrigeration cycles, but can also be applied to compressors that compress other types of fluids to be compressed.

[0058]

As explained above, according to the present invention, the suction conduit passage provided in the suction side bearing member and guiding the compressed fluid from the outside of the cylinder to the working chamber is connected to the remaining cross section of the rotating body pivot hole. A plurality of suction holes that open within a range that is allowable for strength, or a long suction hole that has a deformed cross section that opens within a range that is allowable for strength in the remaining cross section of the rotating body pivot hole. Therefore, without changing the diameter of the bearing that supports the cylinder and piston, and the diameter of the pivot hole, we expanded the suction hole diameter as much as possible to ensure sufficient suction volume, and by improving suction efficiency, we increased the refrigeration capacity and compression. This has the effect of improving performance.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of a fluid compressor showing one embodiment of the present invention.

FIG. 2 (A) is a front view of the main bearing of the same embodiment. (B) is a longitudinal cross-sectional view of the main bearing of the same example.

FIG. 3 is a front view of the main bearing of another embodiment.

FIG. 4 is a partial vertical sectional view of a compression mechanism section of another embodiment.

FIG. 5 is a side view of a piston in another embodiment.

FIG. 6(A) is a longitudinal cross-sectional view of another embodiment taken along line 5A-A in FIG. (B) is a longitudinal sectional view taken along the line B-B in FIG. 5 of another embodiment.

FIG. 7 is a longitudinal sectional view of a conventional main bearing.

FIG. 8 is a front view of the main bearing of the conventional example.

[Explanation of symbols]

4...Cylinder, 6...Main bearing, 7...Subbearing, 6a, 6b...
Pivot hole, 5a, 5b...shaft portion, 5...rotating body (piston),
8...Groove, 10...Working chamber, 9...Blade, 24...Drive mechanism, 14...Suction guide path, 25...Suction hole, 14A...Suction long hole.

Claims (2)

[Claims] Claims: 1. A cylindrical cylinder; two bearing members rotatably supporting both ends of the cylinder and closing both ends of the cylinder; carefully placed,
A cylindrical rotating body whose both end shaft portions are supported by pivot holes provided at eccentric positions of both bearing members, and a cylindrical rotating body that is provided on the outer periphery of the rotating body and gradually decreases in size from the suction side end to the discharge side end of the cylinder. A spiral groove formed at a pitch of and a blade that divides a space between the cylinder and the outer circumferential surface of the rotating body into a plurality of working chambers, and a blade that rotates the cylinder and the rotating body relatively to absorb the compressed fluid that flows into the working chamber from the suction side end of the cylinder. In a fluid compressor, the fluid compressor is equipped with a driving means for sequentially transferring and compressing the fluid to a working chamber at the discharge side end of the cylinder, which is provided on the suction side bearing member and introduces the compressed fluid from the outside of the cylinder into the working chamber at the suction side end. 1. A fluid compressor comprising a suction conduit and a plurality of suction holes constituting the suction conduit and opening within a strength-permissible range in the remaining cross section of the rotating body pivot hole. 2. A cylindrical cylinder; two bearing members rotatably supporting both ends of the cylinder and closing both ends of the cylinder; carefully placed,
A cylindrical rotating body whose both end shaft portions are supported by pivot holes provided at eccentric positions of both bearing members, and a cylindrical rotating body that is provided on the outer periphery of the rotating body and gradually decreases in size from the suction side end to the discharge side end of the cylinder. A spiral groove formed at a pitch of and a blade that divides a space between the cylinder and the outer circumferential surface of the rotating body into a plurality of working chambers, and a blade that rotates the cylinder and the rotating body relatively to absorb the compressed fluid that flows into the working chamber from the suction side end of the cylinder. In a fluid compressor, the fluid compressor is equipped with a driving means for sequentially transferring and compressing the fluid to a working chamber at the discharge side end of the cylinder, which is provided on the suction side bearing member and introduces the compressed fluid from the outside of the cylinder into the working chamber at the suction side end. A suction conduit, and an elongated suction hole whose cross section is deformed within a strength-permissible range and which forms the suction conduit and opens within the strength-permissible range in the remaining cross section of the rotating body pivot hole. Characteristic fluid compressor.