JPS5950879B2 - compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary compressor particularly suitable for compressing refrigerant in a vehicle air conditioning system.

In the conventional compressor, as shown in FIG. 5, the suction port 44 and the discharge port 48 are provided at fixed positions in the housing 45, so when the rotor 46 rotates, one long diameter portion 46a is connected to the vane 47B.
The refrigerant sucked into the working chamber P from the time when the suction operation is completed (solid line position in the figure) until the long diameter portion 46a of the rotor 46 closes the suction port 44
There was a defect in that part of the water flowed back from No. 4, reducing the volumetric efficiency.

Furthermore, a conventional compressor disclosed in US Pat. No. 3,314,368 has been proposed.

A vane is installed in a cylindrical cylinder chamber formed in the housing, and a suction chamber for the compressed fluid is located in the rotor, which is housed in the cylinder chamber and has a long diameter portion that airtightly corresponds to the inner peripheral surface of the chamber. is provided on the outer periphery of the rotor so as to be located between the vane position on the leading side in the rotational direction of the rotor and several diameter parts with respect to the working chamber where the rotor rotates and the suction volume of the compressed fluid is maximized. This is a compressor with a suction port at the top, but since the number of vanes is the same as the length of the long diameter section, after the working chamber reaches its maximum suction volume, the flow will flow backwards until the suction port passes through the vane, resulting in low volumetric efficiency. There was a defect that led to a decline in

In addition, since the above compressor had a structure in which the long diameter part of the rotor was in local contact with the inner circumferential surface of the cylinder chamber, there was a problem with the sealing between the long diameter part and the inner circumferential surface of the cylinder chamber. There was a drawback in that the compressed fluid flows back into the chamber, which also reduces volumetric efficiency.

The present invention has been made to eliminate the above-mentioned defects, and its purpose is to prevent part of the fluid to be compressed from flowing back into the suction chamber during the compression stroke, and to improve sealing performance at the long diameter portion of the rotor. An object of the present invention is to provide a compressor that can improve volumetric efficiency.

In order to achieve the above-mentioned object, the present invention includes vanes and a discharge port in a housing having a cylindrical cylinder chamber inside.
A suction chamber for the fluid to be compressed is provided in each rotor, which is installed in the same cylinder chamber and has a long diameter portion that airtightly corresponds to the inner circumferential surface of the same chamber, and the long diameter portion of the rotor is arranged so that the long diameter portion of the rotor is approximately equal to the curvature of the inner circumferential surface of the cylinder chamber. The discharge ports and vanes are formed in an arcuate surface having the same curvature, the number of the discharge ports and the vanes is greater than or equal to the number of the long diameter portions plus 1, and the discharge ports and the vanes are arranged adjacent to each other in this order from the rotational direction of the rotor, and The rotor rotates and, after passing the vane of the long diameter portion, a suction port is provided in a portion of the rotor located between the vane of the long diameter portion and the rear end of the arcuate surface of the long diameter portion.

Hereinafter, an embodiment embodying the present invention will be described with reference to FIGS. 1 to 3. In the drawings, 1 is a thick-walled short cylindrical housing, and a true cylindrical cylinder chamber C is formed in the hollow part of the housing. has been done.

2 and 3 are six bolts 5 (1
The sub-housings on the suction side and the discharge side are tightened and fixed by screws (only one part is shown in the figure), and as shown in FIG. A pipe (not shown) is connected to the through hole 7 provided on the outer periphery of the sub-housing 3 on the discharge side.
(not shown) are connected.

Reference numeral 8.9 denotes side plates on the suction side and discharge side that are interposed between the housing 1 and the subhousing 2.3 and form both side wall surfaces of the cylindrical cylinder chamber C, and the side plate 8 on the suction side. and the sub-housing 2 form a sub-suction chamber S', and the discharge-side side plate 9 and the sub-housing 3 form a sub-discharge chamber D'.

Reference numeral 10 denotes a rotating shaft which is rotatably supported at the center of the pair of side plates 8 and 9 via bearings 11 and 12, and whose suction side end passes through the center of the sub-housing 2. A sealing member 13 is inserted between the sub-housing 2 and the rotating shaft 10 to lead out.

Reference numeral 14 denotes an elliptical cylindrical rotor fixed on the rotating shaft 10 in the cylinder chamber C, and the rotational axis O of the rotating shaft 10 is
Radius R from (aligned with the center of cylinder chamber C)
outer peripheral surfaces 15a of the pair of long diameter portions 15, 16 where
As shown in FIG. 3, 16a is the inner circumferential surface Ca of the cylinder chamber C. The outer circumferential surface 14 of the rotor 14 is placed as close as possible to the circumferential surfaces 1a, lb, and IC).
A and the inner circumferential surface Ca of the cylinder chamber C, there are two working chambers that move continuously in the rotational direction (this chamber is divided into working chambers P0 to P3 by three vanes 24A to 24C, which will be described later). At the same time, both end surfaces 14b of the rotor 14 are formed.
are brought as close as possible to the inner surfaces 8a and ga of the side plates 8 and 9, respectively, and furthermore, a seal groove 17 is formed in the entire circumference of the end surface 14b of the rotor 14, and a seal ring 18 is fitted into the side plate 8. , 9 are in contact with the inner surfaces 8a, 9a of the inner surfaces 8a, 9a.

In addition, the long diameter portion T5 of the rotor 14, 16 outer peripheral surface 15a
, 16a is the inner peripheral surface C of the cylinder chamber C as shown in FIG.
It is formed into an arc shape that is approximately the same as the curvature of a, and its length is approximately 1
(0 to 20 mm, and the forming angle α of each outer circumferential surface 15a, 16a with respect to the rotational axis O is approximately 10 to 20 degrees in this embodiment) to improve the sealing performance with the inner circumferential surface Ca of the cylinder chamber C. There is.

S is a suction chamber formed by the elliptical inner circumferential surface 14C of the rotor 14 and the side plates 8 and 9, and in this embodiment, a total of eight chambers are formed transparently near the center of the side plate 8 on the suction side. It communicates with the sub-suction chamber S' in the sub-housing 2 through an inlet 19 (only two locations are shown in FIG. 2).

21 is attached to the outer circumferential portion of the rotor 14, as will be described later.
In the state shown in FIG. 1, when the suction volume of the working chamber P2 corresponding to the cylinder inner peripheral surface 1b reaches its maximum, the vane 24 on the leading side in the rotor rotational direction with respect to the working chamber P2
In this embodiment, four first suction ports are transparently provided between the position C and the outer circumferential surface 15a of several long diameter portions 15, and the first suction ports are located between the suction chamber S in the rotor 14 and the Working chamber P
2, so that refrigerant can be supplied from the suction chamber S to the working chamber P2.

Numeral 22 designates four second suction ports in this embodiment, which are transparently provided in the same manner as the first suction ports 21 so as to be located immediately behind the outer peripheral surface 16a of the long diameter portion 16 with respect to the outer peripheral portion of the rotor 14,
The suction chamber S of the rotor 14 and the working chamber P1 are communicated with each other, and refrigerant can be supplied from the suction chamber S to the working chamber P1.

23A to 23C are three vane grooves 24A to 24 recessed in the inner circumferential surface Ca of the cylinder chamber C so as to be parallel to the rotational axis O of the rotor 14 and every 120 degrees;
C denotes three vanes that are tightly fitted into the vane grooves 23A to 23C so as to be able to reciprocate in the radial direction, and the arcuate end surfaces of the vanes 24A to 24C can be slidably contacted with the outer circumferential surface 14a of the rotor 14. be.

The three vanes 24A to 24C are urged to come into contact with the circumferential surface of the rotor by appropriate pressing force using discharge pressure or by the force of a spring.

The first suction port 21 is located when the rotor 14 rotates and the suction volume of refrigerant into the working chamber is maximized, for example, as shown in FIG. 1, the short diameter portion of the rotor 14 is located at the top vane 24A Working chamber P2 between lower vanes 24B and 24C
is the maximum suction volume, and with respect to the working chamber P2, it is located between the position of the vane 24C on the leading side in the rotor rotational direction and the long diameter portion 15 of several rotors 14 (see Fig. 3). .

This relationship holds true for the second suction port 22 as well.

D1 to D3 are three discharge chambers that open outward with respect to the outer peripheral surface of the housing 1 and are recessed immediately after the vanes 24A to 24C, that is, in the counterclockwise direction in FIG. The open ends of the chambers D1 to D3 are sealed with lids 25.

26A to 26C are discharge chambers D1 to D3 for the housing 1.
and the working chambers P1 to P3, respectively, and are transparently provided so as to be located immediately after each of the vane grooves 23A to 23B, and the discharge ports are arranged to communicate with the working chambers P1 to P3, respectively, and are located immediately after the respective vane grooves 23A to 23B. Refrigerant can be supplied to the discharge chambers D1 to D3.

27A to 27C are bolts 28 so as to open and close the respective discharge ports 26A to 26C with respect to the bottom surfaces of the respective discharge chambers D1 to D3.
A check valve made of a thin plate attached to each check valve 27A~
The rotation range of each of the check valves 28A to 28C is restricted by a stopper 29 attached to the back side of the check valve 27C with a bolt 28.

Reference numeral 30 indicates each vane groove 23A to 23 for the housing 1.
C and each of the discharge chambers D1 to D3 are transparent passages that are arranged so as to communicate with each other, and guide the refrigerant pressurized into the discharge chambers D1 to D3 to the vane grooves 23A to 23C.
Pressure is applied to the inner end surfaces of the vanes 24A to 24C in the vanes 24A to 23C, and the vanes 24A to 24C are pressed against the outer peripheral surface 14 of the rotor 14.
It is designed so that it can be brought into pressure contact with a.

31 is the discharge chamber D1 to the housing 1 and the side plate 9.
A transparent passageway is provided so as to communicate between D3 and the sub-discharge chamber D' provided in the sub-housing 3 on the discharge side.
’.

As shown in FIG. 2, 32 is a small chamber shallowly recessed in the inner surface of the sub-housing 3 on the discharge side corresponding to the bearing 12, and 33 is a small chamber 32 and the working chamber P with respect to the sub-housing 3 and the side plate 9. It is a thin passage provided transparently to communicate with the air conditioner, and its opening end 33a on the cylinder chamber C side is located just before the upper vane 24A (clockwise side in the figure) as shown in FIG. Outer peripheral surface 1 of rotor 14
It is located slightly outside the short diameter portion of 4a.

Next, the operation of the compressor constructed as described above will be explained.

Now, in FIG. 1, the rotor 14 is rotated clockwise in the figure, and corresponds to the vane 24A with one short diameter portion located at the top, and three vanes 24A to 24C, and each vane 24A to 24C.
Three working chambers P formed by the three cylinder indoor circumferential surfaces 1a to 1C between 4C and the outer circumferential surface 14a of the rotor 14.
Among 1 to P3, the working chamber P2 corresponding to the inner circumferential surface 1b has the maximum suction volume, while the working chamber 2 corresponding to the inner circumferential surfaces 1a and lc has the maximum suction volume.
two working chambers P1. P3 is the long diameter part 16°15 of the rotor 14
This shows a point in time during the suction and compression operation of the refrigerant, which is divided into two chambers Ps and Pd, respectively.

In this state, a chamber Ps is formed at the rear in the rotational direction of the rotor 14 with respect to the long diameter portion 15.16 of the rotor 14.
is expanded in volume by the rotation of the rotor 14 and becomes negative pressure, and the refrigerant in the suction chamber S in the rotor 14 is sucked into the chamber Ps through the first and second suction ports 21 and 22, and at the same time The volume of the chamber Pd decreases due to the rotation of the rotor 14, and the pressure becomes high. The refrigerant sucked into the chamber Pd is compressed and pushed out from the discharge ports 26A and 26B, and becomes the discharge chamber D.
1. Transferred to D2.

Then, the rotor 14 rotates and the long diameter portion 16 becomes the vane 24B.
Immediately after the second suction port 22 passes over the vane 24B, the suction operation of the refrigerant into the working chamber P1 is stopped, and the working chamber P1 becomes one chamber with the maximum suction volume, and the working chamber P
2 is divided into two chambers by the long diameter portion 16 for suction and compression, and furthermore, immediately after the long diameter portion 15 passes the vane 24A and the first suction port 21 crosses the same vane 24A, it flows into the working chamber P3. The suction operation of the refrigerant is stopped, and the working chamber P3 becomes one chamber with the maximum suction volume.The working chamber P1 is again divided into two chambers by the long diameter portion 15, and suction and compression operations are performed.

Here, the rear end E of the long diameter portion 15 (outer peripheral surface 15a) of the rotor 14 is in contact with the vane 24C (although not shown, the compression operation of the working chamber P2 is completed, and the compression operation of the working chamber P3 is started). 1 and 3, the operation until the rear end E of the long diameter portion 15 is separated from the vane 24C by a certain distance and the working chamber P2 reaches its maximum suction volume will be described.

Now, when the rear end E of the long diameter part of the rotor is slightly separated from the vane 24C, the working chamber P3 is divided into two chambers Ps and Pd as described above.
Refrigerant is sucked into the chamber Ps from the first suction port 21a on the leading side in the rotor rotation direction, while refrigerant is sucked into the working chamber P2 from the first suction port 21b on the rear side in the rotor rotation direction.

In this embodiment, as shown in FIG. 3, the preceding first suction port 21a is provided slightly rearward from the rear end E of the long diameter portion 15, but if this position is provided immediately after the rear end E of the long diameter portion, Since the suction action starts immediately after the rear end E of the long diameter portion passes the vane 24C, high suction efficiency can be obtained.

Further, when the rotor rotates and the first suction port 21b on the rear side passes the vane 24C, the suction operation of the refrigerant into the working chamber P2 is stopped, and the suction operation of the refrigerant into the chamber Ps of the working chamber P3 is stopped at the first suction port 21b on the rear side. This is also done through the mouth 21b.

In this embodiment, as shown in FIGS. 1 and 3, the working chamber P
2 reaches the maximum suction volume, the subsequent first suction port 21
However, if the first suction port 21b is provided just in front of the vane 24C in the same state, the first suction port 21b will be at a position slightly advanced from the vane 24C while the suction operation continues in the working chamber P2. The suction operation from one suction port 21 is continuously performed, and high suction efficiency can be obtained.

Now, in the embodiment of the present invention, three vanes 24A to 24C and discharge ports 26A to 26C are provided on the housing side, and a suction chamber S is provided in the rotor 14.
First and second suction ports 21 and 22 are provided on the outer periphery of the rotor, and the position of the vane on the leading side in the rotational direction of the rotor and several long diameter portions are Since the first and second suction ports 21.22 are provided between the suction ports 21 and 22, it is possible to prevent the refrigerant from flowing back into the suction chamber S from the suction ports 21.22, thereby increasing the volumetric efficiency.

In other words, when the working chamber reaches its maximum suction volume and the compression operation is started by the following long diameter section, the working chamber and the suction port are already blocked off by the vanes, which prevents the refrigerant from flowing backwards and reduces the volume. It is possible to create something that increases efficiency.

By the way, when the first and second suction ports 21.22 are provided immediately after the long diameter portion 15.16 (rear end E) of the rotor 14, the suction action in the working chamber is started and at the same time the suction from the suction ports is Regarding the working chamber when suction starts and the suction volume reaches its maximum, if the suction port is provided just before the position of the vane on the leading side in the rotational direction of the rotor, the suction volume in the working chamber will continue until the suction action in the working chamber ends. Inhalation is performed continuously from the suction port, and the rotor 1 also combines these advantages.
4 is rotated and the suction volume of the refrigerant sucked into the working chamber is maximized, and with respect to the working chamber, a suction port is provided extending from the position of the vane on the leading side in the rotational direction of the rotor to several long diameter parts of the rotor. If the rotor 14
is rotated so that the long diameter portions 15 and 16 become the vanes 24A to 24C.
The refrigerant can be sucked from the very beginning into the chamber Ps that begins to form immediately after passing through the suction port, and the refrigerant flows from the same suction port until the suction volume reaches the maximum. is blocked by the vane.

Therefore, the suction efficiency of the refrigerant sucked into the working chamber can be further improved.

If the suction volume of the refrigerant sucked into the working chamber through the first and second suction ports 21 and 22 is at its maximum, the long diameter of the rotor on the same side as the position of the vane on the leading side in the rotor rotational direction with respect to the working chamber. If no refrigerant is installed between the chamber Ps and the chamber Ps, the refrigerant may not be sucked into the chamber Ps from the beginning, or the suction port may be cut off before the volume reaches its maximum, resulting in a large negative pressure in the chamber Ps. , a large load is applied to the rotor, but this defect can be overcome in the embodiment described above.

One end of the suction port begins at the major diameter section, or if the major diameter section has arcuate outer peripheral surfaces 15a, 15a as shown in FIG. 3, it begins at the rear end E of the major diameter section, and the other end The suction efficiency can be maximized by locating the working chamber at a position immediately in front of the vane on the leading side in the rotational direction of the rotor, when the volume is at its maximum. But it can also be an intermittent hole.

Furthermore, in the embodiment described above, the width of the suction port is made larger than the width of the vane, so that all of the suction ports are not blocked at once, and therefore, the suction flow is smooth without being interrupted.

Note that the present invention can also be embodied in the following embodiments.

(a) As shown in FIG. 4, the rotor 14 is formed into a triangular cylinder shape with rounded corners so that the three major diameter portions 38 to 40 correspond to the inner circumferential surface Ca of the cylinder chamber C in an airtight manner, and each major diameter Immediately after portions 38 to 40 are first to third inlet ports 41, respectively.
43 are provided, and four vanes 24A to 24D are provided at 90 degree intervals on the inner circumferential surface Ca of the cylinder chamber C, and each vane 2
Discharge ports 26A to 26D are provided immediately after ports 4A to 24D, respectively.

Further, the shape of the rotor 14 is formed into a polygonal cylinder shape or more than a square cylinder shape.

In this case as well, the suction ports are provided corresponding to the long diameter portions of the rotor, and the number of discharge ports and vanes is set to be equal to or greater than the number of the long diameter portions of the rotor plus one.

(b) In each of the above embodiments, the inlet ports 21, 22°41
- 430 The number may be increased or decreased, an appropriate number may be arranged at equal intervals in the axial direction of the rotor 14, or the angle of inclination with respect to the outer peripheral surface of the rotor 14 may be formed in a diagonal shape facing rearward in the rotational direction of the rotor 14.

(c) In the above embodiment, the compressor was described as a compressor for refrigerant gas for vehicle air conditioning, but it can also compress gases such as various gases and liquids such as oil.

As described in detail above, the present invention prevents a part of the fluid to be compressed from flowing back into the suction chamber during the compression process, improves the sealing performance at the long diameter part of the rotor, and improves the volume compared to conventional compressors. This has the effect of improving efficiency.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing one embodiment of the present invention, FIG. 2 is a cross-sectional view taken along the line X-X in FIG. 1, FIG. 3 is an enlarged sectional view of the vicinity of the long diameter portion of the rotor, and FIG. FIG. 5 is a cross-sectional view showing another embodiment of the present invention, and FIG. 5 is a cross-sectional view showing an example of a conventional compressor. Housing...1, Side plate...8,9,
Rotor...14, long diameter part...15,1
6.38-40, 1st-3rd inlet...21.
41. 22. 42. 43, Vane...
24A-24D, rooms...Ps. d0

Claims (1)

[Scope of Claims] 1. A housing having a cylindrical cylinder chamber therein is provided with a vane and a discharge port, and a rotor is installed in the cylinder chamber and has a long diameter portion that airtightly corresponds to the inner circumferential surface of the chamber. Suction chambers for the fluid to be compressed are provided inside, and the number of the discharge ports and vanes is greater than or equal to the number of long diameter portions plus 1, and the discharge ports and vanes are arranged adjacent to each other in the order of rotation of the rotor. In addition, the long diameter portion of the rotor is formed into an arcuate surface having approximately the same curvature as the curvature of the circumferential surface of the cylinder chamber, and when the rotor rotates and the vane passes through the long diameter portion, the vane and the arcuate surface of the long diameter portion are A compressor characterized in that a suction port is provided in a rotor portion located between the rear end and the rotor. 2. The compressor according to claim 1, wherein the suction port is provided continuously or intermittently from the vane position after the vane passes through the long diameter portion to the rear end of several of the arcuate surfaces. . 3. The compressor according to claim 1, wherein the suction port is provided immediately after the rear end of the circular arc surface of the long diameter portion of the rotor. 4. The vanes are provided at a total of three locations every 120 degrees, the rotor is formed in an elliptical cylindrical shape, and the suction ports are provided at two locations corresponding to each major diameter portion. compressor. 5. The vanes are provided at a total of four locations every 90 degrees, the rotor is formed into a substantially triangular cylinder shape, and the suction ports are provided at three locations corresponding to each major diameter portion. compressor.