JPH03271590A - Rotary compressor - Google Patents

Abstract

PURPOSE:To reduce the leakage loss, and improve the efficiency of a compressor by reducing a clearance, between a reciprocating plate and a vane channel, as a flow passage of which leakage quantity is large at some times of a leakage quantity through a clearance between the reciprocating plate and both bearings, and reducing a leakage quantity of the high pressure refrigerant to a suction chamber and a compress space through that clearance. CONSTITUTION:The total force G of the pressing force of a spring 23, which is provided in the back of a second vane 21, working in the direction of a roller 5 and the pressure of the high pressure refrigerant discharged into a closed casing works from the back side of the second vane 21 to the direction of the roller 5. When leakage quantities of the high pressure refrigerant from the back sides of both vanes 20, 21 to a suction chamber 13a and a compress space 13b are compaired with each other, sectional area of a clearance of the latter is larger than that of the former at some times, and a leakage quantity of the high pressure refrigerant of the latter is therefore larger than that of the former at some times. Consequently, when a total leakage quantity from both the clearances between a side face 20b of a first vane 20 and a side face 4b of a vane channel 4a, and between a side face 21b of the second vane 21 and a side face 4c of the vane channel 4a is considered, the total leakage quantity can be reduced remarkably by reducing the space of the latter, of which leakage quantity is larger than that of the former at some times, than reducing the space of the former.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and particularly relates to reducing leakage loss.

Prior Art A conventional configuration will be explained with reference to FIGS. 4, 5, and 6. Note that the arrows in FIG. 6 indicate leakage of high-pressure refrigerant, and the arrows in FIG. 5 indicate acting forces.

1 is the sealed casing, 2 is the electric motor part, and shaft 3
via cylinder 4. roller 6, first reciprocating plate 6a, second
Reciprocating plate eb, main bearing7. It is connected to a mechanical part main body 9 constituted by a sub-bearing 8.

The shaft 3 includes a main shaft 3a, a sub-shaft 3b, and a crank 3C. The twisted first reciprocating plate 6a and second reciprocating plate 6b are stored adjacent to the vane groove 10 provided in the cylinder 4. 11 is a spring provided on the back surface of the second reciprocating plate 6b. 12 is an oil supply mechanism connected to the shaft 3. 13a is a suction chamber, and 13b is a compression chamber. 14
is the suction pipe, and the secondary bearing 8. It communicates with the suction chamber 13a via the suction hole 15 of the cylinder 4. 16 communicates with the inside of the sealed casing 1 via a discharge valve 17 which is a discharge hole. Reference numeral 18 denotes a discharge pipe, which opens into the sealed casing 1. 19 is lubricating oil.

Next, the compression mechanism of the rotary compressor will be explained.

Refrigerant gas from the cooling system (not shown) is supplied to the suction pipe 1
4. A suction chamber 13a inside the cylinder 4 led from the suction hole 15
leading to. The refrigerant gas that has reached the suction chamber 13 & is transferred to the shaft 3
The roller 5 rotatably fitted to the crank 3C and the first
The electric motor section 2 is located in the compression chamber 13b partitioned by the reciprocating plate 6a.
It is gradually compressed by the rotational movement of the shaft 3 as the shaft 3 rotates. The compressed refrigerant gas is discharged through the discharge hole 16. Once discharged into the sealed casing 1 via the discharge valve 17, the discharge pipe 1
8 to the cooling system.

Further, lubricating oil 19 is supplied by the oil supply mechanism 12 to the sliding parts such as the shaft 3, the main bearing, and the sub-bearing 8.

Here, the mating surfaces of the first reciprocating plate 6a and the second reciprocating plate 6b have the same plate thickness and are inclined with respect to the direction of reciprocating movement. Therefore, the total force F of the pressing force by the spring 11 provided on the back surface of the second reciprocating plate 6b and the pressure of the high-pressure refrigerant discharged into the sealed casing 1 acts on the back and surface of the second reciprocating plate 6b. ing. Therefore, a force F1 acts on the mating surface 6d of the second reciprocating plate 6b in a direction perpendicular to the mating surface 6d. A force F in the direction of reciprocating movement and a force F2 in the axial direction and perpendicular to the force F act on the second reciprocating plate 6b as a component of the force F1. The second reciprocating plate 6b is then pressed against the main bearing side by the force F2. Further, a reaction force also acts on the first reciprocating plate 6a, and the first reciprocating plate 6a
is pressed against the secondary bearing 8 side. Therefore, the first reciprocating plate 6
The gap between the end surface 6e of a and the sub-bearing 8 and the gap between the end surface 6f of the second reciprocating plate b and the main bearing 7 become smaller.

Therefore, even if the gap is larger than necessary due to the machining accuracy of the vane groove 4a, the cylinder 4, etc. or the assembly accuracy, the gap becomes smaller during operation of the compressor as described above. Therefore, the high pressure refrigerant inside the sealed casing 1 is
, ef and secondary bearing 8. Suction chamber 1 through the gap between main bearings 7
3a and the compression chamber 13b was reduced, resulting in an effect that leakage loss could be reduced.

For example, it is shown in Japanese Utility Model Application Publication No. 63-12685.

Problems to be Solved by the Invention However, with the above configuration, the amount of high-pressure refrigerant leaking into the suction chamber and compression chamber through the gap between the first and second reciprocating plates, the main bearing, and the sub-bearing is reduced. The first thing that can be done is
Also, the amount of leakage through the gap between the side surface of the second reciprocating plate and the vane groove cannot be reduced.

Generally, the thickness of the reciprocating plate is smaller than the height of the reciprocating plate, so when comparing the amount of leakage in the gap between the reciprocating plate and both bearings and the gap between the reciprocating plate and the vane groove, the latter is more is several times more.

Therefore, due to the machining accuracy of the reciprocating plate and the vane groove of the cylinder, and the assembly accuracy, when assembling the compressor, the gap between the reciprocating plate and the vane groove of the cylinder is larger than the minimum required size for sealing. There was a problem in that a large amount of high-pressure refrigerant leaked into the suction chamber and compression chamber through this gap, resulting in large leakage losses. In addition, when considering the total amount of leakage from both the gap between the reciprocating plate and both bearings and the gap between the reciprocating plate and the vane groove, reducing the former, which has a small amount of leakage to begin with, is insufficiently effective. However, the problem was that it was not possible to improve efficiency at all.

Furthermore, since the gap between the end face of the first reciprocating plate and both bearings is biased toward the main bearing, there is also the problem that the amount of refrigerant leaking from the compression chamber to the suction chamber increases through this gap.

The present invention solves the above-mentioned drawbacks of the conventional example, and uses a simple mechanism to improve the leakage between the reciprocating plate and the vane groove, which is a flow path where leakage is several times larger than the amount of leakage through the gap between the reciprocating plate and both bearings. The objective is to reduce the amount of high-pressure refrigerant leaking into the suction chamber and compression chamber through this gap, thereby reducing leakage loss and improving compressor efficiency.

Means for Solving the Problems The present invention provides a cylinder, a main bearing and a sub-bearing fixed to both ends of the cylinder, a shaft having a crank partially housed in the main bearing and the sub-bearing, and a shaft that is rotated by the crank. A freely housed roller, a first vane that slides back and forth in a vane groove provided in the cylinder, and whose tip comes into contact with the roller, and a second vane whose tip does not come into contact with the roller. A first vane and a second vane are arranged in parallel, and the contact surfaces of both vanes are provided with different plate thicknesses so as to be inclined with respect to the direction of reciprocating movement, and the thicker side of the first vane is is the side that comes into contact with the roller, and a spring is provided on the back surface of the second vane to urge the second vane toward the roller.

Function: According to the above-described configuration, the present invention applies a force G, which is the sum of the pressing force by the spring provided on the back surface of the second vane and the pressure of the high-pressure refrigerant discharged into the sealed casing, to the back surface of the second vane. It's working. Therefore, force G1 acts on the inclined contact surface of the second vane in a direction perpendicular to the contact surface. A force G in the reciprocating direction and a force G2 in the axial direction and perpendicular to the force G act on the second vane as components of the force G1. Therefore, the second vane is pressed against the side surface of the vane groove. A reaction force also acts on the first vane, and the first vane is pressed against the side surface of the first vane groove. Therefore, both the gap between the side surface of the first vane and the side surface of the vane groove and the gap between the side surface of the second vane and the side surface of the vane groove become narrow.

Therefore, the gap between the end surfaces of the first and second vanes and both bearings is several times larger than that between the two side surfaces of the first and second vanes, which are flow paths through which the high-pressure refrigerant in the sealed casing leaks into the suction chamber and the compression chamber. The gap between grooves can be made smaller. Therefore, the amount of high-pressure refrigerant leaking into the suction chamber and compression chamber is reduced, and leakage loss can be reduced.

EXAMPLE An example of the present invention will be described below with reference to FIGS. 1, 2, and 3. Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted. Furthermore, the arrows in the figure indicate leaks of high-pressure refrigerant.

4a is a vane groove; 20 is a first groove whose tip is in contact with roller 5;
Vane, 21 is the second vane, 23 is the second vane 2
This is a spring provided on the back of 1.

Further, 20a and 21a are first and second vanes 20 provided with different plate thicknesses so as to be inclined with respect to the direction of reciprocating movement.
．． 21 contact surfaces, 20b and 21b are the side surfaces 20C and 21 of the first and second vanes 20C920d are the end surfaces of the first vane,
21C, 2od is the end face of the second vane 21. Furthermore, 4cl and 4c are the side surfaces of the vane groove 4a, and are respectively the side surface 20b of the first vane 2° and the side surface 2 of the second vane 21.
It faces 1b.

In the above configuration, the force acting on the second vane 21 will be explained. The total force G of the pressing force acting in the direction of the roller 5 by the spring 23 provided on the back surface of the second vane 21 and the pressure of the high-pressure refrigerant discharged into the sealed casing 1 is applied to the back surface of the second vane 21. It acts in the direction of the roller 6 from there. A contact surface 20a between the first vane 20 and the second vane 21.

Since the plate 21a is provided with a different thickness so as to be inclined with respect to the direction of reciprocating movement, a force G1 acts on the contact surface 21b of the second bee 721 in a direction perpendicular to the contact surface 21b. As components of the force G1, a force G in the reciprocating direction and a force G2 in the axial direction and perpendicular to the force G act. The force acting on the enclosed first vane 2o is:
Force G acting on the second vane 21, G1. Each reaction force of G2 will act. Both pages 720°21
The first page 720 is
and the second vane 21 are respectively attached to the side surface 4 of the vane groove 4a.
It will be pressed against b and 4C sides.

Therefore, the upper and lower end surfaces 20c and 20d of the first bay 720 and the upper and lower end surfaces 21c and 21d of the second page 721.

The gap between both bearings 7 and 8 is not smaller than the difference (xy) between the height X of cylinder 4 and the height y of both vanes 20.21. However, the gap between the side surface 20b of the first vane 20 and the side surface 4b of the vane groove 4a and the gap between the side surface 21b of the second vane 21 and the side surface 4C of the vane groove 4a become smaller. Comparing the amount of high-pressure refrigerant leaking from the back side of both vanes 20 and 21 to the suction chamber 13a and compression chamber 13b in the former and latter, the height y of both vanes 20 and 21 is several times larger than the height 2. (y>z), and the gap between the former and the latter is generally the same in the range of 1o/1000 to 2o/1oooμm, so the cross-sectional area of the latter is several times larger, and therefore the amount of leakage of high-pressure refrigerant The latter is several times more common.

Therefore, considering the total amount of leakage from both the gap between the side surface 20b of the first vane 20 and the side surface 4b of the vane groove 4a, and the gap between the side surface 21b of the second vane 21 and the side surface 40 of the vane groove 4a, By making the latter gap, which has several times as much leakage, smaller, the total amount of leakage can be significantly reduced compared to making the former gap smaller.

Contact surface 20 of the first vane 20 and the second vane 21
By changing the inclination angle θ of a and 21a, the magnitude of the component force G2 that acts to press the side surfaces 20b and 21b of both vanes 20 and 21, respectively, against the side surfaces 4b and 4c of the vane groove 4a can be freely adjusted. It can be changed. Specifically, the larger the inclination angle θ, the smaller the component force G2.
Conversely, the smaller the inclination angle θ, the larger the component force G2 becomes.

In this embodiment, the first vane 2o is arranged so as to be pressed against the side surface 4b of the vane groove 4a on the compression chamber 13b side, and the second vane 21 is arranged so as to be pressed against the side surface 4C of the vane groove 4a on the suction chamber 13a side. However, it cannot be said that the same effect can be obtained even if the arrangement is reversed.

Effects of the Invention As is clear from the above description, the present invention comprises a cylinder, a main bearing and a sub-bearing fixed to both ends of the cylinder, and a shaft having a crank partially housed in the main bearing and the sub-bearing. , a roller rotatably housed in the crank, a first vane that reciprocates slidably in a vane groove provided in the cylinder, and whose tip still contacts the roller, and a second vane whose tip does not come into contact with the roller. From the vane, a first vane and a second vane are arranged in parallel, and the contact surfaces of both vanes are provided with different plate thicknesses so as to be inclined with respect to the direction of reciprocating movement, and the plate thickness of the first vane is The thicker side of the roller is the side that comes into contact with the roller, and the back of the second vane is equipped with a spring that biases the second vane in the direction of the roller, so the pressure is higher than the gap between both vanes and both bearings. The gap between both vanes and the side surface of the vane groove, where a large amount of refrigerant leaks into the suction chamber and the compression chamber, becomes smaller, reducing leakage loss and improving the efficiency of the compressor.

In addition, the first vane and the second vane that partition the suction chamber and the compression chamber
Since the upper and lower gaps between the upper and lower end surfaces of the vanes and both bearings can be maintained evenly, the amount of refrigerant leaking from the compression chamber to the suction chamber through this gap can also be reduced, improving the efficiency of the compressor. can.

[Brief explanation of drawings]

Fig. 1 is a cross-sectional view of the vicinity of the vane of a rotary compressor showing an embodiment of the present invention, Fig. 2 is an enlarged view of the main part of Fig. 1, and Fig. 3 is taken along the I-I/ line in Fig. 1. 4 is a vertical cross-sectional view of a conventional rotary compressor, FIG. 6 is an enlarged view of the main parts in FIG. 4, and FIG. 6 is a view taken along line n-n' in FIG. 4. It is. 3...Shaft, 3c...Crank,
4...Cylinder, 4a...Vane groove, 2
0.--.First vane. 20a... Slanted contact surface of the first vane, 21
...Second vane, 21a...Slanted contact surface of second vane, 23...Spring.

Claims (1)

[Claims] a cylinder, a main bearing and a sub-bearing fixed to both ends of the cylinder, a shaft having a crank partially housed in the main bearing and the sub-bearing, and a roller rotatably housed in the crank; The first vane slideably reciprocates in a vane groove provided in the cylinder, and includes a first vane whose tip abuts the roller, and a second vane whose tip does not abut the roller. The second vanes are arranged in parallel, and the contact surfaces of both vanes are provided with different thicknesses so as to be inclined with respect to the reciprocating direction, and the thicker side of the first vane is in contact with the roller. A rotary compressor, the rotary compressor having a spring on the back side of the second vane that urges the second vane toward the roller.