JPH04179888A - Rotary compressor - Google Patents

Abstract

PURPOSE:To improve efficiency of a compressor by inclining contact surfaces of vanes arranged side by side against the direction of reciprocating motion, and providing grooves where cross sectional areas increase and grooves where cross sectional areas decrease respectively from a spring side toward a roller side on the side surfaces where vane grooves of the first vane and the second vane can slide with each other. CONSTITUTION:Contact surfaces 20a and 21a of the first and the second vanes 20 and 21 are arranged by changing the thicknesses of plates so as to be inclined against the direction of reciprocating motion. Grooves 24a, 24b and 24c where cross sectional areas increase and grooves 25a, 25b and 25c where cross sectional areas decrease respectively from the rear side toward a roller 5 side are arranged alternately on the side surface 20b of the first vane. Furthermore, similarly, grooves where cross sectional areas increase and grooves where cross sectional areas decrease are also arranged on the side surface 21b of the second vane. A spring 23 is arranged in the rear side of the second vane 21. Thereby, the space between both vanes and the vane groove side surfaces, where high pressure refrigerant larger in quantity than-that in the space between both vanes and both bearings is leaked into an inhalation chamber and a compression chamber, can be minimized and leakage loss can be reduced so that efficiency of a compressor can be improved while keeping reliability of both vanes.

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. 6, 7, and 8. Note that the arrows in FIG. 8 indicate the leakage of high-pressure refrigerant, and the arrows in FIG. 7 indicate the acting force.

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 6b, main bearing 7. It is connected to a mechanical part main body 9, which is composed of a sub-bearing 8.

The shaft 3 includes a main shaft 3a, a subshaft 3b, and a crank 3C. Further, the first reciprocating plate 6a and the 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. Further, 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 16 of the cylinder 4. Reference numeral 16 denotes a discharge hole, which communicates with the inside of the sealed casing 1 via a discharge valve 17. Reference numeral 18 denotes a discharge pipe, which is open into the sealed casing 1. 19 is lubricating oil.

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

Refrigerant gas from a cooling synutem (not shown) is supplied to 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 13a is
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.

The lubricating oil 19 is supplied to the shaft 3 and the main bearing 7 by the oil supply mechanism 12. It is supplied to sliding parts such as the secondary bearing 8.

Here, the mating surfaces of the first reciprocating plate 6d and the second reciprocating plate 6b have the same plate thickness, and are inclined with respect to the direction of reciprocating movement. Therefore, the second reciprocating plate 6b
A 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 surface of the second reciprocating plate 6b. Therefore, force F1 acts on the mating surface 6d of the second reciprocating plate 6b in a direction perpendicular to the mating surface 6d. The second reciprocating plate 6b receives a force F in the reciprocating direction as a component of the force F1, and a force F2 in the axial direction and perpendicular to the force F.
acts. 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 sub-bearing 8 side. Therefore, the gap between the end surface 6e of the first reciprocating plate 6a and the sub-bearing 8 and the end surface 6f of the second reciprocating plate 6b are
The gap between the main bearing 7 and the main bearing 7 becomes smaller.

Therefore, the processing accuracy of vane g4a, cylinder 4, etc.
Even if the above-mentioned gap is tighter than necessary due to assembly accuracy,
During operation of the compressor, the gap becomes smaller as described above. Therefore, the high-pressure refrigerant inside the sealed casing 1 flows through the end surfaces 6e, 6
f and secondary bearing 8. The suction chamber 13a is inserted through the gap between the main bearings 7.
Also, the amount leaking into the compression chamber 13b was reduced, and leakage loss was 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 width 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, there was the issue of not being able 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 drawbacks of the above-mentioned conventional examples, and uses a simple mechanism to reduce the amount of leakage between the reciprocating plate and the vane groove, which is a flow path that leaks several times more than the amount of leakage through the gap between the reciprocating plate and both bearings. The purpose 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 the efficiency of the compressor.

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. It consists of 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 connected to the roller. A spring that biases the second vane in the direction of the roller is placed on the back surface of the second vane, and a side surface on which the vane grooves of the first vane and the second vane slide is placed on the back side of the second vane, and a spring that biases the second vane toward the roller is placed on the side that contacts the vane groove from the spring side toward the roller side. The groove is provided with a groove whose cross-sectional area increases and a groove whose cross-sectional area decreases.

Effect: The present invention has the above-described configuration, and the total force G 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 is applied 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. Further, a reaction force acts on the first vane as well, and the first vane is pressed against the side surface of the vane groove. When the first and second vanes reciprocate, lubricating oil flows into a groove provided on the side surface whose cross-sectional area changes in the direction of the reciprocating movement, and as the cross-sectional area decreases, pressure is generated. . As a result, the first and second vanes are held at a position where the force G2 and the pressure are balanced. In other words, when the gap between the first and second vanes and the vane groove becomes smaller, the pressure generated in the grooves on the side surfaces of the first and second vanes becomes higher, pushing back the first and second vanes, and when the gap becomes larger, pressure is generated. The pressure decreases and the first and second vanes are pressed against the vane grooves. Therefore, by providing the flexibility of the first and second vanes to move so that the gaps between the first and second vanes and the vane grooves are almost constant regardless of assembly distortion or processing accuracy, 2
The gap between the vane and the vane groove can be kept to a minimum.

Therefore, 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 pressure chamber, are several times larger than the gap between the end surfaces of the first and second vanes and both bearings. The gap between the vane grooves can be kept to a minimum. 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 is shown in FIGS. 1, 2, 3, and 4.
This will be explained with reference to FIG. 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; 2o is a first groove whose tip is in contact with roller 5;
Vane, 21 is the second vane, 23 is the second vane 72
This is a spring provided on the back of 1.

In addition, 2Qa and 2ja are first and second bases 720 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 first and second surfaces:
/20.21 side, 20C.

20d is the end face of the first vane, and 2IC and 21d are the end faces of the second vane 721. Furthermore, +d and +c are vane grooves 4a
and are opposite to the side surface 20b of the first vane 20 and the side surface 21b of the second vane 21, respectively.

Furthermore, the side surface 20b of the first vane is provided with a groove 24a whose cross-sectional area increases from the back surface toward the roller 6 side.

24b, 24c and a groove 25a with a decreasing cross-sectional area.

2sb and 25C are provided alternately. Similarly, a groove 26a with an increased cross-sectional area is also formed on the side surface 21b of the second vane.
, 26b, 26c and a groove 27a with a reduced cross-sectional area,
27b and 27c are provided.

In the above configuration, first, 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 6 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 5 from there.

Contact surface 20a between first vane 720 and 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 plate 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. In addition, the force acting on the first vane 2o is:
The force G acting on the second bay 721, G1. Each reaction force of G2 will act. Both vanes 20°21
The force G2 acting on each of the first vanes 2o
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 side.

The upper and lower end surfaces 20C and 20d of the first vane 2o, the upper and lower end surfaces 21c and 21d of the second vane 21, and both bearings 7
, 8 is the height X of the cylinder 4 and both vanes 20,
It is not smaller than the difference (x-y) in height y of 21. However, the side surface 2ob of the first vane 2o and the vane groove 4
The gap between the side surfaces 4b of a and the side surface 21b of the second vane 21
The gap between the side surface 4C of the vane groove 4a and the side surface 4C of the vane groove 4a becomes smaller. Comparing the amount of high-pressure refrigerant leaking from the back side of both vanes 720, 21 to the suction chamber 13a and compression chamber 13b in the former and latter, the height y of both vanes 20, 21 is several times larger than the height 2. (y>z) dimension, the gap between the former and the latter is generally 1
Since they are almost the same in the range of 0/100 to 20/100 μm, the cross-sectional area of the gap is several times larger in the latter case, and therefore the leakage amount of high-pressure refrigerant is also several times larger in the latter case.

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 4C of the vane groove 4a, By making the latter gap smaller, which has several times as much leakage, the total amount of leakage can be significantly reduced by making the former gap smaller.

Next, the first vane 2o and the second vane 21 and the vane groove 4
The gap between a (δa, δb) will be explained. The first and second vanes accommodated in the vane groove 4a during compressor operation.
When the bays 720.21 reciprocate, the first bay 720. Second
Vane 21 floods and lubricates first and second plates 720.21.

First, the first vane 2o and the second vane 721 are connected to the cylinder 4.
The case where the object moves toward the center of the object will be explained. At this time, grooves 24a, 24b, and 2 whose cross-sectional area increases from the back surface toward the roller 5 side are provided on the side surface 20b of the first vane 2o.
4c inflow portion 24d.

The lubricating oil 19 in 2+e and 2+f is applied to the sealing parts 24q and 24h because the first bay 720 moves toward the center of the cylinder 4.
, 24i. And this sealing part 24 (J, 2
4h, the pressure of the lubricating oil 19 increases due to the wedge effect guided by 24i.

Similarly, on the side surface 21b of the second vane 21, the pressure of the lubricating oil 19 increases in the grooves 26a, 26b, and 26c.

Next K, 11 vane 2o and second base 721 are cylinder 4
A case will be described in which the second vane 21 moves from the center side to the spring 23 side provided on the back side of the second vane 21. At this time, the inflow portions 25d of the grooves 2sa, 2sb, and 2sc are provided on the side surface 20b of the first vane 2o, and the cross-sectional area decreases from the back surface toward the roller side.

The lubricating oil 19 in 2se and 2sf is in the sealing parts 25g and 25h because the first vane moves toward the spring 23 side.

Guided by 25i. And this sealing part 26q.

The pressure of the lubricating oil 19 increases due to the wedge effect while the lubricating oil 19 is being guided to 25h and 25i. Similarly, the second vane 21
There is also a groove 27a on the side surface 21b.

The pressure of the lubricating oil 19 increases at 2yb and 27C. The gap δb between the side surface 2ob of the first vane 2o and the vane groove side surface 4b and the gap δa between the side surface 21b of the second vane 21 and the vane groove 4C are the grooves 24a whose cross-sectional area increases.
~24C, 26a~26c and groove 26 with decreasing cross-sectional area
If a~25c and 27a~27c have the same dimensions, δa=
δb. This is because the hydraulic pressures generated on the side surface 20b of the first vane 2o and the side surface 21b of the second vane 721 are equal. For example, when the gaps δd and δb are not equal and δa>δb, the hydraulic pressure generated on the side surface 21b of the second vane 21 is smaller than the hydraulic pressure generated on the side surface 20b of the first vane 2o. Therefore, the first and second vanes 20.21 move toward the side surface 4c of the vane groove, and when the gap δa is small, the hydraulic pressure generated on the side surface 21b of the second page 721 increases. And both sides 2o
b.

The position where the hydraulic pressure generated in 21b is balanced, that is, δa
The first and second vanes 20°21 are held at the position of =δb. Also, the side surfaces 20 of the first and second vanes 20.21
The hydraulic pressure generated at b and 21 b balances the force G2 generated at the contact surfaces of the first and second vanes 20 and 21, and as a result, the sizes of the gaps δa and δb are determined. Therefore, regardless of assembly distortion or machining accuracy, contact surface 2
0 a.

By changing the magnitude of force G2 at 21a, the gap δ
a and δb can be kept to a minimum. .

That is, by changing the inclination angle θ of the contact surfaces 20a and 21a of the first vane 2o and the second vane 21, the side surfaces 20b and 21b of both vanes 720 and 21 are changed to the side surfaces 4b and 4c of the vane groove 4a, respectively. The magnitude of the component force G2 that acts to press can be freely changed. Specifically, the larger the inclination angle θ, the smaller the component force G2 υ, and conversely, the smaller the inclination angle θ, the larger the component force G2.

Therefore, the side surface 2ob of the first vane 20 and the vane groove side surface 4
b and the side surface 21b of the second vane 21 and the vane groove side surface 4
It is possible to minimize the respective gaps δb and δa between
, 21b, there is no local wear, and reliability can be ensured.

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 entire vane groove 4a on the suction chamber 13a side. However, it goes without saying 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 that is rotatably housed in the crank, 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 plate thickness of the first vane is The thick side is the side that comes into contact with the roller, and a spring that urges the second vane in the direction of the roller is on the back surface of the second vane, and a spring side is provided on the side surface that slides with the vane grooves of the first vane and the second vane. Since it is equipped with grooves whose cross-sectional area increases and grooves whose cross-sectional area decreases toward the roller side, the amount of high-pressure refrigerant leaking into the suction chamber and compression chamber is also reduced through the gap between both vanes and both bearings. The gap between both vanes and the side surfaces of the vane grooves, which have a large amount of friction, can be kept to a minimum, thereby reducing leakage loss and improving the efficiency of the compressor while ensuring the reliability of both vanes.

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 front view of the vicinity of the vane of a rotary compressor showing an embodiment of the present invention, Fig. 2 is an enlarged front view of the main part near the vane shown in Fig. 1, and Fig. 3 is the I -I' line sectional view, Figure 4 is a side view of the first vane of the present invention, Figure 5 is a change curve of clearance and hydraulic pressure between both vanes and the vane groove, Figure 6 is a conventional rotary type FIG. 7 is an enlarged sectional view of essential parts of the rotary compressor shown in FIG. 6, and FIG. 8 is a sectional view taken along line 2--' in FIG. 6. 3...Shaft, 3C...Crank,
4"...Cylinder, 4a...Vane m,
20... First vane, 20a... Slanted contact surface of the first vane, 21... Second vane, 21a... of the second vane. inclined contact surface,
23... Spring, 24a, 24b, 24c.
... Grooves with increasing cross-sectional area, 25a, 25b, 25
c... Groove whose cross-sectional area decreases. Name of agent: Patent attorney Akira Okaji and two others Figure 3 1! 4 E! 4b P4C and 5C 115 Shearance (S (1,, rb) Large I7 Figure 18 Figure

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, and the first vane and 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 spring that biases the second vane in the direction of the roller, and a spring that biases the second vane in the direction of the roller;
A rotary compressor comprising a groove whose cross-sectional area increases and a groove whose cross-sectional area decreases from the spring side toward the roller side on a side surface of the vane that slides with the vane groove.