JP3627454B2 - 2-cylinder rotary compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a two-cylinder rotary compressor used in an air conditioner or a refrigerator.
[0002]
[Prior art]
As a conventional technique, a two-cylinder rotary compressor disclosed in Japanese Utility Model Publication No. 62-186 will be described as an example with reference to the drawings.
[0003]
In FIG. 4, in an airtight container 101, an electric motor unit 102, two compression mechanism units 103a and 103b installed in an axial direction via an intermediate partition plate 106 driven by the electric motor unit 102, and the electric motor unit A crankshaft 104 having two eccentric shaft portions 105a and 105b facing each other by 180 degrees for transmitting the rotational force of 102 to the compression mechanism portions 103a and 103b is provided.
[0004]
Each compression mechanism 103a, 103b includes cylinders 107a, 107b, vanes 109a, 109b slidably installed in vane grooves 108a, 108b provided in the cylinders 107a, 107b, and the crankshaft 104, respectively. It comprises pistons 110a and 110b that are rotatably fitted to the eccentric shaft portions 105a and 105b.
[0005]
Further, a main bearing 111 and a sub-bearing 112 of the crankshaft 104 are installed at both ends in the axial direction of the compression mechanism portions 103a and 103b.
[0006]
Further, elastic members 113a and 113b are installed at one ends of the vanes 109a and 109b, and the force acts to press the vanes 109a and 109b against the outer circumferences of the pistons 110a and 110b, respectively. The cylinders 107a and 107b are partitioned into a suction chamber side space and a discharge chamber side space.
[0007]
With the above configuration, when the motor unit 102 is driven, the rotational force is transmitted to the two eccentric shaft portions 105a and 105b facing each other through the crankshaft 104, and as a result, the pistons 110a and 110b are respectively Eccentric rotation is performed in the cylinders 107a and 107b.
[0008]
As a result, the low-pressure refrigerant gas sucked from the suction holes (not shown) is compressed with the eccentric rotational movement of the pistons 110a and 110b, and becomes high-pressure refrigerant gas from the discharge holes (not shown). The liquid is discharged into the sealed container 101. The high-pressure refrigerant gas acts on one end of the vanes 109a and 109b, and the force due to the pressure acts together with the force of the elastic members 113a and 113b so as to be pressed against the outer periphery of the pistons 110a and 110b.
[0009]
Thereafter, the high-pressure refrigerant gas is discharged from the discharge pipe 114 to the outside of the sealed container 101 through the gap of the electric motor 102.
[0010]
[Problems to be solved by the invention]
However, in the above-described conventional configuration, the force with which the vanes 109a and 109b are pressed against the pistons 110a and 110b is the same as the force by the elastic members 113a and 113b installed at one end of the vanes 109a and 109b, respectively. Of these, the pressing force by the elastic members 113a and 113b causes the vanes 109a and 109b to reciprocate in translation due to the eccentric rotational movement of the pistons 110a and 110b, It changes as the elastic members 113a and 113b themselves expand and contract.
[0011]
When the pistons 110a and 110b are 180 degrees opposite to the angles in the vane grooves 108a and 108b provided in the cylinders 107a and 107b, the elastic members 113a and 113b are in the most extended state (hereinafter, this state is referred to as bottom dead center). On the contrary, when the pistons 110a and 110b are at an angle in the direction of the vane grooves 108a and 108b, the elastic members 113a and 113b are most contracted (hereinafter, this state is referred to as top dead center). Become. Therefore, at the bottom dead center, the force with which the vanes 109a and 109b are pressed against the pistons 110a and 110b is the weakest, and conversely the strongest at the top dead center.
[0012]
The compression mechanisms 103a and 103b are engaged with the eccentric shafts 105a and 105b of the crankshaft 104 that the pistons 110a and 110b are opposed to each other by 180 degrees so that the top dead center is at one compression mechanism. In this state, the other compression mechanism is in the bottom dead center state.
[0013]
Moreover, in addition to the force by said elastic member 113a, 113b, the force by a high pressure refrigerant gas acts on the end of vane 109a, 109b in the direction pressed on the outer periphery of piston 110a, 110b.
[0014]
Due to the above configuration, when the compressor is operated at an extremely high load, that is, when the difference between the pressure of the high-pressure refrigerant gas and the pressure of the low-pressure refrigerant gas is large, the top dead center state is very strong. The vanes 109a and 109b are pressed against the pistons 110a and 110b by force. When such an operating state continues, the wear of the tips of the vanes 109a and 109b proceeds abnormally, resulting in a decrease in reliability. In particular, in recent years, compressors using HFC-based refrigerants that are being used in place of conventional refrigerants are generally known to have severer sliding conditions, and wear at the tips of the vanes 109a and 109b It was one of the big challenges.
[0015]
Further, since the elastic members 113a and 113b are repeatedly expanded and contracted, there is a problem that the elastic members 113a and 113b may be broken due to fatigue unless a design with a sufficient safety factor is performed.
[0016]
Further, since a relatively large torque is required when starting the compressor, an elastic member is installed only on the vane of one compression mechanism, as disclosed in, for example, Japanese Patent Application Laid-Open No. 62-29788. However, there is a technique in which the starting torque is reduced by applying only the force due to the pressure of the high-pressure refrigerant gas inside the hermetic container without being installed in the vane of the other compression mechanism. However, in such a method, when the pressure of the high-pressure refrigerant gas is small, the force with which the vane is pressed against the outer periphery of the piston is too small, and as a result, the refrigerant gas leaks from between the vane and the piston and is compressed. There was a risk of reducing efficiency.
[0017]
The present invention solves the above-described conventional problems, and an object of the present invention is to provide a two-cylinder rotary compressor capable of pressing a vane against a piston with a relatively simple structure with a moderate force. And
[0018]
[Means for Solving the Problems]
In order to solve the above-described problems, the present invention is configured to connect the end of each arc-shaped connecting member to the end of each vane in the cylinder outer peripheral direction so as to be rotatable with respect to the end of the vane. It is formed in contact with the inner wall of the sealed container on the partial outer peripheral side . By this connecting member, the vane of one compression mechanism part is pushed up by the eccentric rotational movement of the piston that is rotatably fitted to the eccentric shaft part of the crankshaft. Part of the vane is pushed down, so that it is pressed against the piston. Thereby, not only an elastic member for pressing the vane against the piston becomes unnecessary, but also the vane can be reliably pressed against the piston with an appropriate force.
[0019]
In the present invention, the end of each arc-shaped connecting member is rotatably connected to the end of each vane in the cylinder outer circumferential direction, and the arc-shaped connecting member is connected to the closed container on the outer peripheral side of the intermediate portion thereof. It is in contact with the inner wall . And according to this structure, the vane of one compression mechanism part is pushed up by the eccentric rotational movement of the piston rotatably fitted to the eccentric shaft part of the crankshaft, and the operation is rotatably connected to one end of the vane. Is transmitted to the connecting member having a circular arc shape. The other end of the arc-shaped connecting member is rotatably connected to one end of the vane of the other compression mechanism portion, and a part of the connecting member is brought into contact with the inner wall of the sealed container. The operation of the arc-shaped connecting member pushes down the vane of the other compression mechanism, and as a result, the vane is pressed against the piston.
[0020]
In the present invention, the arc-shaped connecting member is an elastic member. According to this configuration, the vane can be pressed against the piston with an optimum and constant force by appropriately setting the rigidity of the arc-shaped elastic member.
[0021]
【Example】
Embodiments of the present invention will be described below with reference to the drawings.
[0022]
(Example 1)
In FIG. 1, in an airtight container 1, an electric motor unit 2, two compression mechanism units 3a and 3b installed in an axial direction via an intermediate partition plate 6 driven by the electric motor unit 2, and the electric motor unit A crankshaft 4 having two eccentric shaft portions 5a and 5b opposed to each other by 180 degrees for transmitting the rotational force of 2 to the compression mechanism portions 3a and 3b is provided.
[0023]
The compression mechanism portions 3a and 3b include cylinders 7a and 7b, vanes 9a and 9b slidably installed in vane grooves 8a and 8b provided in the cylinders 7a and 7b, and the crankshaft 4 It consists of pistons 10a and 10b that are rotatably fitted to the eccentric shaft portions 5a and 5b.
[0024]
A main bearing 11 and a sub-bearing 12 of the crankshaft 4 are installed at both axial ends of the compression mechanism portions 3a and 3b.
[0025]
Further, at one end of the vanes 9a and 9b, concave portions 13a and 13b are provided, both end portions 14a and 14b of the connecting member 14 are rotatably connected, and the axial height central portion of the connecting member 14 is provided. Is provided with a support point 15. The ends of the vanes 9a and 9b opposite to the ones where the recesses 13a and 13b are provided are in contact with the outer circumferences of the pistons 10a and 10b, respectively, and the cylinders 7a and 7b have a suction chamber side space and a discharge chamber side. It is partitioned into a space.
[0026]
With the above configuration, when the electric motor unit 2 is driven, the rotational force is transmitted to the two eccentric shaft portions 5a and 5b facing each other through the crankshaft 4, and as a result, the pistons 10a and 10b respectively Eccentric rotation is performed in the cylinders 7a and 7b. As a result, the low-pressure refrigerant gas sucked from the suction holes (not shown) is compressed with the eccentric rotational motion of the pistons 10a and 10b. Thereafter, the refrigerant gas compressed by the compression mechanism portion 3a becomes high-pressure refrigerant gas from a discharge hole (not shown) and is temporarily discharged into the main shaft-side discharge space 16. In addition, the refrigerant gas compressed by the compression mechanism 3b becomes high-pressure refrigerant gas from a discharge hole (not shown) and is once discharged into the countershaft side discharge section 17, and then passes through the communication hole 18. , And are discharged into the spindle-side discharge space 16. Thereafter, the gas is discharged from the annular gap 19 into the sealed container 1, passes through the gap of the electric motor 2, and is discharged from the discharge pipe 20 to the outside of the sealed container 1.
[0027]
Further, as the pistons 10a and 10b perform eccentric turning motion in the cylinders 7a and 7b, the vanes 9a and 9b perform reciprocal translational motion. When the vane 9a (9b) of one compression mechanism 3a (3b) is pushed up by the piston 10a (10b), the movement of the vane 9a (9b) moves to the one end 14a (14b) of the connecting member 14 via the recess 13a (13b) of the vane. Is transmitted. Since the supporting point 15 is provided in the central portion of the axial height of the connecting member 14, the movement passes through the other end 14b (14a) of the connecting member 14 and the vane of the other compression mechanism 3b (3a). It transmits so that the recessed part 13b (13a) may be pushed down. As a result, the vane 9b (9a) is pushed down, and one end of the vane 9b (9a) is pressed against the piston 10b (10a). Further, as the crankshaft 4 rotates, these operations are repeated alternately.
[0028]
Therefore, when one piston pushes up the vane, the other vane is reliably pressed against the piston via the connecting member, so that an elastic member for pressing the vane against the piston as in the prior art becomes unnecessary, and this elastic member There are no issues such as breakage.
[0029]
The connecting portions 13a and 13b of the vanes 9a and 9b with the connecting member 14 are formed as spherical concave portions, and both ends 14a and 14b of the connecting member 14 are formed as spherical convex portions, whereby the vanes 9a and 9b and the connecting members are formed. The surface pressure at the 14 connecting portions can be reduced, and wear at this portion can be suppressed.
[0030]
Furthermore, by installing the support point 15 of the connecting member 14 in a part of the intermediate partition plate 6, there is no need to add a part for providing a separate support point.
[0031]
(Example 2)
In the embodiment shown in FIG. 2, the same components as those shown in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
[0032]
In the figure, recesses 13a and 13b are provided at one ends of vanes 9a and 9b, and both end portions 14a and 14b of a connecting member 14 are connected via elastic members 21a and 21b. A fulcrum 15 is provided at the center of the axial height of 14.
[0033]
With the above configuration, the vanes 9a and 9b perform reciprocal translational movements as the pistons 10a and 10b perform eccentric turning motions in the cylinders 7a and 7b. When the vane 9a (9b) of one compression mechanism part 3a (3b) is pushed up by the piston 10a (10b), one end of the connecting member 14 from the recess 13a (13b) of the vane via the elastic member 21a (21b). The movement is transmitted to 14a (14b). Since the support point 15 is provided in the central portion of the connecting member 14 in the axial direction, the movement is performed from the other end 14b (14a) of the connecting member 14 through the elastic member 21b (21a) to the other compression mechanism. It transmits so that the recessed part 13b (13a) of the vane of the part 3b (3a) may be pushed down. As a result, the vane 9b (9a) is pushed down, and one end of the vane 9b (9a) is pressed against the piston 10b (10a). Further, as the crankshaft 4 rotates, these operations are repeated alternately.
[0034]
Therefore, when one piston pushes up the vane, the other vane is reliably pressed against the piston via the elastic member and the connecting member. In addition, since the displacement of the elastic member itself hardly changes and a constant force always acts, the vane can be pressed against the piston with an optimal and constant force by setting the rigidity of the elastic member appropriately in advance. Can do.
[0035]
Furthermore, even if there are gaps between parts due to part tolerance or assembly tolerance, they are absorbed by the elastic members 21a and 21b, so that part processing or assembly is facilitated.
[0036]
(Example 3)
In the embodiment shown in FIG. 3, the same components as those shown in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
[0037]
In the figure, recesses 13a and 13b are provided at one ends of vanes 9a and 9b, both ends of an arc-shaped connecting member 22 are rotatably connected, and a part of the connecting member 22 is hermetically sealed. It is made to contact the inner wall of the container 1.
[0038]
With the above configuration, the vanes 9a and 9b perform reciprocal translational movements as the pistons 10a and 10b perform eccentric turning motions in the cylinders 7a and 7b. When the vane 9a (9b) of one compression mechanism part 3a (3b) is pushed up by the piston 10a (10b), the movement is caused at one end of the arc-shaped connecting member 22 via the recess 13a (13b) of the vane. Communicated. Since the vicinity of the center of the height of the connecting member 22 in the axial direction is in contact with the inner wall of the hermetic container 1, the movement from the other end of the connecting member 22 to the recess 13b of the vane of the other compression mechanism 3b (3a). (13a) is transmitted to be pushed down. As a result, the vane 9b (9a) is pushed down, and one end of the vane 9b (9a) is pressed against the piston 10b (10a). Further, as the crankshaft 4 rotates, these operations are repeated alternately.
[0039]
Therefore, when one piston pushes up the vane, the other vane is surely pressed against the piston via the arc-shaped connecting member, so that the conventional elastic member for pressing the vane against the piston becomes unnecessary.
[0040]
Further, by giving elasticity to the arc-shaped connecting member 22 itself, the vane can be pressed against the piston with an optimum and constant force. Further, even if gaps between parts due to part tolerance or assembly tolerance occur, these are absorbed by the elastic member 22, so that parts can be processed or assembled easily.
[0041]
【The invention's effect】
According to the present invention, one end of the vanes of each compression mechanism portion is connected to each other by the arc-shaped connection member, and a part of the connection member is brought into contact with the inner wall of the sealed container. The vane is pushed up by the eccentric rotational movement of the piston, and its movement is transmitted to an arc-shaped coupling member rotatably connected to one end of the vane, and the vane of the other compression mechanism part is pushed down. Pressed against. Therefore, the vane can be reliably pressed against the piston.
[0042]
Also, since the arc-shaped connecting member itself has elasticity, the vane can be pressed against the piston with an optimum and constant force by appropriately setting the rigidity of the arc-shaped connecting member in advance. The progress of wear at the vane tip can be reduced. Further, even if there are gaps between parts due to part tolerance or assembly tolerance, they are absorbed by the elastic member, so that part processing or assembly is facilitated.
[0043]
As described above, the effect of being able to reliably press the vane against the piston with a constant force with a relatively simple structure without using an elastic member for pressing the vane against the piston as in the prior art. Can be obtained.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a two-cylinder rotary compressor showing a first embodiment of the present invention. FIG. 2 is a longitudinal sectional view of an essential part of a two-cylinder rotary compressor showing a second embodiment of the present invention. FIG. 3 is a longitudinal sectional view of an essential part of a two-cylinder rotary compressor showing a third embodiment of the present invention. FIG. 4 is a longitudinal sectional view of a conventional two-cylinder rotary compressor.
DESCRIPTION OF SYMBOLS 1 Airtight container 6 Intermediate | middle partition plates 9a and 9b Vane 10a, 10b Piston 13a, 13b Vane recessed part 14 Connection member 14a, 14b Connection member convex part 15 Connection member support point 21a, 21b Elastic member 22 Arc-shaped connection member

Claims (2)

In the sealed container, the motor part, two compression mechanism parts installed in the axial direction via the intermediate partition plate, and 180 degrees opposite each other for transmitting the rotational force of the motor part to the compression mechanism part A crankshaft having two eccentric shaft portions, and a cylinder having a cylindrical cylinder for housing each of the eccentric shaft portions and a radial passage through each of the compression mechanism portions. and slidably installed the vane groove provided Te, wherein constituted by a rotatably fitted the installed piston eccentric shaft portion of the crank shaft, the vane cylinder circumferential end A two-cylinder rotary compressor in which a portion is disposed so as to be in contact with the outer peripheral surface of the piston, and a main bearing and a sub-bearing that support the crankshaft are installed at both axial ends of the two compression mechanisms. And the end of each vane in the cylinder outer circumferential direction End of the arc-shaped connecting member is rotatably coupled to the vane ends respectively, the arcuate connecting member is characterized by comprising abuts on the closed container inner wall at the intermediate portion outer peripheral side of the 2-cylinder rotary compressor. The two-cylinder rotary compressor according to claim 1, wherein the arc-shaped connecting member is an elastic member.

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