CN1127625C - Rotary sealed compressor and refrigeration cycle device thereof - Google Patents

Abstract

In a rotary hermetic compressor that generates high pressure in a hermetic casing, the compression mechanism unit 2 is provided with a plurality of cylinders 8A, 8B and vanes 15a, 15b. Wherein, eccentric rollers 13a, 13b are equipped with free eccentric rotation in each cylinder 8A, 8B; and blades 15a, 15b are arranged on these cylinders, and due to being pushed by the pushing force device, its front end is in contact with the above-mentioned eccentric rollers. The peripheral surfaces of the eccentric rollers are connected, and the cylinder chambers 14a, 14b are divided into two chambers along the direction of rotation of the eccentric rollers. The pressing device for pressing the above-mentioned one blade is the elastic member 26, and the pushing device for pushing the other blade is the high-pressure gas in the closed casing.

Description

Rotary hermetic compressor and refrigeration cycle device

The present invention relates to a rotary hermetic compressor constituting, for example, a refrigeration cycle system of an air conditioner, and a refrigeration cycle device constituting a refrigeration cycle with the compressor.

The structure of a general rotary hermetic compressor is that a motor and a compression mechanism connected to the motor are installed in the closed casing. Once the gas compressed by the above-mentioned compression mechanism is discharged into the closed casing, the closed casing becomes high pressure. state.

In the above-mentioned compression mechanism unit, the eccentric roller is mounted in the cylinder so as to be eccentrically rotatable. Moreover, a vane receiving groove is designed on the cylinder, and the vane is slidably mounted in the groove. By being pushed by the pushing force device, the front end edge of the vane is in contact with the peripheral surface of the above-mentioned eccentric roller.

Therefore, the inside of the cylinder is divided into two chambers by the blade along the rotation direction of the eccentric roller. One side chamber communicates with the suction part, and the other side chamber communicates with the discharge part. The suction part is connected with a suction pipe, and the opening of the discharge part faces into the closed casing.

A coil spring is usually used as the elastic member as the pressing means for pressing the blade. One end of the coil spring is in contact with the inner peripheral surface of the closed case, and the other end is in contact with the back surface of the vane, so that the vane in contact with its free end is elastically pushed. Since the above-mentioned helical springs are always pressed against the blades, compression begins to take place after activation.

In addition, especially in the case of multi-cylinder rotary hermetic compressors such as two cylinders that have recently become mainstream, the wall thickness of the single cylinder is thinner, and there is also a space for accommodating the coil spring, which reduces the rigidity of the cylinder. Therefore, the outer diameter of the cylinder needs to be designed to be larger to compensate for the impact of the decrease in the rigidity of the cylinder, resulting in an increase in the diameter of the closed shell.

Furthermore, since each cylinder is provided with a horizontal hole for inserting the coil spring, the machining process is complicated. Since there are two cylinders, two coil springs are required, which increases the cost of parts. After the insertion process of each coil spring is completed, it is necessary to prevent it from being ejected again, so the operation is very complicated.

In addition, since each cylinder is provided with a horizontal hole for inserting the coil spring, the strength for preventing deformation of the vane groove is reduced. Therefore, when the cylinders are fixedly mounted on the closed casing by means such as arc spot welding, the blade grooves are deformed due to the influence of stress generated during welding, so that the blades cannot move smoothly, resulting in serious consequences.

On the other hand, HFC (hydrogenated hydrocarbon) mixed refrigerants that do not contain chlorine atoms will be used as new refrigerants that will soon replace the R22 refrigerants that have been used frequently.

The compressor that compresses this HFC mixed refrigerant into a high-pressure high-temperature gas and circulates it in the refrigeration system has high rotational efficiency, so it is most suitable for a rotary hermetic compressor with high compression performance.

The HFC mixed refrigerant has a theoretical refrigeration capacity stronger than that of traditional refrigerants. In particular, if the refrigerant is changed to the high-pressure and high-capacity refrigerant R410A, it is expected to obtain a higher efficiency (COP) than the current R22 refrigerant.

However, if the refrigeration capacity and working pressure of the refrigerant are 1.5 times that of R22, and the pressure on the movable components such as the rotating shaft is equivalent to that of R22, the wall thickness of the cylinder can only be reduced.

However, if the wall thickness of the cylinder is reduced, the rigidity will of course be lowered. If the rigidity of the cylinder is lowered, the accuracy of the parts processing will of course not be guaranteed, resulting in increased deformation during assembly, causing gas leakage, resulting in reduced efficiency.

In addition, since the wall thickness of each cylinder is thinner than that of a single-cylinder type in a two-cylinder compressor, it is necessary to increase the outer diameter of the cylinder when using R410A refrigerant, making this problem even more necessary.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a rotary hermetic compressor and a refrigeration cycle apparatus constituting a refrigeration cycle system using the rotary hermetic compressor. When the rotary hermetic compressor is equipped with multiple cylinders, at least one cylinder vane pushing member can be omitted, thereby reducing the number of parts and processing steps, while not reducing the rigidity of the cylinders, achieving miniaturization, Thin wall, and improve the reliability of the equipment.

In order to achieve the above object, the rotary hermetic compressor of the first scheme is equipped with a motor and a compression mechanism connected to the motor in the closed casing. Once the gas compressed by the compression mechanism is discharged into the closed casing, the closed casing The body becomes high pressure. It is characterized in that: the above-mentioned compression mechanism part is provided with a plurality of cylinders and vanes, wherein, eccentric rollers are installed in each cylinder to rotate freely and eccentrically, and the vanes are arranged on these cylinders, due to being pushed by the pushing device, Its front end is in contact with the peripheral surface of the above-mentioned eccentric roller, and divides the cylinder into two chambers along the rotation direction of the eccentric roller; the pushing force device of the above-mentioned pushing blade is the elastic member and the high-pressure gas in the closed casing. .

As a scheme 2, it is characterized in that: on the rotary hermetic compressor described in scheme 1, the high-pressure gas from the closed casing is used as the cylinder of the above-mentioned pushing force application member, and its outer diameter is designed to be smaller than that of the elastic member used as the above-mentioned cylinder. The outer diameter of the cylinder that pushes the urging member is small.

As solution 3, it is characterized in that: on the rotary hermetic compressor described in solution 1, a cylinder using an elastic member as the above-mentioned pushing force device is used, and its outer peripheral part is embedded and fixed on the inner peripheral wall of the above-mentioned closed casing. .

As a fourth aspect, in the rotary hermetic compressors according to the first to third aspects, the elastic member is a coil spring.

As a fifth aspect, it is characterized in that the above-mentioned compression mechanism is used in the rotary hermetic compressor according to the first aspect to compress a refrigerant having a working pressure higher than that of R22.

As scheme 6, it is characterized in that: on the rotary hermetic compressor described in scheme 1, the above-mentioned motor is electrically connected to the control device, and the control device is provided with a frequency converter capable of changing the operating frequency, so that it can operate at low frequency when starting , when the discharge pressure reaches the set pressure, it is high-frequency operation.

As solution 7, it is characterized in that: on the rotary hermetic compressor described in solution 1, the cylinder using the high-pressure gas in the closed casing as the above-mentioned pushing force applying device is used, and its outer peripheral part is embedded in the above-mentioned closed casing on the inner peripheral wall.

As scheme 8, it is characterized in that: on the rotary hermetic compressor described in scheme 1, among the above-mentioned blades, the blades pushed by the high-pressure gas in the closed casing are formed with a cross section in the shape of an arc, and the circle The radius Rv of the arc is smaller than the inner radius Rc of the undercut hole for machining the blade receiving groove provided on the opposite side of the blade (Rv<Rc).

As solution 9, it is characterized in that: on the rotary hermetic compressor described in solution 1, among the above-mentioned blades, the blades pushed by the high-pressure gas in the closed casing are chamfered with a radius of less than 1mm on the two edges on the back side processing.

In order to achieve the above-mentioned purpose of the refrigeration cycle device, as the tenth proposal, the rotary hermetic compressor is equipped with a motor and a compression mechanism connected to the motor in the hermetic casing, and once the gas compressed by the compression mechanism is discharged to In the closed shell, the closed shell becomes a high-pressure state. It is characterized in that its refrigeration cycle is composed of a rotary hermetic compressor, a condenser, an expansion mechanism, and an evaporator. The above-mentioned compression mechanism is equipped with multiple cylinders and vanes. , wherein, eccentric rollers are installed in each cylinder freely eccentrically rotating; and the vanes are arranged on these cylinders, and due to being pushed by the pushing force body, the front ends of the eccentric rollers are in contact with the peripheral surface of the above-mentioned eccentric rollers, and along the The rotating direction of the eccentric roller divides the cylinder into two chambers, wherein at least one pushing force body of the pushing blade adopts an elastic member, and at least one pushing force body of the pushing blade adopts a closed shell Gas under pressure in the body.

By adopting the above-mentioned means for solving the problems, the above-mentioned invention has sufficient reliability in pressing the vane even if the wall thickness of the cylinder is thin.

Fig. 1 is a longitudinal sectional view of a rotary hermetic compressor according to an embodiment of the present invention.

Figure 2 is an exploded perspective view of the upper cylinder and the lower cylinder of the embodiment shown in Figure 1 .

Fig. 3 (A) is the state schematic diagram of the upper cylinder chamber and the lower cylinder chamber after the embodiment shown in Fig. 1 starts; (B) is the state diagram of the upper cylinder chamber and the lower cylinder chamber when the compression is stable.

Fig. 4 is a longitudinal sectional view of a rotary hermetic compressor according to another embodiment of the present invention.

Fig. 5 (A) is the plan view of upper cylinder in the embodiment shown in Fig. 4; (B) is the plan view of upper cylinder.

Fig. 6 is a plan view of the back side of the blade and the longitudinal hole of another embodiment.

Fig. 7 is a plan view of the back side of the blade and the longitudinal hole of another embodiment. In the figure: 1...closed shell; 3...electric motor; 2...compression mechanism; 13a, 13b...eccentric roller; 8A, 80A...upper cylinder; 8B, 80B...lower cylinder; 26...pushing body (screw spring); 15a, 15b...blade; 30...inverter; 40...control device (control part); 24a, 24b...longitudinal hole.

Next, an embodiment of a rotary hermetic compressor will be described with reference to the drawings. The compressor constitutes, for example, a refrigeration cycle system of an air conditioner, and the refrigerant used here is an HFC mixed refrigerant. Moreover, among the HFC mixed refrigerants, it is preferable to use R410A.

The R410A is formed by mixing difluoromethane (R32) and pentafluoroethane (R125) at a weight ratio of 50% each.

As shown in FIG. 1 , the rotary hermetic compressor includes a hermetic casing 1 . Inside the closed case 1, a compression mechanism unit 2 to be described later is provided at the lower part, and an electric motor 3 is provided at the upper part. The compression mechanism part 2 and the motor 3 are connected by a rotating shaft 4 .

The motor 3 is composed of a stator 5 and a rotor 6, wherein the stator 5 is fixed on the inner wall surface of the closed casing 1, and the rotor 6 is inserted on the above-mentioned rotating shaft 4, and is arranged to have a certain gap between the inner surface of the stator 5 form.

The motor 3 is connected to a frequency converter 30 capable of changing its operating frequency, and is electrically connected to a control unit 40 through the frequency converter 30 . The control unit 40 is a control device for controlling the frequency converter 30 .

In the above-mentioned compression mechanism unit 2, two cylinders 8A, 8B are vertically arranged on the lower portion of the rotating shaft 4 through a partition plate 7. As shown in FIG. Since the refrigerant used in the cylinders 8A and 8B is R410A high-pressure refrigerant, the amount of heat transfer per unit volume is large. Therefore, its wall thickness is thinner than conventional cylinders using R22 refrigerant, and it is expected to reduce the isolation volume.

The main bearing 9 coincides with the upper surface of the above-mentioned cylinder 8A, and together with the valve cover a, is fixed on the cylinder 8A by mounting bolts 10 . The auxiliary bearing 11 is overlapped with the lower surface of the above-mentioned cylinder 8B, and is fixed on the cylinder 8B by the mounting bolt 12 together with the valve cover b.

On the other hand, the above-mentioned rotating shaft 4 is freely rotatably supported on the above-mentioned main bearing 9 and sub-bearing 11 at the middle portion and the lower end portion thereof. Furthermore, the rotating shaft 4 penetrates the interior of the cylinders 8A, 8B, and two eccentric portions 4a, 4b are integrally formed with a phase difference of approximately 180°. The eccentric parts 4a, 4b are located in the respective cylinders 8A, 8B, and rollers 13a, 13b are fitted on the outer peripheries thereof.

The cylinders 8A, 8B are divided into upper and lower parts by the partition plate 7, the main bearing 9, and the sub-bearing 11, and cylinder chambers 14a, 14b are formed therein. The eccentric rollers 13a, 13b are housed in the respective cylinder chambers 14a, 14b so as to be eccentrically rotatable, and the cylinder chambers are crescent-shaped when viewed from their own planes.

In each cylinder 8A, 8B, vanes 15a, 15b that divide cylinder chambers 14a, 14b into a high-pressure side and a low-pressure side are provided. Each vane 15a, 15b is pressed and urged toward the eccentric roller 13a, 13b side by a pressing body as a pressing means to be described later.

The two cylinders 8A, 8B are respectively connected to the suction pipes 16a, 16b, and the other end of the suction pipes joins outside the closed casing 1 and is connected to the reservoir 17. In addition, an outlet pipe 18 is connected to the upper end portion of the closed case 1 . The outlet pipe 18 is connected to the above-mentioned accumulator 17 through a condenser 19 , an expansion mechanism 20 and an evaporator 21 . In this way, for example, a refrigeration cycle of an air conditioner is constituted.

Next, the cylinders 8A, 8B and the above-mentioned pressing body will be described in detail with reference to FIG. 2 .

Openings are provided in the upper cylinder 8A and the lower cylinder 8B, and the openings form cylinder chambers 14a, 14b having the same diameter, and a plurality of mounting holes 22 having the same pitch diameter are provided around the cylinder chambers 14a, 14b. … The mounting hole 22 on the upper cylinder 8A side is a threaded hole, and the mounting hole 22 on the lower cylinder 8B side is a through hole.

From the cylinder chambers 14a and 14b of the respective cylinders 8A and 8B, vane receiving grooves 23a and 23b having the same width and the same length are respectively designed radially outward. Since the vane receiving grooves 23a, 23b are formed by, for example, broaching, longitudinal holes 24a, 24b for withdrawing broaches are also provided at the ends of the two receiving grooves.

The horizontal hole 25 is designed only on the cylinder 8A, and the horizontal hole 25 communicates with the vertical hole 24a of the outer peripheral surface and the vane receiving groove 23a. A coil spring 26 serving as an elastic member of the pressing body is housed in the horizontal hole 25 . The outer diameter of this cylinder 8A is substantially the same as the inner diameter of the above-mentioned closed case 1 .

Further, as shown in FIG. 1 , the outer peripheral portion of the upper cylinder 8A is embedded and fixed on the inner wall surface of the closed casing 1 . In this state, one end of the coil spring 26 is in contact with one side wall of the vane 15 a received in the vane receiving groove 23 a, and the other end is in contact with the inner wall of the closed casing 1 .

The coil spring 26 elastically presses the vane 15a toward the eccentric roller 13a. When the front end edge of the vane 15a forms a semicircle in plan view and has almost no sliding resistance with the circular eccentric roller 13a wall in plan view, the vane 15a is always in line with the eccentric roller 13a no matter how much the rotation angle of the eccentric roller 13a is. touch.

Therefore, if the eccentric roller 13a rotates eccentrically along the inner peripheral wall of the cylinder chamber 14a, the vane 15a reciprocates along the vane receiving groove 23a.

Further, as shown in FIG. 2, a plurality of gas discharge holes 27 are formed in the upper cylinder 8A with a pitch diameter larger than the diameter of the pitch circle of the above-mentioned mounting holes 22, respectively.

On the other hand, the outer diameter of the lower cylinder 8B is smaller than that of the upper cylinder 8A. In fact, it is only necessary to have the minimum outer diameter that can provide the mounting hole 22 and the vane receiving groove 23b, and the outer periphery thereof is eccentric with respect to the opening forming the cylinder chamber 14b.

The vane 15b is slidably accommodated in the vane receiving groove 23b, and the vane 15b has the same size as the vane 15a provided on the upper cylinder 8A. The pressing body that presses the vane 15b toward the eccentric roller 13b side is high-pressure gas that is compressed by the upper and lower cylinders 8A, 8B and discharged into the closed casing 1 .

Then, when the control unit 40 sends an operation signal to the motor 3 through the frequency converter 30, the rotating shaft 4 is driven to rotate, and the eccentric rollers 13a, 13b provided on the upper and lower cylinders 8A, 8B rotate eccentrically in the cylinder chambers 14a, 14b. .

As shown in FIG. 3(A), on the upper cylinder 8A, since the vane 15a is usually elastically pushed by the coil spring 26, the front end edge of the vane 15a is in sliding contact with the peripheral wall of the eccentric roller 13a, and the cylinder chamber 14a is Divided into two parts.

When the rotational contact position of the eccentric roller 13a and the inner peripheral wall of the cylinder chamber 14a and the contact position of the vane 15a and the eccentric roller are approximately at the same position, in this state, the spatial volume of the cylinder chamber 14a reaches the maximum. Refrigerant gas, that is, R410A gas which is a low-pressure HFC mixed refrigerant, is sucked from the accumulator 17 through the suction pipe 16a and fills the cylinder chamber 14a.

Along with the eccentric rotation of the eccentric roller 13a, the rotational contact position of the eccentric roller 13a on the inner peripheral wall of the cylinder chamber 14a moves, so that the contact position of the blade 15a and the eccentric roller from the rotational contact position of the cylinder chamber 14a along the rotational direction The volume of the cylinder chamber in between is reduced. That is, the gas introduced into the cylinder chamber 14a until then is gradually compressed.

As the rotating shaft 4 continues to rotate, the capacity of the cylinder chamber 14a is further reduced, so that the introduced gas is compressed to a specified pressure, and then the discharge valve not shown in the figure is opened, and the high-pressure gas is discharged into the cylinder through the valve cover a. And fill the closed casing 1 . The high-pressure gas that is full of the closed casing 1 is discharged through the outlet pipe 18 on the top of the closed casing.

In addition, when the motor 3 is just started, the amount of high-pressure gas compressed in the cylinder chamber 14a and discharged into the closed casing 1 is very small, and the closed casing is not in a completely high-pressure state.

Therefore, in the lower cylinder 8B, there is no high-pressure gas that presses and applies force to the vane 15a. As shown in Figure (A), the eccentric roller 13b rotates in the cylinder chamber 14b, and the vane 15b is completely received in the receiving groove 23b, and its front edge is not pressed against the eccentric roller and protrudes into the cylinder chamber.

It can be said that on the lower cylinder chamber 14b, the eccentric roller 13b only performs idle rotation, and the cylinder chamber has no compressive action at all.

After the set time has elapsed, the amount of high-pressure gas discharged from the upper cylinder chamber 14b increases to reach the high-pressure condition set in the closed casing 1 . Thus, the vane 15b provided on the lower cylinder 8B is subjected to a large back pressure, and as shown in FIG.

Therefore, even in the lower cylinder chamber 14b, the compression action as described above starts. In the upper cylinder chamber 14a, the compression effect continues. Thereafter, until the operation is stopped, since the high pressure is maintained in the closed casing 1, the compression operation in the lower cylinder chamber 14b will also continue.

As shown in Figure 1, the high-pressure gas discharged from the closed casing 1 through the outlet pipe 18 is condensed and liquefied in the condenser 19, adiabatically expanded in the expansion mechanism 20, and the latent heat of evaporation of the heat exchange air is taken away in the evaporator 21 , so as to achieve the effect of cooling. The evaporated refrigerant is guided to the accumulator 17 for gas-liquid separation, and then sucked into the compression mechanism part 2 of the compressor through the suction pipes 16a and 16b to perform the above cycle.

In addition, when it is desired to advance the time when the lower cylinder chamber 14b starts to compress, the control unit 40 can be used to control the frequency converter 30 to increase the rotational speed of the rotating shaft 4 from the beginning of operation, so that the pressure in the housing can rise to the set value in a short time. pressure.

On the contrary, when it is desired to delay the starting time of the operation, the frequency converter 30 can be controlled by the control unit 40 to reduce the rotation speed of the rotating shaft 4 from the beginning of the operation, and it takes a certain time for the pressure in the casing to rise to the set pressure. Furthermore, it is also possible to increase the rotational speed after considering that the protruding action of the vane 15b into the lower cylinder chamber 14b is completed.

The vane 15b on the side of the lower cylinder chamber 14b protrudes using the pressure difference between the inside of the closed casing 1 and the lower cylinder chamber 14b, and is located on the low pressure side of the system before the compression in the lower cylinder chamber 14b starts. However, if the pressure in the casing is 0.1 megapascal (MPa) higher than the pressure in the cylinder chamber, it is almost equivalent to the thrust of the coil spring 26 that pushes the vane 15a into the upper cylinder chamber 14a, so that the vane 15b can protrude and follow the eccentricity. Rotational movement of roller 13b.

Normally, the pressure to protrude the vane 15b to the lower cylinder chamber 14b can be generated within a few seconds with a commercial power supply (50/60Hz), and within a maximum of 10 seconds with a variable frequency power supply starting from 10Hz.

Therefore, it is completely feasible functionally to use the high-pressure gas of the closed casing 1 as the pushing force device to push and force the vane 15b to the lower cylinder chamber 14b.

By the way, under the condition that the operation continues and the system is stable, the pushing force of the pressure in the casing on the vane 15b is tens of times that of the pushing force (elastic force) of the coil spring 26 on the upper cylinder 8A, Originally, from a functional point of view, the coil spring may not be needed, but it will increase some workload.

In addition, in the compressor of the present invention, only one cylinder (here, the upper cylinder 8A) produces compression when starting, so the load on sliding members such as the rotating shaft 4 is reduced by half. That is to say, on an air conditioner with a large amount of refrigerant, if a large amount of liquid refrigerant is sucked into the cylinder chamber for liquid compression at the time of starting according to the operating conditions, it is easy to cause damage to the sliding components.

According to the structure of the present invention, since the load on the sliding member is reduced, damage to the member can be prevented. Also, the accumulator 17, which is often used on such rotary compressors, can also be removed.

In any case, at least on the lower cylinder 8B that utilizes the high-pressure gas in the closed casing 1 as the pushing and applying device for pushing and applying force to the blade 15b, there is no need to design the horizontal hole 25 for inserting the coil spring 26, Therefore, even if the wall thickness of the cylinder is thin, the rigidity can be increased, and the deformation of the vane housing groove 23b can be minimized.

In addition, the rapid flying of the above-mentioned vane 15b is the main cause of collision noise between the eccentric roller 13b and the vane, so it is preferable to avoid rapidly increasing the operating frequency. As a means of avoiding the rapid rise of the pressure in the casing, such a method can be adopted: the frequency converter 30 is controlled by the control unit 40, so that the operating frequency of the motor 3 is relatively low when starting, and the pressure in the casing must reach a high pressure state after a period of time. Slow down the protruding speed of the blade 15b, and then increase the operating frequency. In addition, it is also effective to reduce the throttling action of the expansion valve constituting the expansion mechanism 20, to open a defrosting valve not shown in the figure, and the like.

In the above-mentioned embodiment, the upper cylinder 8A is provided with a coil spring 26 as a pushing device for pushing the vane 15a so that the outer peripheral portion of the upper cylinder is embedded on the inner peripheral wall of the closed casing 1, while the lower cylinder 8B utilizes the inner peripheral wall of the closed casing to The high-pressure gas serves as the pushing means for pushing the blade 15b. However, the present invention is not limited to this form, and may be configured as follows.

That is, a rotary hermetic compressor is configured as shown in FIG. 4 . Compared with the compressor described above in FIG. 1 , only the pressing means of the upper cylinder 80A pressing the vane 15 a and the pressing means of the lower cylinder 80B pressing the vane 15 b are different as described below.

Although there are some differences in the detailed structure on the drawings, they are basically composed of the same components, so the same symbols are used and no further description is given. Moreover, the structures of the electrical control and the refrigeration cycle are the same as those described above, so descriptions are omitted here.

The upper cylinder 80A is in a form as shown in FIG. 5(A) plan view. That is, the cylinder chamber 14a and the concentric circular cylinder body 80a are formed as a circular opening.

A substantially fan-shaped first edge portion 80b having a relatively large area protrudes integrally from a part of the peripheral surface of the cylinder body 80a. Further, a substantially rectangular second edge portion 80c having a smaller area than the first edge portion protrudes at a position substantially 180° from the center of the first edge portion 80b.

The outer peripheral surface of the first edge portion 80b and the outer peripheral surface of the second edge portion 80c are concentric with the cylinder chamber 14a and the cylinder body 80a and formed in an arc having the same radius as the inner periphery of the closed case 1 .

The cylinder body 80a is provided with a vane receiving groove 23a that opens to the cylinder chamber 14a and accommodates the vane 15a. Moreover, a longitudinal hole 24a is designed on the boundary portion between the cylinder body 80a and the first edge portion 80b as a tool relief hole during machining of the vane receiving groove 23a.

In addition, a plurality of mounting bolt holes 22 are designed at predetermined positions of the cylinder body 80a for fixing the main bearing 9 to the upper cylinder 80A via bolts 10 .

The lower cylinder 80B is in a form as shown in FIG. 5(B) plan view. That is, the cylinder chamber 14b and the concentric circular cylinder body 80a are formed as a circular opening. A substantially rectangular edge 80d protrudes from a part of the peripheral surface of the cylinder body 80a.

On the cylinder body 80a, a vane accommodating groove 23b opening on the cylinder chamber 14b and for accommodating the vane 15b is designed. Moreover, a longitudinal hole 24b is designed on the boundary between the cylinder body 80a and the edge portion 80d as a tool relief hole during machining of the vane receiving groove 23b.

Furthermore, a horizontal hole 25 is designed in the middle of the vertical hole 24b to communicate with the above-mentioned vane receiving groove 23b. In this horizontal hole 25, a coil spring 26, which is an elastic member serving as a urging force means, is inserted. Also, the end of the horizontal hole 25 is closed by a cover body 28 shown only in FIG. 4 .

In addition, a plurality of through holes 22 are designed at predetermined positions of the cylinder body 80a for fixing the lower cylinder 80B, the partition plate 7 and the auxiliary bearing 11 to the upper cylinder 80A through bolts 12 .

Again as shown in Figure 4, the outer peripheral portion of the upper cylinder 80A is embedded on the inner peripheral wall of the closed casing 1, therefore, although not shown in the figure, especially in the aforementioned cylinder body 80a, the first edge 80b , the second edge portion 80c, and the inner peripheral wall of the closed case 1, a space portion for gas discharge is formed.

And the eccentric roller 13a can freely eccentrically rotate and be contained in the cylinder chamber 14a, the vane 15a is received in the vane accommodating groove 23a, owing to utilize the high-pressure gas in the closed housing 1 as the device of pushing this vane, so except the vane There are no other components to load.

The eccentric roller 13b is freely eccentrically mounted in the cylinder chamber 14b of the lower cylinder 80B, and the vane 15b is received in the vane receiving groove 23b. The vane 15b is elastically urged by the coil spring 26 and contacts the peripheral wall surface of the eccentric roller 13b.

In the rotary hermetic compressor thus constituted, immediately after the motor 3 is started, the amount of high-pressure gas compressed in the lower cylinder chamber 14b and discharged into the closed casing 1 is small, and the closed casing is not in a completely high-pressure state.

Therefore, on the upper cylinder 80A, there is no high-pressure gas that presses the vane 15a. Although the eccentric roller 13a rotates in the cylinder chamber 14a, because the vane 15a is completely received in the vane receiving groove 23a, its front edge does not move toward the vane 15a. The cylinder chamber protrudes and presses on the roller, so the eccentric roller 13a is actually just idling, and the cylinder chamber 14a has no compression effect at all.

After the set time has elapsed, the amount of high-pressure gas discharged from the lower cylinder chamber 14b increases, and the set high-pressure condition is reached in the closed casing 1 . At this time, the vane 15a provided on the upper cylinder 80A is subjected to a large back pressure, and the vane is pressed to contact the peripheral wall of the eccentric roller 13a.

Therefore, also in the upper cylinder chamber 14a, the compression action as previously described starts. In the lower cylinder chamber 14b, the compression effect continues. Thereafter, until the operation is stopped, since the high pressure is maintained in the closed casing 1, the compression work in the upper cylinder chamber 14a will also continue.

In addition, regardless of the compressor shown in FIG. 1 or FIG. 4, the backs of the blades 15a, 15b that are pushed and exerted by the high-pressure gas in the closed casing 1 can be designed in the form shown in FIG. 6 or 7.

Beginning with Fig. 6, when the radius of the longitudinal holes 24a, 24b used as the relief holes for machining the vane receiving grooves is set as Rc, the back sides of the ends of the vanes 15a, 15b near the longitudinal holes are shaped like arcs in section. The radius of the arc is Rv. Furthermore, the radius Rv of the circular arc of the cross section of the blades 15a and 15b is smaller than the radius Rc of the vertical hole (Rv<Rc).

In particular, from the time when the vane pushed by the pressure in the housing starts to start, until the difference between the pressure in the housing and the cylinder chamber reaches 0.1 MPa in a very short time, due to the gap between the front end of the vane and the surrounding wall of the eccentric roller, And intermittent contact occurs between the back of the blade and the peripheral surface of the longitudinal hole, which may generate intermittent noise.

If utilize the structure of Fig. 6, the front end portion of blade 15a, 15b is the mutual contact of circular arc surface of course, also is the mutual contact of circular arc surface at the back, so, can further suppress the generation of intermittent noise. In addition, the vanes and cylinders made of brittle materials do not form gaps or damage, and can prevent the vanes from clogging with the cylinder.

Next, Fig. 7 will be described. Here, the radii of the vertical holes 24a, 24b may be predetermined radii. However, the two edges on the back of the blades 15a and 15b are designed as arcs with a radius of 1mm or less.

Therefore, since the back surfaces of the blades 15a and 15b are in contact with each other on the arcuate surfaces, generation of intermittent noise can be further suppressed. In addition, the vanes and cylinders made of brittle materials do not form gaps or damage, and can prevent the vanes from clogging with the cylinder.

In addition, although the above-mentioned embodiment described relates to a 2-cylinder type compressor provided with 2 cylinder chambers, it is not limited to this, and it is also applicable to a multi-cylinder rotary hermetic compressor having 2 or more cylinders.

As mentioned above, if the invention of Scheme 1 is adopted, since at least one device for pushing the blades uses an elastic member, and at least one device for pushing the blades uses high-pressure gas in a closed casing, the use of high-pressure gas is reduced. Gas is used as the number of parts on the cylinder side of the vane pressing device, which has the effect of simplifying the processing.

According to the invention of Claim 2, the elastic member for pressing the vane of at least one cylinder can be eliminated, thereby reducing the set outer diameter of the cylinder.

According to the invention of claim 3, the assembly of the compression mechanism can be expected to be simplified.

If the invention of scheme 4 is adopted, the length of the groove for accommodating the vanes can be shortened, so that the outer diameter of the cylinder can be reduced.

If the invention of Scheme 5 is adopted, HFC mixed refrigerants, especially high-pressure refrigerants such as R410A, can be used.

According to the invention of Claim 6, the collision noise between the vane and the cylinder can be eliminated on the cylinder side where the vane pushing means is made of high-pressure gas.

According to the invention of Claim 7, the assembly of the compression mechanism part can be expected to be simplified.

If the inventions of scheme 8 and scheme 9 are adopted, since the blades and the cylinder are in smooth contact, generation of intermittent noise can be suppressed.

If the invention of Claim 10 is adopted, it is expected to reduce the number of components in the refrigeration cycle system, especially the compressor, and reduce the assembly process.

Claims (10)

1, a kind of rotary sealed compressor, this compressor is equipped with motor and the rotary compressor structure portion that is connected with this motor in enclosing housing, in a single day gas by the compression of above-mentioned compressor structure portion be discharged in the enclosing housing, promptly become high pressure conditions in the enclosing housing, it is characterized in that: above-mentioned compressor structure portion is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder, and blade is located in these cylinders, owing to be subjected to pushing the pushing of force application device, the side face of its front end and above-mentioned eccentric roller joins, and will be divided into two chambers in the cylinder along the sense of rotation of eccentric roller; The pushing force application device of above-mentioned pushing blade is the pressurized gas in resilient member and the enclosing housing.

2, rotary sealed compressor as claimed in claim 1.It is characterized in that: adopt the interior pressurized gas of enclosing housing to design forr a short time as the cylinder outside dimension of above-mentioned pushing force application device than adopting resilient member as the cylinder external diameter of above-mentioned pushing force application device.

3, rotary sealed compressor as claimed in claim 1 is characterized in that: adopt the cylinder of resilient member as above-mentioned pushing force application device, its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing.

4, as each described rotary sealed compressor of claim 1～3, it is characterized in that: above-mentioned resilient member as the pushing force application device is a helical spring.

5, rotary sealed compressor as claimed in claim 1 is characterized in that: the high refrigeration agent of the compression work pressure ratio R22 of above-mentioned compressor structure portion.

6, rotary sealed compressor as claimed in claim 1, it is characterized in that: above-mentioned motor is electrically connected with frequency variator that can change operation frequency and control gear, utilize control gear, be low operating frequency in the time of can making starting, and be high operating frequency when head pressure rises to setting pressure.

7, rotary sealed compressor as claimed in claim 1 is characterized in that: adopt the cylinder of the interior pressurized gas of enclosing housing as above-mentioned pushing force application device, its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing.

8, rotary sealed compressor as claimed in claim 1, it is characterized in that: will be subjected to the blade of enclosing housing inner high voltage gas pushing in the above-mentioned blade, it is the shape of circular arc that its back side forms section, and its circular arc radius R v than to the vacuum side of blade setting and as the processing of blade receiving groove with the little (Rv＜Rc) of the inside radius Rc in withdrawing hole.

9, rotary sealed compressor as claimed in claim 1.It is characterized in that: be subjected to the blade of enclosing housing inner high voltage gas pushing in the above-mentioned blade, the digonous part in its back side is carried out the chamfer machining of radius below 1mm.

10, a kind of refrigerating circulatory device, rotary sealed compressor wherein, motor and the rotary compressor structure portion that is connected with this motor are housed in enclosing housing, and in a single day the gas that is compressed by above-mentioned compressor structure portion be discharged in the enclosing housing, promptly becomes high pressure conditions in the enclosing housing; It is characterized in that: its refrigeration cycle is made of rotary sealed compressor, condenser, expansion mechanism and vaporizer,

The above-mentioned compressor structure portion of rotary sealed compressor is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder, and blade is located on these cylinders, owing to be subjected to pushing the pushing of force body, the side face of its front end and above-mentioned eccentric roller joins, and will be divided into two chambers in the cylinder along the sense of rotation of eccentric roller;

The pushing force body of at least 1 pushing blade is to adopt resilient member, and the pushing force body of at least 1 pushing blade adopts the pressurized gas in the enclosing housing.

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