JPS62218680A - Compressor - Google Patents

Abstract

PURPOSE:To reduce power needed to drive a rolling piston by arranging rolling pistons and vanes respectively in a plurality of cylinder chambers and affording communication between a discharge port and intake ports in the other cylinder chambers. CONSTITUTION:Rolling pistons 153-159 and rotors 111-117 are provided in a plurality of cylinder chambers 131-137. A discharge port in one cylinder chamber communicates to intake ports in the other cylinder chambers and is arranged in series. Thus, working fluid in the discharge is compressed to a predetermined amount of high pressure and the phases of respective processes in a plurality of cylinder chambers are deviated from each other so that the fluctuation of torque needed to drive the rolling piston is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a compressor, and is effective for use as a refrigerant compressor in, for example, an automobile air conditioner.

[Conventional technology]

Conventionally, a cylinder chamber was formed in the housing, a rolling piston was rotatably disposed in the cylinder chamber, the center of rotation of the rolling piston was eccentric from the central axis of the cylinder chamber, and the cylinder chamber was partitioned by vanes. , the so-called rotasco type compressor was known.

In addition, in this type of rotasco type compressor, it is also possible to form a plurality of cylinder chambers, for example, in Japanese Patent Application Laid-Open No. 53-10
This was known in Japanese Patent No. 3212, etc.

However, this type of conventional compressor sucks working fluid into the cylinder chamber, and after discharging it into the cylinder chamber,
It was designed to be discharged directly to the outside of the compressor. Therefore, even if a plurality of cylinder chambers are formed, the refrigerant discharged from each cylinder chamber is similarly high-pressure, making it impossible to reduce the discharge pulsation. Further, in each cylinder, the working fluid must be compressed at once from the low pressure of the inhaler to a predetermined high pressure, and a large amount of power is required to drive the rolling piston at that time.

[Problems to be solved by the present invention]

The present invention was devised in view of the above points, and an object of the present invention is to reduce the power required to drive the rolling piston in each cylinder chamber in a compressor having a plurality of cylinder chambers. In addition, the compressor of the present invention aims to perform the compression process smoothly and to moderate fluctuations in the torque required to drive the compressor.

[Configuration and operation]

In order to achieve the above object, in the present invention, a plurality of cylinder chambers are provided in a housing, and a rolling piston and a vane are arranged in each cylinder chamber. Therefore, each cylinder chamber can perform a suction compression action. moreover,
A configuration is adopted in which the discharge hole of one of the plurality of cylinder chambers is communicated with the suction hole of the other cylinder chamber. Further, a suction passage for sucking working fluid from the outside is connected to the suction hole of the most upstream cylinder chamber among the plurality of cylinder chambers.

Further, among the plurality of cylinder chambers, the discharge hole of the most downstream cylinder chamber can communicate with a discharge passage that discharges the working fluid to the outside.

Therefore, in the compressor of the present invention, the working fluid is first compressed to a predetermined amount in the most upstream cylinder chamber among the plurality of cylinder chambers. Next, the working fluid compressed in the cylinder chamber is discharged to the adjacent second cylinder chamber. In this state, the working fluid compressed in the upstream cylinder chamber and having a predetermined amount of high pressure is sucked into the adjacent cylinder chamber.

Then, in the second cylinder chamber, the gas is further compressed to a predetermined amount, and then discharged to the next adjacent cylinder chamber. In this way, a plurality of cylinder chambers are provided, and the refrigerant compressed by the upstream cylinder chamber is sucked into the high-flow side cylinder chamber, and is further compressed in that state. In this way, compression is performed for a while, and the working fluid compressed in the most downstream cylinder chamber is then projected outward from the compressor.

〔Effect of the invention〕

Therefore, in the compressor of the present invention, each of the plurality of cylinder chambers may require a relatively small amount of pressure wJ. Even if the compression in each cylinder chamber is relatively small, since a plurality of cylinder chambers are arranged in series, the working fluid is compressed to a high pressure to a predetermined amount when discharged from the compressor.

Furthermore, in the compressor of the present invention, since the suction process and the compression process in each of the plurality of cylinder chambers are out of phase,
Overall, the variation in torque required for rolling piston drive is extremely small.

〔Example〕

An embodiment of the compressor of the present invention will be described below based on the drawings.

In FIG. 1, a case 101 is formed of aluminum alloy into a cylindrical shape with a bottom, and inside this case 101 are a front housing 119, a ml cylinder housing 161,
A first connecting portion housing 187, a second cylinder housing 163, a second connecting portion housing 189, a third cylinder housing 165, a third connecting portion housing 191, a fourth cylinder housing 167, and a rear housing 185 are provided.

The first cylinder housing 161, the second cylinder housing 163, the third cylinder housing 165, and the fourth cylinder housing 167 each have a first cylinder chamber 1
31, second cylinder chamber 133, third cylinder chamber 135,
A fourth cylinder chamber 137 is formed. Each cylinder chamber has a cylindrical shape. In each cylinder chamber, there is a 10th ring piston 153 and a 2nd ring piston 153.
0-ring piston 155, 30th-ring piston 1
57 and a 40th ring piston 159 are rotatably arranged. That is, the tenth ring piston 153
, the 20th ring piston 155, the 30th ring piston 157, and the 40th ring piston 159 are the 10th ring piston 111, the 20th ring piston 113, and the 30th ring piston 159, respectively.
115 and the 40th tab 117.

Also, the 10th-ta 111, the 20th-ta 113, the 30th-ta
The shaft 115 and the 40th shaft 117 are respectively
It is fixed to 09.

The shaft 109 is rotatably supported by a bearing 145 disposed on the front housing 119 and a bearing 147 disposed on the rear housing 185. Also,
An electromagnetic clutch (not shown) is provided at the tip of the shaft 109. The driving force of a vehicle engine (not shown) is transmitted through this electromagnetic clutch.

Therefore, the shaft 109 receives the driving force and rotates within the housing. And this shaft 109
The rotation is transmitted to the tenth ring piston 153 via the tenth ring piston 111. Similarly, it is transmitted to the 20th ring piston 155 via the 20th ring piston 113. 30th-
The signal is transmitted to the 30th ring piston 157 via the rotor 115. and is transmitted to the 40th ring piston 159 via the 40th ring piston 117. Therefore, the 10th ring piston, the 20th ring piston 155, the 30th ring piston 157, and the 40th ring piston 15
7 rotates within the cylinder chamber due to the rotation of the shaft 109. Note that the center of rotation of the shaft 109 coincides with the central axes of the first cylinder chamber, the second cylinder chamber 133, the third cylinder chamber 135, and the fourth cylinder chamber 137.

That is, the shaft 109 and the cylinder chamber are arranged concentrically. However, the 10th-ta 111, the 20th
-ta 113, 30th ta 115, and 40th ta 117
are arranged eccentrically from the shaft 109, so the 10th ring piston 153, the 20th ring piston 155, the 30th ring piston 157, and the 40th ring piston 159 are located in the first cylinder chamber 131, respectively.
It rotates eccentrically within the second cylinder chamber 133, third cylinder chamber 135, and fourth cylinder chamber 137. Therefore, the first cylinder chamber I31, the second cylinder chamber 133
, the volumes of the third cylinder chamber 135 and the fourth cylinder chamber 137 vary according to the rotations of the 10th ring piston 153, the 20th ring piston '155, the 30th ring piston 157, and the 40th ring piston 159. I will do it.

Note that the first cylinder chamber 131, the second cylinder chamber 133,
As shown in FIG. 2, a first vane 193, a second vane 195, a third vane 197, and a fourth vane 199 are arranged in the third cylinder chamber 135 and the fourth cylinder chamber 137, By the first vane 193, second vane 195, third vane 197, and fourth vane 199, respectively,
The space is divided into two.

Further, as shown in FIG. 2, each cylinder chamber has a suction hole and a discharge hole opened therein.

The first suction hole 169 that opens into the first cylinder chamber 131 is
is formed in the front housing 119, and this first
The suction chamber 141 and the first cylinder chamber 13 are connected by the suction chamber 169.
1 is communicated with. A first discharge port 177 that opens into the first cylinder chamber 131 communicates with a second suction port 171 that opens into the second cylinder chamber 133 via a first communication passage 209 . Note that the first communication path 209 is formed in the third discharge port 181.

Similarly, the second discharge port 1 opens into the second cylinder chamber 133.
79 and the third suction chamber 17 that opens into the third cylinder chamber 135.
3 through a second communication path 211. Second
The communication path 211 is formed within the second connection housing 189. Further, the third discharge port 181 that opens into the third cylinder chamber 135 and the fourth suction hole 175 that opens into the fourth cylinder chamber 137 communicate with each other through the third communication passage 213 .

The third communicating passage 213 is formed within the third connecting portion housing 191. Further, a fourth discharge port 183 that opens into the fourth cylinder chamber 137 is formed in the rear housing 185, and the fourth cylinder chamber and the discharge chamber 139 communicate with each other through the fourth discharge port 183.

Note that the first vane 193, the second vane 195, the third vane 197, and the fourth vane 199 are connected to the tenth ring piston 153 and the twentieth ring piston by the spring 151, respectively.
- ring piston 155, 30th - ring piston 15
7. The 40th link is pressed toward the piston 159 side.

Next, the operation of the compressor having the above configuration will be explained based on FIG. 2. FIG. 2 is a schematic diagram showing the state of each cylinder chamber.

Further, the phases of the rolling piston in each cylinder chamber are shown at 0 degrees, 90 degrees, 180 degrees, and 270 degrees.

First, the first cylinder chamber 131 will be explained.

The first cylinder chamber 131 is 90 degrees and 180 degrees from the 0 degree phase.
Compression is performed in the first chamber 217 toward a state of 270 degrees, and at the same time suction is performed in the second chamber 219.

The first chamber 217 is 90 degrees to 180 degrees, and the 10th chamber is 270 degrees.
- As the ring piston 153 rotates, its volume decreases. With this volume reduction, the internal refrigerant is compressed,
It is discharged from the first discharge port 177.

Conversely, the second chamber 219 is 90 degrees, 180 degrees, 270 degrees and the first
As the O-ring piston 153 rotates, it increases its volume. As the volume increases, refrigerant is introduced into the second chamber 219 from the first suction hole 169.

When the phase of the first cylinder chamber 131 is 0 degrees, the phase of the second cylinder chamber 133 is shifted by 270 degrees. Therefore, when the 10th ring piston 153 and the 20th ring piston 155 are rotated 90 degrees, The refrigerant discharged from the first chamber 217 is transferred to the second chamber 21 of the second cylinder chamber 133.
introduced in 9.

In this state, the refrigerant is compressed to a predetermined amount in the first chamber 217 of the first cylinder chamber 131, so the compressed refrigerant is introduced into the second chamber 219 of the second cylinder chamber 133. . Therefore, the second cylinder chamber 133
A larger amount of refrigerant is introduced into the second chamber 219 than its volume. This state is the same in the state in which the 10th ring piston 153 and the 20th ring piston 55 are rotated by 180 degrees, and in the state in which they are rotated by 270 degrees.

For example, when the 10th ring piston 153 and the 20th ring piston 155 are rotated 270 degrees, the first
The pressure in the first chamber 217 of the cylinder chamber 131 is the highest, so even if the volume of the second chamber 219 in the second cylinder chamber 133 is the maximum, the pressure in the first chamber 217 of the first cylinder chamber 131 is the highest. The high-pressure refrigerant in the chamber 217 is discharged toward the second chamber 219 in the second cylinder chamber 133.

A similar operation is also achieved between the second cylinder chamber 133 and the third cylinder chamber 135. That is, the high-pressure refrigerant compressed in the first chamber 217 in the second cylinder chamber 133 is further introduced into the second chamber 219 in the third cylinder chamber 135 . As a result, the refrigerant is further compressed in the third cylinder chamber 135. Similar compression is achieved in the fourth cylinder chamber 137 as well.

Therefore, the refrigerant discharged from the fourth cylinder chamber 137 has the highest pressure. and,
In this high pressure state, the discharge chamber 1 is discharged from the fourth discharge port 183.
39 is discharged. The refrigerant discharged into the discharge chamber 139 is discharged toward the condenser of the refrigeration cycle via the discharge pipe 107, as described above. Although not shown, a discharge valve is provided at the fourth discharge port 183 of the fourth cylinder chamber 137.

Note that in the refrigeration cycle, lubricating oil is mixed into the refrigerant. Therefore, the refrigerant sucked into the compressor contains a predetermined amount of lubricating oil. During compression in this compressor, the lubricating oil contained in the refrigerant is transferred to the 10th ring piston 153, the 20th ring piston 155,
30th ring piston 157, 40th ring piston 159, first vane 193, second vane 195
, the third vane 197, and the fourth vane 199. The lubricating oil is separated from the discharged refrigerant in the discharge chamber 139.

The lubricating oil separated in the discharge chamber 139 is supplied to sliding parts such as the bearings 147 and 145 through an oil supply hole (not shown). As is clear from FIG. 2, in the compressor of this example, the 10th tank 111, the 20th tank 113, and the 30th tank 1
The sizes of the 15th and 40th data 117 have been increasing for a while. In other words, the tenth ring piston 153
The diameter of the 20th ring piston 155 is larger, the diameter of the 30th ring piston 157 is larger than the diameter of the 30th ring piston 157, and the diameter of the 40th ring piston 157 is larger than that of the 30th ring piston 157.
The diameter of is thicker.

This means that the compression ratio to each cylinder is different.

For example, in the first cylinder chamber 131, the total compression is 4
About 0% is achieved. Approximately 30% of the total compression is achieved in the second cylinder chamber 133. Further, in the third cylinder chamber 135, about 20% of the total compression is achieved. The fourth and final cylinder chamber 137 is configured to achieve the remaining 10% compression.

In this way, since the outer diameter of the rolling piston is increased toward the cylinder chamber on the downstream side, the contact area between the rolling piston and the cylinder housing increases as the pressure of the refrigerant in the cylinder chamber increases. That is, the area of the second cylinder housing 163 facing the 20th ring piston 155 is larger than the area of the first cylinder housing 161 facing the 10th ring piston 153, and furthermore, the area of the 30th cylinder housing 163 facing the 20th ring piston 155 is larger than that of the first cylinder housing 161 facing the 10th ring piston 153. The area of the third cylinder housing 165 facing the ring piston 157 is increased.

The opposing area between the 40th ring piston 159 and the fourth cylinder housing 167 is the largest.

In this way, since there is a large opposing area, the first chamber 21
No matter how much the pressure inside the cylinder chamber increases, the leakage of the refrigerant from the cylinder chamber 7 to the second chamber 219 is effectively prevented.

In addition, rolling piston 153, 155, 157.1
59 is disposed on each rotor 111, 113, 115° 117 so as to be freely transferable. Therefore, the rotor 111,1
When pistons 13, 115, and 117 rotate, rolling pistons 153, 155, 157, and 159 revolve within the cylinder chambers without rotating. The number of revolutions of the shaft 109 is one revolution R/r rotation.

Note that R is the inner diameter of the cylinder, and r is the outer diameter of the rolling piston. That is, the number of times the rolling piston makes sliding contact increases as the outer diameter of the rolling piston becomes smaller.

However, as mentioned above, since the outer diameter of the rolling piston is small, the pressure inside the cylinder is small. Therefore, the pressure between the vane tip and the outer surface of the rolling piston may be made smaller as the outer diameter of the rolling piston is smaller toward the cylinder chamber. In other words, the rolling piston that comes into sliding contact with the vane more often has a lower contact pressure with the vane.

Therefore, irrespective of an increase in the pressure inside the cylinder, seizure at the vane tip can be effectively prevented.

As mentioned above, since the compression ratio in each cylinder chamber is different, if compression is not performed in an appropriate cylinder chamber among the plurality of cylinder chambers, the discharge requirement of the compressor can be favorably reduced. is possible.

FIG. 3 shows another embodiment.

As shown in this figure, the first vane 193, the second vane 1
95, the third vane 197, and the fourth vane 199 are provided with a first solenoid valve 201, a second solenoid valve 203, a third solenoid valve 205, and a fourth solenoid valve 207, respectively.

A voltage is applied to the first solenoid valve 201, and the first solenoid valve 201
is excited, the first vane 193 is forced into the first vane 193.
It will be retracted into the cylinder housing 161.

That is, when the first solenoid valve 201 is excited, the magnetic force of the first solenoid valve 201 exceeds the setting and force of the spring 151, and the first vane 193
It will not be discharged to the side. Therefore, the first solenoid valve 20
1 is energized, simply the 10th ring piston 1
53 idles inside the first cylinder housing 161.

Similarly, when the second electromagnetic valve 203 is energized, the second vane 195 is retracted into the second cylinder housing 163, and the 20th ring piston 155 idles within the second cylinder chamber 133. Similarly, when the third electromagnetic valve 205 is excited, the 30th ring piston 157 idles within the third cylinder chamber 135. Similarly, when the fourth solenoid valve 207 is energized, the 40th ring piston 159 idles within the fourth cylinder 137.

Therefore, among the four solenoid valves, for example, the first solenoid valve 20
In a state where voltage is applied only to cylinder 1, compression is performed in second cylinder chamber 133, third cylinder chamber 135, and fourth cylinder chamber 137. Therefore, in this state, compression is not performed in the first cylinder chamber 131, and therefore the overall compression ratio is reduced by about 40%.

When both the first solenoid valve 201 and the second solenoid valve 203 are excited at the same time, compression is not performed in the first cylinder chamber 131 and the second cylinder chamber 133. In this state, compression is performed only in the third cylinder chamber 135 and the fourth cylinder chamber 137, and therefore the compression ratio is reduced by about 70%.

Furthermore, the third solenoid valve 205 is also energized, and the first solenoid valve 205 is also energized.
01, the second solenoid valve 203, and the third solenoid valve 205 are energized, compression is performed only in the fourth cylinder chamber 137, and therefore the compression capacity is reduced to 10%.

In this way, there are four valves at li +1, and by applying voltage to appropriate electromagnetic valves, it is possible to change the discharge capacity of the compressor as appropriate.

There are other types of variable displacement compressors. In the example shown in FIG. 3, the first vane 193 and the second vane 195
, the third vane 197, and the fourth vane 199, or all of them can be retracted into the housing to change the discharge capacity of the compressor. The discharge capacity of the compressor may be controlled by switching the three-way passage 213.

Further, in the above example, the tenth ring piston 153,
The 20th ring piston 155, the 30th ring piston 157, and the 40th ring piston 159 are the 10th ring piston 111, the 20th ring piston 113, and the 30th ring piston 159, respectively.
It is directly connected to the shaft 109 via the 15th and 40th pistons 117, and therefore the 10th ring piston 15
3. The 20th ring piston 155, the 30th ring piston 157, and the 40th ring piston 159 were designed to rotate at the same rotational speed, but by making the rotational speeds different from each other. Good too.

That is, a reduction mechanism is provided between the shaft 109 and the 20th motor 113, the 30th motor 115, and the 40th motor 117, and the rotational speeds of the 10th motor 111 and the 20th motor 113 are made different. You can do it like this.

Of course, in this case, the 10th-taper 111 and the 20th-taper 1
Not only 13, but also 10th 111 and 20th 113
The rotation speeds of the 30th motor 115 and the 40th motor 117 are mutually changed.

By slowing down the rotational speed of the cylinder chamber on the downstream side, that is, on the high pressure side, the driving force of the compressor as a whole can be more balanced.

Further, in the above example, four cylinder chambers were provided, but the number of cylinder chambers is of course not limited to four, and may be any number as long as it is a plurality of chambers.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing one embodiment of the compressor of the present invention, FIG. 2 is an explanatory diagram for explaining the operation of the compressor shown in FIG. 1, and FIG. 3 is a sectional view showing another embodiment of the compressor of the present invention. It is an explanatory diagram. 109...Shaft 111...10th evening, 11
3...20th evening, 115...30th evening, 117
...40th-ta, 119...front housing,
131...first cylinder chamber, 133...second cylinder chamber. 135...Third cylinder chamber, 137...Fourth cylinder chamber, 153...10th ring piston, 155...
...20th ring piston, 157...30th ring piston, 159...40th ring piston. +61...First cylinder housing, 163...Second cylinder housing, 165...Third cylinder housing, 167...Fourth cylinder housing, 185
...Rear housing, 193...First vane, 19
5...Second vane, 197...Third vane, 199
...Fourth vane.

Claims (1)

[Scope of Claims] A housing having a plurality of cylindrical cylinder chambers therein, and a plurality of housings rotatably disposed within each cylinder chamber in the housing, the center of rotation of which is eccentric from the central axis of the cylinder chamber. a rolling piston; a shaft that rotationally drives the plurality of rolling pistons; a plurality of vanes disposed in the housing so as to be able to protrude into the plurality of cylinder chambers; A suction passage that introduces working fluid into a suction hole formed in a side cylinder chamber, a discharge passage that leads discharge fluid from a discharge hole on the most downstream side among the plurality of cylinder chambers, and a plurality of cylinders in the housing. A plurality of suction holes and a plurality of discharge holes formed to open with each of the cylinder chambers, and a communication passage connecting one discharge hole and the suction hole of another cylinder chamber among the cylinder chambers. Compressor features.