JPH05172076A - Multicylinder rotary compressor - Google Patents

Abstract

PURPOSE:To reduce the loss of compressing leakage gas so as to enable highly efficient operation of a multicylinder rotary compressor even during capacity control by bypassing a delivery portion and the suction side of the compressor by means of a valve mechanism even if gas leaks into a stopped cylinder. CONSTITUTION:A multicylinder rotary compressor having a cylinder 3 provided with a cylinder stopping mechanism includes an opening 27 provided near a delivery portion inside the cylinder 3 provided with the cylinder stopping mechanism, a passage 29 communicating with the suction side from the opening 27, and a valve mechanism 28 for opening and closing the passage 29.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to high efficiency in capacity control operation of a multi-cylinder rotary compressor.

[0002]

2. Description of the Related Art FIGS.
It is sectional drawing of the refrigerating cycle and compressor which perform the conventional capacity control shown by 50991 gazette. A conventional capacity-controlled refrigeration cycle will be described with reference to FIGS. 12
FIG. 13 is a cycle configuration diagram showing an example of a conventional capacity control refrigeration cycle, and FIG. 13 is a sectional view showing details of the compressor in FIG. In FIG. 12, 1 is a hermetic compressor related to a compressor having a compression element 2 and a cylinder decompression element 3. The compression element 2 and the compression element 3 are, for example, unit compressors that form the hermetic compressor 1, and only the compression element 2 is used during capacity control. Compressing element discharge pipe 4
Is joined to the compression element discharge pipe 5, and is connected to the condenser 7 by the high pressure gas pipe 6. The condenser 7 is connected to an evaporator 8 via a decompressor 10 by a high pressure liquid pipe 9, and the evaporator 8 is connected to the hermetic compressor 1 by a low pressure gas pipe 11. The low pressure gas pipe 11 is connected to the compression element suction pipe 1 on the way.
2 and the compression element suction pipe 13, which are respectively connected to the compression element 2 and the compression element 3. A two-way valve 14 for capacity control is provided in the middle of the compression element suction pipe 13.
The hermetic compressor 1 will be described in more detail with reference to FIG. 5. Reference numeral 15 is a chamber in which the compression element 2 and the compression element 3 are housed. The chamber 15 also fixes and holds the motor stator 16 and the compression element cylinder block 17.

An upper bearing 18 is fixed to the upper portion of the compression element cylinder block 17, and the upper bearing 1
8 is a crankshaft 20 to which a rotor 19 of the motor is fixed
Is held in a rotatable state. The lower end of the crankshaft 20 is rotatably held by a lower bearing 22 having a compression element discharge chamber 21 therein.
Are fixed to the compression element cylinder block 17 together with the compression element cylinder block 23 and the partition plate 24. Then, the upper bearing 18, the compression element cylinder block 1
7. The compression chamber 25 of the compression element 2 is formed by the partition plate 24,
The partition plate 24, the compression element cylinder block 23, and the lower bearing 22 form a compression chamber 26 of the compression element 3.

Next, the operation will be described. The compression stroke of the hermetic compressor 1 configured as described above includes the roller 2 of the compression element 2 which is eccentrically rotated by the crankshaft 20 in the compression chambers 25 and 26 of the compression element 2 and the compression element 3, respectively.
7. The roller 28 of the compression element 3 is used. Then, the flow of the refrigerant gas in the compression element 2 is sucked into the compression chamber 25 from the compression element suction pipe 12, and after being compressed, is discharged from the compression element discharge valve 29 into the chamber 15 which is a high pressure chamber. After that, the rotor 19 and the stator 16 of the motor
Is cooled and discharged from the compression element discharge pipe 4. On the other hand, the flow of the refrigerant gas in the compression element 3 is sucked into the compression chamber 26 from the compression element suction pipe 13, and after being compressed, is discharged from the compression element discharge valve 30 to the compression element discharge chamber 21. After that, the gas is further discharged from the compression element discharge pipe 5 through the discharge passage 31 provided in the lower bearing 22 and the compression element cylinder block 23. In the conventional capacity control refrigeration cycle described above, when the load of the refrigeration cycle becomes small, the two-way valve 14 for capacity control provided in the compression element suction pipe 13 is closed and the decompression cylinder compression element 3 is closed. The capacity of the refrigeration cycle was controlled so that the refrigerant did not flow into.

[0005]

Since the conventional multi-cylinder rotary compressor for carrying out capacity control is constructed as described above,
During the capacity control, the cylinder decompression element 3 is operated in vacuum, so that between the partition plate 24 and the end surface of the roller 28 of the compression element 3,
Alternatively, there is a problem that the leakage between the lower bearing 22 and the end surface of the roller 28 is large, and the adiabatic compression efficiency of the hermetic compressor 1 is significantly reduced as compared with the case where the capacity control is not performed.

Further, in a conventional multi-cylinder compressor with a cylinder deactivation mechanism having a bypass passage that connects the suction side of the cylinder decompression-side compression element and the inside of the closed container, the inside of the cylinder and the back of the vane become equal pressure during capacity control. However, there is a problem that the vane is blown off by the force received from the rolling piston and the vane and the rolling piston cannot always be in contact with each other, which causes abnormal noise.

The present invention has been made in order to solve the above-mentioned problems, and eliminates the compression work loss due to the gas leaking into the cylinder deactivation cylinder during capacity control, and performs highly efficient capacity control operation. An object of the present invention is to obtain a cylinder rotary compressor, and to obtain a multi-cylinder rotary compressor that can be operated without causing abnormal noise, because the vane always comes into contact with the rolling piston even during capacity control.

[0008]

A multi-cylinder rotary compressor according to claim 1 has a cylinder with a cylinder deactivation mechanism, and an opening provided in the vicinity of a discharge portion in the cylinder with the cylinder deactivation mechanism. And a passage communicating from the opening to the suction side, and a valve mechanism for opening and closing the passage.

A multi-cylinder rotary compressor according to a second aspect of the present invention has a cylinder with a cylinder deactivation mechanism, and is provided with a bypass passage for connecting the suction side of the cylinder with the cylinder deactivation mechanism and the inside of a closed container. It is a thing.

A multi-cylinder rotary compressor according to claim 3 is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And a discharge side of another compression element, a first bypass passage having a first control valve, a discharge side and a suction side of the compression element with the cylinder deactivating mechanism, and the cylinder deactivation control valve. And a second bypass passage having a second control valve, and during normal operation, the cylinder deactivation control valve, the first control valve are open, and the second control valve is closed. During capacity control, the cylinder deactivation control valve is closed, the first control valve and the second control valve are open or the cylinder deactivation control valve is open, the first control valve is closed, and the second control valve is It is to be opened.

A multi-cylinder rotary compressor according to a fourth aspect is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And a discharge side of another compression element, a first bypass passage having a first control valve, a discharge side of the compression element with the cylinder deactivation mechanism, and an upstream side of the cylinder deactivation control valve. And a second bypass passage having a second control valve, and the cylinder deactivation control valve and the first control valve are opened during normal operation.
The second control valve is closed, the cylinder deactivation control valve and the first control valve are closed, and the second control valve is open during capacity control.

A multi-cylinder rotary compressor according to a fifth aspect is a multi-cylinder rotary compressor having a compression element in which a refrigerant suction passage is provided independently, and the discharge side of the one compression element and the other compression element. A first bypass passage that is provided between the discharge side and the suction side of the one compression element and that has a second control valve that is provided between the discharge side and the suction side of the one compression element. 2 bypass passages, and the first
The control valve is open, the second control valve is closed, and the first control valve is closed and the second control valve is open during capacity control.

A multi-cylinder rotary compressor according to a sixth aspect is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And a discharge side of another compression element, the first bypass passage having a first control valve and the compression element with the cylinder deactivation mechanism have a displacement greater than that of another compression element. It is a small one.

A multi-cylinder rotary compressor according to a seventh aspect of the present invention includes a compression element with a cylinder deactivation mechanism, and a bypass passage for connecting the suction side of the compression element with the cylinder deactivation mechanism and the inside of a closed container. In the multi-cylinder rotary compressor, the compression element with the cylinder deactivating mechanism has a spring force of a vane spring larger than a spring force of a vane spring of another compression element.

[0015]

In the multi-cylinder rotary compressor according to the first aspect of the present invention, even if the leaked gas enters the deactivated cylinder, the valve mechanism bypasses the discharge portion and the suction side to reduce the loss of compressing the leaked gas. It can be reduced and highly efficient operation can be performed even during capacity control.

In the multi-cylinder rotary compressor according to the second aspect of the present invention, when the capacity is controlled, the cylinder deactivation cylinder becomes equal in pressure to the high pressure chamber so that compression work loss is eliminated and highly efficient operation can be performed.

According to another aspect of the multi-cylinder rotary compressor of the present invention, even if the leaking gas enters the decompressing compression element, the leaking gas is bypassed by bypassing the discharge side and the suction side of the compression element by the valve mechanism. By preventing the loss of compressing and compressing the inside of the compression element to a high pressure or a low pressure, it is possible to further reduce the leaked gas, so that highly efficient operation can be performed even during capacity control.

In the multi-cylinder rotary compressor according to the present invention, even if the leaked gas enters the decompressed compression element, the valve mechanism bypasses the discharge side of the compression element and the suction side of the compressor. Since only the low pressure on the suction side is compressed, highly efficient operation can be performed even during capacity control.

A multi-cylinder rotary compressor according to a fifth aspect of the present invention includes a valve mechanism for bypassing the suction side and discharge side of one compression element, and the discharge side of the compressor to bypass the compression side. Since the pressure inside both becomes low, the gas in the compression element is not compressed, and the amount of gas leaking in is small, so that highly efficient operation can be performed even during capacity control.

In the multi-cylinder compressor of claim 6, the displacement amount of the compression element on the capacity control side is made smaller than the displacement amount of the other compression element, so that the amount of gas leaking into the compression element on the capacity control side is reduced. It reduces the compression work loss and enables highly efficient operation during capacity control.

In the multi-cylinder rotary compressor according to the seventh aspect of the present invention, the vane of the cylinder decompression element separates from the rolling piston during the cylinder decompression operation by setting a large spring force of the vane spring of the cylinder decompression element. Without any abnormal noise.

[0022]

【Example】

Example 1. Embodiment 1 of the present invention will be described below with reference to the drawings. 1 is a cross-sectional view of a multi-cylinder rotary compressor according to Embodiment 1 of the present invention, and FIG. 2 is a model view showing a cylinder for cylinder deactivation and a bypass passage.

In FIG. 1 and FIG. 2, reference numeral 14 is for stopping the inhalation,
A two-way valve for deactivating the cylinder, 13 is a compression element suction pipe, 2
6 is a compression chamber, 27 is an opening provided near the discharge part, 2
Reference numeral 8 denotes a valve mechanism that opens and closes the bypass passage, and by the back pressure inside the bypass pipe 29, the top 30 is pressed against the opening 27 to open and close. Ring 31 is top 30
This is a ring for preventing deviation. The high-pressure side control valve 32 and the low-pressure side control valve 33 control the pressure in the bypass pipe 29.
Connected to 3. The pipe to the suction side also serves as a bypass passage.

Next, the operation will be described. During normal operation, by closing the low pressure side control valve 33 and opening the high pressure side control valve 32, the inside of the bypass pipe 29 becomes high pressure,
Since the top 30 is pressed against the opening 27, the bypass passage is closed. For capacity control, when the two-way valve 14 is closed, the inside of the cylinder deactivation cylinder becomes close to a vacuum, but the gas from each sliding portion, etc. Since it leaks in, it is compressed and requires extra work. Here, the low pressure side control valve 3
3 is opened and the high pressure side control valve 32 is closed, the pressure in the bypass pipe 29 is reduced and the top 30 is opened.
And the compression element suction pipe 13 communicate with each other. Therefore, the refrigerant gas leaking into the cylinder deactivation cylinder is returned to the suction side without being compressed, and extra compression work is not performed, so that highly efficient operation can be obtained.

Example 2. Embodiment 2 of the present invention will be described below with reference to the drawings. FIG. 3 is a sectional view of a multi-cylinder rotary compressor according to a second embodiment of the present invention. In FIG. 3, 14 is a two-way valve for stopping suction and performing cylinder deactivation, 13 is a compression element suction pipe, 26 is a compression chamber, 29 is a bypass pipe, and the compression element suction pipe 13 and a high pressure chamber. The inside of the chamber 15 is made to communicate by opening a two-way valve 32 provided in the bypass pipe 29.

Next, the operation will be described. During normal operation, the two-way valve 14 provided on the suction pipe 13 is opened, the two-way valve 32 provided on the bypass pipe 29 is closed, and normal compression action is performed in all compression chambers.

Next, when the two-way valve 14 is closed for the capacity control operation, the inside of the cylinder decompression chamber becomes close to a vacuum, and the refrigerant gas leaks in, causing compression work loss. When the valve 32 is opened, the high pressure chamber in the chamber 15 and the suction pipe 13 are communicated with each other, the pressure inside the decompression cylinder chamber becomes high, compression work is not performed, loss is eliminated, and highly efficient operation is obtained.

Example 3. The third embodiment of the present invention will be described below. 4 is a model diagram of a multi-cylinder rotary compressor according to Embodiment 3 of the present invention, and FIG. 5 is a sectional view thereof. In FIGS. 4 and 5, 40 is a cylinder deactivation control valve for stopping suction and performing cylinder deactivation, 2 is a compression element, 3 is a compression element for cylinder deactivation, and 15
Is a chamber, 41 is a first bypass passage, 42 is a first control valve, 43 is a second bypass passage connecting the discharge side and the suction side of the cylinder decompression element, and 44 is a second control valve.

Next, the operation will be described. During normal operation, the cylinder deactivation control valve 40 is opened, the first control valve 42 is opened, and the second control valve 42 is opened.
By closing the control valve 44, compression is performed by both the compression element 2 and the cylinder deactivation compression element 3. For capacity control,
When the cylinder deactivation control valve 40 is closed, the inside of the compression element 3 for cylinder decompression becomes close to a vacuum, but gas leaks from each sliding portion and the like, so that compression is performed, and an extra amount is generated accordingly. Need a job. Here, when the second control valve 44 is opened, the discharge side and the suction side of the cylinder decompression element 3 communicate with the chamber 15 through the first bypass passage 41 and the second bypass passage 43,
The inside of the cylinder decompression element 3 has a high pressure, the refrigerant is returned to the suction side without being compressed, and highly efficient operation can be performed without gas leakage. Alternatively, the cylinder control valve 40
Is opened, the first control valve 42 is closed, and the second control valve 44 is opened, so that the discharge side of the cylinder decompression element 3 and the suction side of the compressor communicate with each other and the pressure becomes low. Therefore, the refrigerant is returned to the suction side without being compressed, and even if gas leaks and enters, the refrigerant is not compressed to a high pressure and is discharged at a low pressure, so that compression loss can be reduced and high efficiency operation can be obtained.

Example 4. Another embodiment of the present invention will be described below. FIG. 6 is a model diagram of a multi-cylinder rotary compressor according to another embodiment of the present invention. In FIG. 6, 4
0 is a cylinder deactivation control valve for stopping suction and decommissioning, 2 is a compression element, 3 is a compression element for cylinder deactivation, 15 is a chamber, 41 is a compression element for cylinder deactivation 3 the discharge side and the discharge side of the compressor Of the high pressure gas pipe 6 of the first bypass passage, 42 is the first control valve, 4
3 is a second bypass passage connecting the discharge side of the cylinder decompression element and the low pressure gas pipe 11 on the suction side of the compressor, and 44 is a second control valve.

Next, the operation will be described. During normal operation, the cylinder deactivation control valve 40 is opened, the first control valve 42 is opened, and the second control valve 42 is opened.
By closing the control valve 44, compression is performed by both the compression element 2 and the cylinder deactivation compression element 3. Next, due to the capacity control operation, when the cylinder deactivation control valve 40 is closed, the inside of the compression element 3 for cylinder deactivation becomes close to a vacuum, but the gas leaks from each sliding part, etc. Done and requires extra work. Therefore, the first control valve 42 is closed,
By opening the second control valve 44, the discharge side of the cylinder decompression element 3 and the suction side of the compressor communicate with each other through the second bypass passage 43, and the pressure becomes low. Therefore, the refrigerant is returned to the suction side without being compressed, and even if gas leaks in, it is discharged only after being compressed to a high pressure and only to a low pressure, so that compression loss can be reduced and highly efficient operation can be achieved. can get.

Example 5. The fifth embodiment of the present invention will be described below. FIG. 7 is a model diagram of a multi-cylinder rotary compressor according to Embodiment 5 of the present invention. In FIG. 7, 2 is a compression element, 3 is a cylinder decompression element, 15 is a chamber, 41 is a cylinder decompression element 3, and a first bypass passage that connects the discharge side of the cylinder decompression element and the high-pressure gas pipe 6 on the discharge side of the compressor. , 42 is the first control valve,
Reference numeral 43 is a second bypass passage connecting the discharge side of the cylinder decompression element and the low pressure gas pipe 11 on the suction side of the compressor, and 44 is a second control valve.

Next, the operation will be described. During normal operation, the first control valve 42 is opened and the second control valve 44 is closed, so that compression is performed by both the compression element 2 and the cylinder deactivation compression element 3. At the time of capacity control, the first control valve 42 is closed,
By opening the second control valve 44, the discharge side of the cylinder decompression element 3 and the suction side of the compressor communicate with each other through the second bypass passage 43, and the pressure becomes low. Therefore, the refrigerant is returned to the suction side without being compressed, and the inside of the cylinder decompression element is not in a vacuum but in a low pressure, so that the amount of gas leaked can be reduced, so that highly efficient operation can be obtained.

Example 6. Embodiment 6 of the present invention will be described below. FIG. 8 is a model diagram of a multi-cylinder rotary compressor according to Embodiment 6 of the present invention. Even if the first control valve 42 of the third embodiment is replaced with the check valve 45, a pseudo operation can be expected.

Example 7. The seventh embodiment of the present invention will be described below. FIG. 9 is a model diagram of a multi-cylinder rotary compressor according to Embodiment 7 of the present invention. Even if the cylinder deactivation control valve 40 of the third embodiment is replaced with the check valve 46, a pseudo operation can be expected.

Example 8. Embodiment 8 of the present invention will be described below with reference to the drawings. FIG. 10 is a sectional view of a multi-cylinder rotary compressor according to Embodiment 8 of the present invention. In the figure, 3 is a compression element for capacity control, and the displacement amount is smaller than that of the compression element 2.

Next, the operation will be described. During normal operation, the two-way valve 40 provided on the suction pipe 13 is opened, and normal compression action is performed in all compression chambers. Next, when the two-way valve 40 is closed due to the capacity control operation, the inside of the cylinder decompression chamber becomes close to a vacuum, the refrigerant gas leaks, and compression work loss occurs. The compression work loss is proportional to the displacement amount of the compression element, but the multi-cylinder rotary compressor of the present claim sets the displacement amount of the cylinder decompression chamber to be small, so that the compression work loss is reduced, Highly efficient operation is possible during capacity control. Note that the smaller the displacement of the cylinder decompression chamber, the smaller the work loss of recompression and the higher the efficiency of the compressor during capacity control.However, in normal operation without capacity control, the maximum compressor Since the capacity decreases, the optimum value of the displacement is determined by the balance between the maximum capacity required and the efficiency during capacity control.

Example 9. Embodiment 9 of the present invention will be described below with reference to FIG.
1 will be described. FIG. 11 shows the eleventh embodiment of the present invention.
3 is a cross-sectional view of a cylinder decompression-side compression element of the multi-cylinder rotary compressor according to FIG. In the figure, 61 is a rolling piston, 60 is a vane, and 62 is a vane spring having a larger spring force than the vane springs of other compression elements provided at the back of the vane 60.

Next, the operation will be described. During normal operation, the vane 60 is pushed toward the center of the compression chamber 13 by the back pressure, which is a high pressure equal to the pressure inside the chamber 15, and the vane spring 62, and can always be in contact with the rolling piston 61. However, when the pressure inside the compression chamber 13 becomes high due to high efficiency operation during capacity control, the vanes 60 are pushed only by the vane springs 62, so that when the rolling piston 61 faces the vane direction during rotation,
It is defeated by the force of pushing and a strange noise is generated. Therefore, if the vane spring 62 is changed to a vane spring 62 having a large spring force so as not to lose the force received from the rolling piston 61, the vane 60 is always in contact with the rolling piston 61 and no abnormal noise is generated.

Example 10. In the ninth embodiment, the vane spring 62 having a large spring force is used, but the number of the vane springs 62 may be increased, and the same effect as that of the ninth embodiment can be obtained.

[0041]

The present invention has the following effects.
A multi-cylinder rotary compressor according to claim 1, wherein the multi-cylinder rotary compressor has a cylinder with a cylinder deactivation mechanism, wherein an opening is provided in the vicinity of the discharge part in the cylinder with the cylinder deactivation mechanism, and a suction side from this opening. Since it is configured to include a passage communicating with the passage and a valve mechanism that opens and closes this passage, even if leaked gas enters the cylinder deactivation cylinder, the valve mechanism bypasses the discharge portion and the suction side, The loss of compressing the leaked gas is reduced, and highly efficient operation can be achieved even during capacity control.

A multi-cylinder rotary compressor according to a second aspect of the present invention has a cylinder with a cylinder deactivation mechanism, and is provided with a bypass passage that connects the suction side of the cylinder with the cylinder deactivation mechanism and the inside of a closed container. Since the configuration is adopted, the inside of the cylinder deactivation cylinder becomes equal in pressure to the high-pressure pressure chamber during capacity control, and compression work loss is eliminated, so that highly efficient operation can be performed.

A multi-cylinder rotary compressor according to claim 3 is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And a discharge side of another compression element, a first bypass passage having a first control valve, a discharge side and a suction side of the compression element with the cylinder deactivating mechanism, and the cylinder deactivation control valve. And a second bypass passage having a second control valve, and during normal operation, the cylinder deactivation control valve, the first control valve are open, and the second control valve is closed. During capacity control, the cylinder deactivation control valve is closed, the first control valve and the second control valve are open or the cylinder deactivation control valve is open, the first control valve is closed, and the second control valve is Since it is configured to open, the valve mechanism connects the discharge side and the suction side of the cylinder decompression element so that high pressure or low pressure of the same pressure can be applied. It achieved because, not performed the compression in the cylinder deactivation for compression element, also reduces the loss would compress the leakage entering gas, the effect of enabling a highly efficient operation even during capacity control.

A multi-cylinder rotary compressor according to claim 4 is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And a discharge side of another compression element, a first bypass passage having a first control valve, a discharge side of the compression element with the cylinder deactivation mechanism, and an upstream side of the cylinder deactivation control valve. And a second bypass passage having a second control valve, and the cylinder deactivation control valve and the first control valve are opened during normal operation.
Since the second control valve is closed, and the cylinder deactivation control valve and the first control valve are closed and the second control valve is opened during the capacity control, the valve mechanism allows the cylinder deactivation. Since the discharge side and the suction side of the compression element communicate with each other and the same low pressure can be achieved, the cylinder decompression element does not perform compression, and the loss of compressing leaking gas is reduced, and even during capacity control. This has the effect of enabling highly efficient operation.

A multi-cylinder rotary compressor according to a fifth aspect of the present invention is a multi-cylinder rotary compressor having a compression element in which a refrigerant suction passage is provided independently, and the discharge side of the one compression element and the other compression element. A first bypass passage that is provided between the discharge side and the suction side of the one compression element and that has a second control valve that is provided between the discharge side and the suction side of the one compression element. 2 bypass passages, and the first
The control valve is open, the second control valve is closed, and the first control valve is closed and the second control valve is open during capacity control. Since the discharge side and the suction side of the compression element communicate with each other and the same low pressure can be achieved, the cylinder decompression element does not perform compression, and also reduces the loss of compressing leaked gas, and also during capacity control. This has the effect of enabling highly efficient operation.

A multi-cylinder rotary compressor according to claim 6 is a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein the discharge side of the compression element with the cylinder deactivation mechanism. And the discharge side of the other compression element, the first bypass passage having the first control valve and the compression element with the cylinder deactivating mechanism have a displacement smaller than that of the other compression element. With this configuration, it is possible to reduce the amount of gas that leaks into the cylinder deactivation cylinder, reduce compression work loss, and perform highly efficient operation during capacity control.

A multi-cylinder rotary compressor according to a seventh aspect of the present invention includes a compression element with a cylinder deactivation mechanism, and a bypass passage for connecting the suction side of the compression element with the cylinder deactivation mechanism and the inside of a closed container. In the multi-cylinder rotary compressor, the compression element with the cylinder deactivation mechanism is configured such that the spring force of its vane spring is larger than the spring force of the vane springs of the other compression elements. The vane of the side compression element does not separate from the rolling piston, and no abnormal noise is generated.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a multi-cylinder rotary compressor according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of the multi-cylinder rotary compressor according to the first embodiment of the present invention.

FIG. 3 is a vertical sectional view of a multi-cylinder rotary compressor according to a second embodiment of the present invention.

FIG. 4 is a model diagram of a multi-cylinder rotary compressor according to a third embodiment of the present invention.

FIG. 5 is a sectional view of a multi-cylinder rotary compressor according to a third embodiment of the present invention.

FIG. 6 is a model diagram of a multi-cylinder rotary compressor according to a fourth embodiment of the present invention.

FIG. 7 is a model diagram of a multi-cylinder rotary compressor according to a fifth embodiment of the present invention.

FIG. 8 is a model diagram of a multi-cylinder rotary compressor according to a sixth embodiment of the present invention.

FIG. 9 is a model diagram of a multi-cylinder rotary compressor according to a seventh embodiment of the present invention.

FIG. 10 is a vertical sectional view of a multi-cylinder rotary compressor according to an eighth embodiment of the present invention.

FIG. 11 is a cross-sectional view of an inactive cylinder side compression element according to Embodiment 9 of the present invention.

FIG. 12 is a refrigeration cycle diagram of a conventional multi-cylinder rotary compressor.

FIG. 13 is a vertical cross-sectional view of a conventional multi-cylinder rotary compressor.

[Explanation of symbols]

 3 Cylinder Cylinder 6 High Pressure Gas Pipe 11 Low Pressure Gas Pipe 13 Compression Cylinder Suction Pipe for Cylinder Cylinder 14 Two-way Valve 15 Chamber 27 Opening 29 Bypass Pipe 40 Cylinder Cylinder Control Valve 41 First Bypass Passage 42 First Control Valve 43 No. 2 bypass passage 44 second control valve 45 check valve 46 check valve 57 bypass passage 62 vane spring

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tomoaki Oikawa 3-18-1, Oga, Shizuoka City Shizuoka Manufacturing Co., Ltd.

Claims (7)

[Claims] 1. In a multi-cylinder rotary compressor having a cylinder with a cylinder deactivation mechanism, an opening provided in the vicinity of a discharge part in the cylinder with the cylinder deactivation mechanism and a communication from this opening to a suction side. A multi-cylinder rotary compressor having a passage for opening and a valve mechanism for opening and closing the passage. 2. A multi-cylinder rotary compressor having a cylinder with a cylinder deactivation mechanism, comprising: a multi-cylinder rotary compressor provided with a bypass passage that connects the suction side in the cylinder with the cylinder deactivation mechanism and the closed container. Machine. 3. A multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein a discharge side of the compression element with the cylinder deactivation mechanism and a discharge side of another compression element. A first bypass passage having a first control valve provided between the discharge side and the suction side of the compression element with the cylinder deactivation mechanism and the cylinder deactivation control valve; A second bypass passage having a valve, and during normal operation, the cylinder deactivation control valve, the first control valve is open, and the second control valve is closed,
During capacity control, the cylinder deactivation control valve is closed, the first control valve and the second control valve are open or the cylinder deactivation control valve is open, the first control valve is closed, and the second control valve is A multi-cylinder rotary compressor characterized by being opened. 4. A multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, wherein a discharge side of the compression element with the cylinder deactivation mechanism and a discharge side of another compression element. A first bypass passage having a first control valve provided between the discharge side of the compression element with the cylinder deactivation mechanism and the upstream side of the cylinder deactivation control valve; A second bypass passage having a valve, the cylinder deactivation control valve, the first control valve is open, the second control valve is closed during normal operation, and the cylinder deactivation control valve during capacity control. A multi-cylinder rotary compressor, wherein the first control valve is closed and the second control valve is opened. 5. A multi-cylinder rotary compressor having a compression element in which a refrigerant suction passage is independently provided, the multi-cylinder rotary compressor being provided between a discharge side of the one compression element and a discharge side of the other compression element, A first bypass passage having a first control valve;
A second bypass passage having a second control valve is provided between the discharge side and the suction side of the one compression element, and the first control valve is open during the normal operation, and the second bypass passage is provided. Control valve is closed, the first control valve is closed during capacity control, and the second control valve is closed.
The control valve of is a multi-cylinder rotary compressor characterized by being opened. 6. In a multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism using a cylinder deactivation control valve, a discharge side of the compression element with the cylinder deactivation mechanism and a discharge side of another compression element. A multi-cylinder rotation characterized in that a first bypass passage provided between and having a first control valve and the compression element with the cylinder deactivation mechanism have a displacement amount smaller than displacement amounts of other compression elements. Type compressor. 7. A multi-cylinder rotary compressor having a compression element with a cylinder deactivation mechanism and comprising a bypass passage communicating the suction side of the compression element with the cylinder deactivation mechanism and the inside of a closed container. The multi-cylinder rotary compressor is characterized in that the compression element with a cylinder mechanism has the spring force of its vane spring made larger than the spring force of the vane spring of other compression elements.