KR100921372B1 - Refrigerant suction structure in fixed displacement type piston compressor, and operation control method in fixed displacement type piston compressor - Google Patents

Abstract

The introduction passages 31 of the rotary valves 35 and 36 have outlets 312 and 313 for delivering refrigerant from the suction pressure region 142 to the respective compression chambers 271 and 281. The switch portion in the shut-off state blocks the portion 142 of the suction pressure region in the compressor 10 from the outlets 312 and 313 of the introduction passage 31. The switching section includes a valve body 42, a working pressure chamber 412, and a working pressure applying unit 48. The working pressure chamber 412 introduces an operating pressure for acting on the valve body 42 to arrange the valve body 42 in a communication position. The pressure in the suction pressure region 142 is opposed to the pressure in the working pressure chamber 412 via the valve body 42.

Refrigerant suction, valve body, working pressure

Description

REFRIGERANT SUCTION STRUCTURE IN FIXED DISPLACEMENT TYPE PISTON COMPRESSOR, AND OPERATION CONTROL METHOD IN FIXED DISPLACEMENT TYPE PISTON COMPRESSOR}

The present invention relates to a refrigerant suction structure in a fixed displacement piston compressor provided with a rotary valve. The piston defines a compression chamber in the cylinder bore. The rotary valve has an introduction passage for introducing refrigerant from the suction pressure region into the compression chamber. The rotary valve rotates integrally with the rotating shaft. Moreover, this invention relates to the operation control method in a fixed displacement piston compressor.

JP-A-7-119631 and JP-A-2006-83835 disclose a piston compressor using a rotary valve. JP-A-64-88064 and JP-A-2000-145629 disclose a piston compressor using a suction valve of a reed valve type. The piston compressor using a rotary valve has less suction resistance and superior energy efficiency when suction gas is sucked into the cylinder bore than a piston compressor using a reed valve type suction valve.

Japanese Patent Laid-Open No. 7-119631 discloses a start shock that may occur at the start of a compressor. At the time of startup of the compressor, if the torque sharply increases along with the compression of the gas, the load is applied to the internal combustion engine as the vehicle engine, and as a result, the running speed of the vehicle may decrease for a moment. In that case, the vehicle occupant feels shock.

The rotary valve of Unexamined-Japanese-Patent No. 7-119631 can move to the axial direction of a rotating shaft according to the pressure of a control pressure chamber. The compressor has a suction port as a suction pressure region located at the center of the cylinder block. The rotary valve has a bypass groove that can communicate the cylinder bore to the suction port. The rotary valve moves axially so that the bypass groove communicates almost all of the cylinder bores to the inlet port at the compressor shutdown and at compressor startup. Therefore, even when the piston compresses the gas in the cylinder bore at the start of the compressor, the gas in the cylinder bore flows to the suction port via the bypass groove. As a result, starting shock is suppressed.

The clearance in the main surface of a rotary valve should be made as small as possible. This is to prevent gas leakage along the main surface of the rotary valve and to allow the rotary valve to rotate. The clearance also needs to allow the rotary valve to move in the axial direction. However, managing such clearances is very difficult.

The piston compressor of Japanese Patent Application Laid-Open No. 2000-145629 has a differential pressure sensing on / off valve that opens and closes by a differential pressure between a discharge pressure and a suction pressure. The differential pressure sensing opening / closing valve is disposed between a low pressure refrigerant channel for introducing refrigerant from the outside of the compressor to the compressor and a suction chamber located in the compressor. When the compressor is started from the pressure balanced state, the differential pressure sensing on / off valve is closed and prevents the refrigerant from flowing into the suction chamber from outside the compressor. As a result, the starting shock is alleviated.

However, even when the differential pressure detecting switching valve is closed, the refrigerant remains in the suction chamber, and the residual refrigerant is sucked into the cylinder bore and compressed. Since the volume of the suction chamber is made large to suppress the suction pulsation of the compressor, the amount of refrigerant sucked into the cylinder bore is large in the state where the differential pressure sensing switching valve is closed. Therefore, the effect of the starting shock relief by a differential pressure sensing switching valve is not enough.

An object of the present invention is to improve the effect of mitigating shock.

According to one aspect of the present invention, a refrigerant suction structure in a fixed displacement piston compressor is provided. The compressor has a rotating shaft connected to an external drive source through a clutch. The plurality of cylinder bores are arranged around the rotating shaft. The plurality of pistons are respectively accommodated in the cylinder bores, thereby partitioning the compression chambers into the respective cylinder bores. The cam body is integrated with the rotating shaft. The cam body interlocks rotation of the rotating shaft with each piston. The rotary valve has an introduction passage for introducing a refrigerant from each suction pressure region into each compression chamber. The rotary valve rotates integrally with the rotating shaft. The suction pressure region has a portion in the compressor. The introduction passage has an outlet for delivering the coolant toward each compression chamber. The refrigerant intake structure has a switching portion that can be switched between communicating and interrupted states. The switch in the communicating state allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The switching part in the cutoff state cuts off a part of the suction pressure region in the compressor from the outlet of the introduction passage. The switching part has a valve body which can be switched to the communicating position and the cutoff position and arranged. The valve body in the communication position allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The valve body in the cutoff position cuts off a portion of the suction pressure region in the compressor from the outlet of the inlet passage. The working pressure chamber introduces a working pressure for acting on the valve body to position the valve body in the communication position. The operating pressure applying unit applies the operating pressure to the working pressure chamber. The pressure in the suction pressure region is opposed to the pressure in the working pressure chamber through the valve body.

According to another aspect of the present invention, a refrigerant suction structure in a fixed displacement piston compressor is provided. The refrigerant suction structure has a switching section that can be switched between communicating and interrupted states. The switch in the communicating state allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The switching part in the cutoff state cuts off a part of the suction pressure region in the compressor from the outlet of the introduction passage. The switching part has a valve body which can be switched to the communicating position and the cutoff position and arranged. The valve body in the communication position allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The valve body in the cutoff position cuts off a portion of the suction pressure region in the compressor from the outlet of the inlet passage. The electromagnetic drive unit drives the valve body by an electromagnetic force.

According to another aspect of the present invention, there is provided a driving control method in a fixed displacement piston compressor. The operation control method includes preparing a switching unit that can be switched to a communicating state and a disconnected state. The switch in the communicating state allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The switching part in the cutoff state cuts off a part of the suction pressure region in the compressor from the outlet of the introduction passage. The switching section includes a valve body, a working pressure chamber, and a working pressure applying section. The valve element can be disposed by switching between a communication position allowing a portion of the suction pressure region in the compressor to communicate with the outlet of the inlet passage and a blocking position for blocking a portion of the suction pressure region in the compressor from the outlet of the inlet passage. Do. The working pressure chamber introduces a working pressure acting on the valve body to arrange the valve body in the communication position. The operating pressure imparting unit imparts the working pressure to the working pressure chamber. The operating pressure applying unit includes a switching valve arranged to switch the refrigerant in the discharge pressure region to a first state capable of supplying the working pressure chamber and a second state in which it cannot supply. The operation control method is equipped with putting a clutch into a connected state after changing a switching valve to a 2nd state, when switching a clutch from a shut-off state to a connected state. The operation control method includes switching the switching valve to the first state after the clutch is in the connected state.

According to another aspect of the present invention, there is provided a driving control method in a fixed displacement piston compressor. An operation control method is equipped with the switching part which can be switched to a communication state and a interruption state. The switch in the communicating state allows the portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage. The switching part in the cutoff state cuts off a part of the suction pressure region in the compressor from the outlet of the introduction passage. The switching section includes a valve body and an electromagnetic drive section. The valve element can be disposed by switching between a communication position allowing a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage, and a cutoff position for blocking a portion of the suction pressure region in the compressor from the outlet of the introduction passage. Do. The electromagnetic drive unit can drive the valve body by an electromagnetic force. The electromagnetic drive unit can be switched to a first state in which the valve body is disposed in the communication position and a second state in which the valve body is arranged in the shutoff position. The driving control method includes providing the clutch in the connected state after switching the clutch from the shutoff state to the connected state after setting the electromagnetic drive unit to the second state. The driving control method includes putting the electromagnetic drive unit in the first state after the clutch is in the connected state.

Other features and advantages of the present invention will become apparent from the following detailed description and the accompanying drawings in order to explain the features of the present invention.

(The best form to carry out invention)

The features considered to be novel of this invention are especially clear in the attached Claim. BRIEF DESCRIPTION OF THE DRAWINGS The present invention, which includes objects and benefits, will be understood by referring to the accompanying drawings the description of preferred embodiments at the present time described below.

1 to 6 show a fixed displacement piston compressor 10 according to a first embodiment of the present invention.

As shown in FIG. 1, the front cylinder block 11 is connected to the rear cylinder block 12. As shown in FIG. The front housing 13 is connected to the front cylinder block 11, and the rear housing 14 is connected to the rear cylinder block 12. The front cylinder block 11, the rear cylinder block 12, the front housing 13, and the rear housing 14 constitute the entire housing of the compressor 10.

The front discharge chamber 131 is formed in the front housing 13. The rear discharge chamber 141 and the suction chamber 142 are formed in the rear housing 14. The front discharge chamber 131 and the rear discharge chamber 141 are portions of the discharge pressure region in the compressor 10, respectively. The suction chamber 142 is a part of the suction pressure region in the compressor 10. The inside of a compressor means the inside of the whole housing of the compressor 10, and the outside of a compressor means the outside of the whole housing of the compressor 10. As shown in FIG.

As shown in FIG. 1, between the front cylinder block 11 and the front housing 13, the valve plate 15, the valve formation plate 16, and the retainer formation plate 17 are arrange | positioned. The valve plate 18, the valve forming plate 19, and the retainer forming plate 20 are disposed between the rear cylinder block 12 and the rear housing 14. Discharge ports 151 and 181 are formed in the valve plates 15 and 18, respectively, and discharge valves 161 and 191 are formed in the valve forming plates 16 and 19. The discharge valves 161 and 191 open and close the discharge ports 151 and 181, respectively. Retainers 171 and 201 are formed in the retainer forming plates 17 and 20, respectively. The retainers 171 and 201 regulate the opening degree of the discharge valves 161 and 191.

As shown in FIG. 1, the rotating shaft 21 is rotatably supported by the front cylinder block 11 and the rear cylinder block 12. As shown in FIG. A front shaft hole 111 and a rear shaft hole 121 are formed through the front cylinder block 11 and the rear cylinder block 12, and a rotating shaft 21 is formed in the front shaft hole 111 and the rear shaft hole 121. Is fitted. The outer circumferential surface of the rotary shaft 21 is in contact with the inner circumferential surfaces of the front shaft hole 111 and the rear shaft hole 121, and the rotary shaft 21 is the front cylinder block through the inner circumferential surfaces of the front shaft hole 111 and the rear shaft hole 121. Directly supported by 11 and rear cylinder block 12. The outer peripheral surface portion of the rotary shaft 21 in contact with the front shaft hole 111 is the front seal main surface 211, and the outer peripheral surface portion of the rotary shaft 21 in contact with the rear shaft hole 121 is rear. Seal principal face 212.

The swash plate 23 as a cam body is fixed to the rotating shaft 21. The swash plate 23 is accommodated in the swash plate chamber 24 formed by the front cylinder block 11 and the rear cylinder block 12. A lip seal type shaft seal member 22 is disposed between the front housing 13 and the rotary shaft 21. The shaft seal member 22 prevents gas leakage from between the front housing 13 and the rotary shaft 21. The protruding end of the rotating shaft 21 which protrudes outward from the front housing 13 is connected to the vehicle engine 26 which is an external drive source via the electromagnetic clutch 25. The rotary shaft 21 obtains a rotation driving force from the vehicle engine 26 via the electromagnetic clutch 25.

As shown in FIG. 2A, the front cylinder block 11 is formed so that a plurality of front cylinder bores 27 are arranged around the rotary shaft 21. As shown in FIG. 2B, a plurality of rear cylinder bores 28 are formed in the rear cylinder block 12 so as to be arranged around the rotation shaft 21. The double headed piston 29 is accommodated in the front cylinder bore 27 and the rear cylinder bore 28 which are paired in front and rear, respectively.

As shown in FIG. 1, the rotational movement of the swash plate 23 integrally rotating with the rotary shaft 21 is transmitted to the double head piston 29 via the shoe 30, so that the double head piston 29 is moved to the front cylinder. The inside of the bore 27 and the rear cylinder bore 28 reciprocate back and forth. The double head piston 29 partitions the front compression chamber 271 in the front cylinder bore 27 and partitions the rear compression chamber 281 in the rear cylinder bore 28.

As shown in FIG. 1, the inside of the rotary shaft 21 has an in-axis passage 31 extending along the rotation axis 210 of the rotary shaft 21. The inlet 311 of the in-axis passage 31 is located in the rear end surface of the rotating shaft 21, and opens in the suction chamber 142. As shown in FIG. The in-axis passageway 31 has a front outlet 312 and a rear outlet 313. The front outlet 312 opens to the front seal main surface 211 of the rotary shaft 21. The rear outlet 313 opens to the rear seal main surface 212.

As shown in FIG. 2A, the front cylinder block 11 has a front communication passage 32 equal in number to the front cylinder bore 27. Each front communication path 32 communicates each front cylinder bore 27 with the front shaft hole 111. As shown in FIG. 2B, the rear cylinder block 12 has the same number of rear communication paths 33 as the rear cylinder bores 28. Each rear communication path 33 communicates each rear cylinder bore 28 with the rear shaft hole 121. With the rotation of the rotary shaft 21, the front outlet 312 of the in-axis passage 31 intermittently communicates with each front communication path 32, and the rear outlet 313 is each rear communication path 33. Intermittently).

1, in the case of a stroke in which the double-headed piston 29 moves from left to right, that is, in a state in which the double-headed piston 29 makes a certain front cylinder bore 27 a suction stroke, the front outlet 312 communicates with the corresponding front communication path 32. As a result, the refrigerant in the shaft passage 31 of the rotary shaft 21 is sucked into the corresponding front compression chamber 271 via the front outlet 312 and the corresponding front communication path 32.

1, in the case of a stroke in which the double head piston 29 moves from right to left, that is, in a state in which the double head piston 29 makes a certain front cylinder bore 27 as a discharge stroke, the front seal main surface 211 ) Blocks the front outlet 312 from the corresponding front communication path 32. As a result, the refrigerant in the front compression chamber 271 pushes the discharge valve 161 out of the discharge port 151 and is discharged to the front discharge chamber 131. The refrigerant discharged to the front discharge chamber 131 flows out to the external refrigerant circuit 34 through the discharge passage 341.

1, in the case of a stroke in which the double head piston 29 moves from right to left, that is, in a state in which the double head piston 29 makes a certain rear cylinder bore 28 a suction stroke, the rear outlet 313 Communicates with the corresponding rear communication path 33. As a result, the refrigerant in the in-axis passage 31 of the rotary shaft 21 is sucked into the corresponding rear compression chamber 281 via the rear outlet 313 and the corresponding rear communication path 33.

1, in the case of a stroke in which the double head piston 29 moves from left to right, that is, in a state in which the double head piston 29 makes a certain rear cylinder bore 28 a discharge stroke, the rear seal main surface 212 ) Blocks the rear outlet 313 from the corresponding rear communication path 33. As a result, the refrigerant in the rear compression chamber 281 pushes the discharge valve 191 out of the discharge port 181 and is discharged to the rear discharge chamber 141. The refrigerant discharged to the rear discharge chamber 141 flows out to the external refrigerant circuit 34 through the discharge passage 343.

As shown in FIG. 1, a heat exchanger 37, an expansion valve 38, and a heat exchanger 39 are disposed in the external refrigerant circuit 34. The heat exchanger 37 takes heat from the refrigerant. The expansion valve 38 controls the refrigerant flow rate in accordance with the fluctuation of the gas temperature measured at the outlet of the heat exchanger 39. The heat exchanger 39 transfers the surrounding heat to the refrigerant. The refrigerant flowing out to the external refrigerant circuit 34 is returned to the suction chamber 142.

As shown in FIG. 1, the part of the front seal main surface 211 of the rotating shaft 21 functions as the 1st rotary valve 35. As shown in FIG. A portion of the rear seal main surface 212 of the rotary shaft 21 functions as the second rotary valve 36. That is, the rotating shaft 21 is a rotary valve. It can be said that the 1st rotary valve 35 and the 2nd rotary valve 36 are formed integrally with the rotating shaft 21, respectively. The rotation axis 210 of the rotation shaft 21 is the rotation axis of the first rotary valve 35 and is also the rotation axis of the second rotary valve 36.

As shown in FIG. 1, the rear end surface of the rotary shaft 21, that is, the rear end surface of the second rotary valve 36 intersects with the rotation axis 210 of the rotary valve. The in-axis passage 31 and the front outlet 312 constitute an introduction passage of the first rotary valve 35. The in-axis passage 31 and the rear outlet 313 constitute an introduction passage of the second rotary valve 36. The front shaft hole 111 is a 1st valve accommodation chamber which accommodates the 1st rotary valve 35. The rear shaft hole 121 is a second valve accommodation chamber that accommodates the second rotary valve 36.

As shown in FIG.3 and FIG.4, the rear housing 14 has the end wall 40 which forms the suction chamber 142. As shown in FIG. The cylinder 41 is integrally formed on the inner surface of the end wall 40. The inside of the cylinder 41 is called the working pressure recessed part 411 as a working pressure chamber formation recessed part. A spool-shaped valve body 42 is slidably inserted into the working pressure recess 411. The valve body 42 includes a disk-shaped piston portion 43 and a cylindrical portion 44. The piston portion 43 partitions the working pressure chamber 412 in the working pressure recess 411. The pressure in the suction chamber 142, that is, the suction pressure, is opposed to the pressure in the working pressure chamber 412 through the valve body 42. The peripheral wall of the cylindrical part 44 has an inlet 441. That is, the inlet 441 opens to the outer circumferential surface of the cylindrical portion 44 and communicates with a cylinder interior 442 of the cylindrical portion 44. The cylinder 442 is an internal passage of the valve body 42.

As shown in FIG. 3 and FIG. 4, the cylindrical guide cylinder 45 is integrally formed in the cross section of the rear cylinder block 12 so that it may oppose the cylinder 41. As shown in FIG. The cylinder 451 of the guide cylinder 45 communicates with the inlet 311 of the shaft passage 31 as an introduction passage. The tip of the guide cylinder 45 is separated from the tip of the cylinder 41. The cylindrical portion 44 of the valve body 42 is slidably fitted to the guide cylinder 45. A circlip 46 is attached to the inner circumferential surface of the guide cylinder 45, and a first return spring 47 is disposed between the circlip 46 and the piston portion 43. The first return spring 47 elastically supports the valve body 42 so as to be close to the end wall 40 of the rear housing 14. As the valve body 42 approaches the end wall 40, the volume of the working pressure chamber 412 decreases.

3 shows a state in which the valve body 42 is in the communication position so that the valve body 42 allows the in-axis passage 31 to communicate with the suction chamber 142. 4 shows a state in which the valve body 42 is in the shut off position such that the valve body 42 shuts off the suction chamber 142 from the in-axis passage 31. That is, in the state shown in FIG. 3, the entire inlet 441 of the valve body 42 is exposed into the suction chamber 142. The shaft passage 31 communicates with the suction chamber 142 via the cylinder 451 of the guide cylinder 45, the cylinder 442 of the cylindrical portion 44, and the introduction port 441. In the state shown in FIG. 4, the entire inlet 441 deeply enters into the working pressure recess 411. As a result, the cylindrical portion 44 of the valve body 42 blocks the in-axis passage 31 from the suction chamber 142.

3 and 4, a communication port 401 is formed through the end wall 40 of the rear housing 14. The communication port 401 opens into the working pressure chamber 412. The communication port 401 communicates with a supply port 481 of an electromagnetic three-way valve 48 via a conduit 63. The electromagnetic three-way valve 48 functions as a switching valve constituting an operating pressure application portion.

As shown in FIG. 3 and FIG. 4, the electromagnetic three-way valve 48 has a cylindrical valve housing 49. The valve housing 49 includes a small diameter cylinder portion 491 and a large diameter cylinder portion 492, and the fixed iron core 50 is fixed and accommodated in the small diameter cylinder portion 491. In the small diameter cylinder portion 491, the movable iron core 51 is slidably fitted. The movable iron core 51 has a flange 511 located at the large diameter cylinder portion 492. An elastic support spring 52 is disposed between the step 493 between the small-diameter cylindrical portion 491 and the large-diameter cylindrical portion 492 and the flange 511. The elastic support spring 52 elastically supports the movable iron core 51 in a direction away from the fixed iron core 50. The coil 53 is wound around the small diameter cylindrical part 491 so that the fixed iron core 50 and the movable iron core 51 may be extended. When the coil 53 is supplied with current, the fixed iron core 50 is excited to attract the movable iron core 51 to resist the spring force of the elastic support spring 52.

As shown in FIG.3 and FIG.4, the movable core 51 accommodates the 1st valve body 54 inside. The first valve body 54 faces the fixed iron core 50 and can be contacted to and detached from the fixed iron core 50. A valve seat 501 is integrally formed at the end face of the fixed iron core 50 opposite to the movable iron core 51. The elastic support spring 55 elastically supports the first valve body 54 toward the valve seat 501. The fixed iron core 50 has a passage 56 therein. The passage 56 penetrates the valve seat 501. The inlet 561 of the passage 56 communicates with the rear discharge chamber 141 through the conduit 57.

As shown in FIG.3 and FIG.4, the cover 58 is fitted in the large diameter cylinder part 492 of the valve housing 49. As shown in FIG. The second valve body 60 is attached to the end face of the movable iron core 51 opposite to the lid 58. The second valve body 60 can be contacted to and detached from the lid 58. The cover 58 has a discharge port 581 formed therethrough. When the 2nd valve body 60 is in contact with the cover 58, the discharge port 581 is interrupted | blocked from the cylinder 494 of the large diameter cylinder part 492. The discharge port 581 communicates with the suction chamber 142 through the pipeline 59.

As shown in FIG. 3 and FIG. 4, the groove 61 is formed in the main surface of the movable iron core 51. As shown in FIG. The groove 61 communicates with the space 62 between the fixed iron core 50 and the movable iron core 51. The cylinder 494 of the large diameter cylinder portion 492 communicates with the space 62 through the groove 61. The cylinder 494 of the large diameter cylinder portion 492 communicates with the working pressure chamber 412 through the supply port 481 formed through the large diameter cylinder portion 492 and the conduit 63.

As shown in FIG. 1, the control computer C controls the electromagnetic three-way valve 48 and the electromagnetic clutch 25, respectively, by magnetization and demagnetization. The air conditioning apparatus operation switch 64, the room temperature setter 65, and the room temperature detector 66 are signal-connected to the control computer C. As shown in FIG. The room temperature setter 65 sets the target room temperature, and the room temperature detector 66 detects the room temperature. When the air conditioner operating switch 64 is in the ON state, the control computer C supplies a current to the electromagnetic three-way valve 48 and the electromagnetic clutch 25 based on the temperature difference between the target room temperature and the detected room temperature. In other words, the control element is controlled.

When the detected temperature is lower than the target temperature, or when the detected temperature is higher than the target temperature and the temperature difference between the detected temperature and the target temperature is equal to or less than the allowable difference, the control computer C stops supplying current to the electromagnetic clutch 25. do. In this case, the electromagnetic clutch 25 is cut off, and the rotational driving force of the vehicle engine 26 is not transmitted to the rotational shaft 21. In addition, when the detection temperature is higher than the target temperature and the temperature difference between the detection temperature and the target temperature exceeds the allowable difference, the control computer C supplies a current to the electromagnetic clutch 25. In this case, the electromagnetic clutch 25 is brought into a connected state, and the rotation driving force of the vehicle engine 26 is transmitted to the rotation shaft 21.

The timing chart of FIG. 6 shows the clutch waveform K1, the three-way valve waveform V, and the torque waveform T1. The clutch waveform K1 indicates the timing of supply of current to the electromagnetic clutch 25. The clutch waveform K1 shows the clutch start timing t1 which is a timing at which energization to the electromagnetic clutch 25 is started, and the clutch end timing t2 which is a timing at which electricity supply to the electromagnetic clutch 25 is terminated. The three-way valve waveform V indicates the timing of supply of current to the electromagnetic three-way valve 48. The three-way valve waveform V includes the first energization period V1 set corresponding to the clutch start timing t1 and the second energization period V2 set corresponding to the clutch end timing t2. Have The starting timing t3 of the first energizing period part V1 is before the clutch starting timing t1, and the ending timing t4 of the first energizing period part V1 is the clutch starting timing t1. It is later than). In other words, when the control computer C starts to supply current to the electromagnetic clutch 25, the control computer C first supplies current to the electromagnetic three-way valve 48, and then supplies current to the electromagnetic clutch 25. Do it. The starting timing t5 of the second energizing period portion V2 is before the clutch ending timing t2, and the ending timing t4 of the second energizing period portion V2 is the same as the clutch ending timing t2. Do.

5 is a flowchart showing an operation control program for controlling the operation of the compressor 10. The control computer C controls the operation of the compressor 10 based on the operation control program shown in the flowchart. The operation control of the compressor 10 will be described below in accordance with the operation control program shown in the flowchart.

The compressor 10 is in an operation stop state (state in which the electromagnetic clutch 25 is cut off), and the electromagnetic three-way valve 48 is in an element demagnetization state (energization stop state). In the state where the electromagnetic three-way valve 48 is elementary, as shown in FIG. 3, the first valve body 54 is separated from the valve seat 501, and the second valve body 60 is the discharge port 581. To close it. When the working pressure chamber 412 is at a pressure equivalent to the discharge pressure, the valve body 42 is at the communication position shown in Fig. 3, but when the working pressure chamber 412 is at a pressure corresponding to the suction pressure, the valve The sieve 42 is in the blocking position shown in FIG.

In step S1, the control computer C judges whether or not the compressor operation start mode (mode to start energization with the electromagnetic clutch 25) based on the comparison between the detected temperature and the target temperature. In step S1, in the case of YES, that is, in the compressor operation start mode, in step S2, the control computer C starts to energize the electromagnetic three-way valve 48. When current is supplied to the electromagnetic three-way valve 48, as shown in FIG. 4, the first valve body 54 contacts the valve seat 501, the passage 56 is closed, and the second valve body ( 60 is removed from the lid 58 and the discharge port 581 is opened. In this state, the working pressure chamber 412 passes through a discharge passage including a communication port 401, a pipe 63, a supply port 481, a cylinder 494, a discharge port 581, and a pipe 59. In communication with the suction chamber 142. Therefore, the inside of the working pressure chamber 412 becomes the same pressure area as the inside of the suction chamber 142. Therefore, the valve body 42 is reliably arrange | positioned in the interruption | blocking position shown in FIG. 4 by the spring force of the 1st return spring 47, and the communication between the inlet 441 and the suction chamber 142 is interrupted | blocked. do.

In step S3, the control computer C determines whether the time ta from the start of energization to the electromagnetic three-way valve 48 has elapsed (t1-t3 = ta in the case illustrated in FIG. 6). Judge. In the case of YES in step S3, that is, when time ta has elapsed from the start of energization to the electromagnetic three-way valve 48, the control computer C in step S4 passes to the electromagnetic clutch 25. Start energization. As a result, the electromagnetic clutch 25 shifts from the blocked state to the connected state, and the rotation shaft 21 and the swash plate 23 start rotation.

In step S5, the control computer C determines whether or not time tb ((t4-t1) = tb in the case illustrated in Fig. 6) has elapsed from the energization start to the electromagnetic clutch 25. do. In the case of YES in step S5, that is, when time tb has elapsed from the energization start to the electromagnetic clutch 25, in step S6, the control computer C moves to the electromagnetic three-way valve 48. Stop energization. When the current supply to the electromagnetic three-way valve 48 is stopped, as shown in FIG. 3, the passage 56 is opened away from the valve seat 501, and the second valve body ( 60 is in contact with the cover 58, the discharge port 581 is closed. In this state, communication between the suction chamber 142 and the working pressure chamber 412 is blocked. The working pressure chamber 412 is connected to the communication port 401, the conduit 63, the supply port 481, the cylinder 494, the groove 61, the space 62, the passage 56, and the conduit 57. It communicates with the rear discharge chamber 141 through the supply passage which is made. Thereby, the refrigerant pressure (discharge pressure) in the rear discharge chamber 141 is introduced into the working pressure chamber 412, and the working pressure chamber 412 becomes the same pressure area | region as the inside of the rear discharge chamber 141. FIG. The communication port 401 and the conduit 63 are common passages connecting the working pressure chamber 412 to the electromagnetic three-way valve 48.

The pressure (operating pressure) of the refrigerant in the rear discharge chamber 141 is higher than the pressure in the cylinder 442, and the pressure in the operating pressure chamber 412 is the pressure of the cylinder 442 and the spring of the first return spring 47. Resisting the force, the valve body 42 is disposed at the communication position shown in FIG. As a result, the inlet 441 is exposed into the suction chamber 142 so that the inlet 441 communicates with the suction chamber 142. Therefore, the refrigerant in the suction chamber 142 flows into the in-axis passageway 31 through the introduction port 441.

After stopping the energization to the electromagnetic three-way valve 48, in step S7, the control computer C starts the compressor operation stop mode (electromagnetic clutch 25) based on the comparison between the detected temperature and the target temperature. Mode to stop the power supply to the furnace). In step S7, in the case of YES, that is, in the compressor operation stop mode, in step S8, the control computer C starts to energize the electromagnetic three-way valve 48. When the energization to the electromagnetic three-way valve 48 is started, communication between the working pressure chamber 412 and the rear discharge chamber 141 is cut off, and the working pressure chamber 412 communicates with the suction chamber 142. That is, the operating pressure equivalent to the discharge pressure in the working pressure chamber 412 is discharged to the suction chamber 142. In other words, the working pressure in the working pressure chamber 412 is released.

In step S9, the control computer C determines whether the time tc ((2-2-5) = tc in the case illustrated in Fig. 6) has elapsed from the energization start to the electromagnetic three-way valve 48. Judge. In the case of YES in step S9, that is, when time tc has elapsed from the start of energization to the electromagnetic three-way valve 48, the control computer C in step S10 controls the electromagnetic three-way valve 48. And energization to the electromagnetic clutch 25 are stopped. After the process of step S10, the control computer C shifts to step S1.

The torque waveform T1 in FIG. 6 is an example of torque fluctuations. When energization is started by the electromagnetic clutch 25, the torque fluctuates. In this embodiment, when starting energization to the electromagnetic clutch 25, it energizes the electromagnetic three-way valve 48 before starting electricity supply to the electromagnetic clutch 25, and after energizing the electromagnetic clutch 25, it is an electromagnetic three way. The energization to the valve 48 is stopped. As a result, the sudden torque fluctuation (variation part T11 in the torque waveform T1) when the energization is started to the electromagnetic clutch 25 is suppressed. Further, even when the energization to the electromagnetic clutch 25 is stopped, the torque fluctuates. In the present embodiment, when the energization to the electromagnetic clutch 25 is stopped, the energization to the electromagnetic three-way valve 48 is performed before the energization to the electromagnetic clutch 25 is stopped. As a result, sudden torque fluctuations when the energization to the electromagnetic clutch 25 is stopped are suppressed.

The electromagnetic three-way valve 48, the working pressure chamber 412, and the valve body 42 constitute a switch portion. The switching unit is in a state in which the suction chamber 142, which is a part of the suction pressure region in the compressor 10, communicates with the front outlet 312 and the rear outlet 313 of the in-axis passage 31, which is the introduction passage, and the state of blocking. Can be switched to 1 and 3, the electromagnetic three-way valve 48 is in a first state (element state) capable of supplying the refrigerant in the rear discharge chamber 141, which is the discharge pressure region, to the working pressure chamber 412. In FIG. In FIG. 4, the electromagnetic three-way valve 48 is in a second state (excitation state) in which the refrigerant in the rear discharge chamber 141 which is the discharge pressure region cannot be supplied to the working pressure chamber 412.

1st Embodiment has the following advantages.

(1) In a state where the pressure in the rear discharge chamber 141 which is the operating pressure is not introduced into the working pressure chamber 412, the valve body 42 is disposed at the shutoff position shown in FIG. When the valve body 42 is disposed in the shutoff position, the suction chamber 142, which is the suction pressure region in the compressor 10, is cut off from the inlet 441. When the operation of the compressor 10 is started (when the rotation of the rotary shaft 21 is started), since the rotation of the rotary shaft 21 is started after the valve body 42 is disposed in the blocking position in advance, There is no refrigerant inflow from the suction chamber 142 into the cylinder 442 and the shaft passage 31. Therefore, sudden torque fluctuation is suppressed and starting shock is alleviated. In addition, since communication between the suction chamber 142 and the inlet 441 in the compressor 10 is blocked, the front compression chamber 271 or the rear compression chamber ( The amount of refrigerant compressed in 281) is small. Therefore, the effect of suppressing torque fluctuation, that is, the effect of mitigating shock is improved.

(2) When the working pressure in the working pressure chamber 412 is released, the valve body 42 returns to the shutoff position by the spring force of the first return spring 47. Adoption of the 1st return spring 47 is a simple structure for returning the valve body 42 to a interruption position.

(3) The inlet 441, which is the inlet of the cylinder 442 of the valve body 42, enters the working pressure recess 411 deeply and is shielded when the valve body 42 is in the shutoff position. When 42 is in the communication position, it is exposed outside the working pressure recess 411 into the suction chamber 142. The configuration in which the introduction port 441 enters and leaves the working pressure recess 411 is very suitable for increasing the introduction port 441 to secure a sufficient passage cross-sectional area of the introduction passage.

7 illustrates a second embodiment of the present invention. The device configuration is the same as in the case of the first embodiment.

Although the apparatus structure in 2nd Embodiment is the same as the case of 1st Embodiment, when starting electricity supply to the electromagnetic clutch 25, as shown by the electricity supply start part K21 in clutch waveform K2. The point of gradually increasing the energization amount of is different from the case of the first embodiment. After the supply current value reaches maximum, the energization to the electromagnetic three-way valve 48 is stopped. By this energization start to the electromagnetic clutch 25, the fluctuation | variation of the fluctuation part T21 in the torque waveform T2 which shows a torque fluctuation is suppressed rather than the case of 1st Embodiment.

For example, in the conventional fixed displacement piston compressor without a switching part, the torque at the start is large, that is, the load on the electromagnetic clutch 25 is large. For this reason, in the conventional compressor, when the energization amount is gradually increased in the same manner as in the present embodiment, slip occurs in the electromagnetic clutch 25. Therefore, in the conventional compressor, it is difficult to secure the reliability of the electromagnetic clutch 25.

In this embodiment, since the torque at the start is small, that is, the load to the electromagnetic clutch 25 is small, the operation control which gradually increases the energization amount with respect to the electromagnetic clutch 25 is possible.

8 and 9 describe a third embodiment. The same code | symbol is used for the same structural part as 1st Embodiment.

As shown in FIG. 8, a check valve 68 is disposed at a portion 34A of the external refrigerant circuit 34 upstream of the heat exchanger 37, and an external refrigerant circuit upstream of the check valve 68. The portion 34A of 34 is connected to the working pressure chamber 412 by the communication port 401 and the inflow passage L. As shown in FIG. The check valve 68 is formed in the portion 34A downstream from the connection portion between the portion 34A of the external refrigerant circuit 34 and the inflow passage L. The portion 34A of the external refrigerant circuit 34 is a discharge pressure region. An electromagnetic on / off valve 67 is disposed in the inflow passage L. The electromagnetic on-off valve 67 and the check valve 68 constitute a working pressure applying unit. The solenoid on-off valve 67 as a switching valve is subjected to excitation control of the control computer C. In Fig. 8, the electromagnetic on / off valve 67 is in an excited state, and the electromagnetic on / off valve 67 is in an open state in which the inflow passage L is open. When the solenoid valve 67 is in the excited state, the refrigerant (discharge refrigerant) in the portion of the portion 34A of the external refrigerant circuit 34 upstream from the check valve 68 is transferred to the working pressure chamber 412. Inflow is possible. In Fig. 9A, the solenoid on-off valve 67 is in the element state, and the solenoid on-off valve 67 is in the closed state in which the inflow passage L is blocked. The solenoid valve 67 is a normally closed solenoid valve that is closed in a non-energized state (element state). However, even when the solenoid valve 67 is in the closed state, some gas leakage is possible. Formed.

The waveform W1 in the timing chart of FIG. 9B shows the timing of supply of current to the solenoid valve 67. The energization of the solenoid on-off valve 67 is started after the energization start to the electromagnetic clutch 25 (for example, one second later, and (t6-t1) later in the example), and the solenoid on-off valve 67 The energization stop after energization with respect to) is the same as the termination timing (the energization stop at the clutch termination timing t2 in the example of FIG. 9B) for the electromagnetic clutch 25.

When the energization to the electromagnetic clutch 25 is stopped, the electricity supply to the electromagnetic on-off valve 67 is also stopped simultaneously, and the electromagnetic on-off valve 67 shifts from the open state to the closed state. When the energization to the electromagnetic clutch 25 is stopped, that is, when the operation of the compressor 10 is stopped, the discharge of the refrigerant is lost, so the check valve 68 is closed. As a result, the pressure balancing in the compressor 10 proceeds quickly.

When the operation of the compressor 10 is stopped, the solenoid on-off valve 67 is in a closed state, but since some gas leakage is possible at the solenoid on-off valve 67, the operating pressure chamber 412 and the communication port 401 ) And the refrigerant corresponding to the discharge pressure remaining in the portion of the inflow passage L between the solenoid on / off valve 67 via the solenoid on / off valve 67, and the external refrigerant circuit upstream of the check valve 68 ( Leak to portion 34A of FIG. Therefore, the pressure balancing in the working pressure chamber 412 also advances. Therefore, until the next time when energization to the electromagnetic clutch 25 is started (in the example of FIG. 9B, time t1), the valve body 42 is connected to FIG. 9A by the spring force of the first return spring 47. It is arranged in the blocking position indicating.

Before the energization to the electromagnetic clutch 25 is started, the electromagnetic on / off valve 67 is in an element state (closed state), and the energization to the electromagnetic on / off valve 67 is started after the energization to the electromagnetic clutch 25 is started. Therefore, the valve body 42 is in the shut off position for a while from the start of energization to the electromagnetic clutch 25, and the refrigerant in the suction chamber 142 does not flow into the in-axis passage 31. Thereby, starting shock at the start of the compressor 10 is alleviated.

After the energization to the electromagnetic clutch 25 is started, when energization is started to the solenoid valve 67, the solenoid valve 67 shifts from the closed state to the open state, and the external refrigerant circuit upstream of the check valve 68. The part 34A of 34 communicates with the working pressure chamber 412. After the start of energization to the electromagnetic clutch 25 (that is, after the compressor 10 has started to operate), the check valve 68 is kept open by discharging the coolant so that the discharge coolant discharges the external coolant circuit 34. It is refluxed to the suction chamber 142 via. In the state where energization to the electromagnetic clutch 25 is continued (that is, the state in which the compressor 10 is operated), the electromagnetic on / off valve 67 is kept open and an external refrigerant circuit upstream of the check valve 68. The refrigerant pressure (discharge pressure) in the portion 34A of 34 propagates to the working pressure chamber 412 via the inflow passage L and the solenoid valve 67. Thereby, the valve body 42 is arrange | positioned at the communication position shown in FIG.

The check valve 68, the solenoid valve 67, the working pressure chamber 412, and the valve body 42 constitute a switching unit. The switching section communicates with the suction chamber 142, which is a part of the suction pressure region in the compressor 10, communicating with the front outlet 312 and the rear outlet 313 of the introduction passage, and the suction chamber 142 with the front outlet. It is switchable to the interruption state which cuts off from 312 and the rear outlet 313. In Fig. 8, the solenoid valve 67 is in a first state (excitation state) capable of supplying the refrigerant of the portion 34A of the external refrigerant circuit 34, which is the discharge pressure region, to the working pressure chamber 412. In Fig. 9A, the solenoid valve 67 is in a second state (element state) in which the refrigerant of the portion 34A of the external refrigerant circuit 34 cannot be supplied to the working pressure chamber 412.

The third embodiment also has the same advantages as in the case of the first embodiment.

10-11B, 4th Embodiment is described. The same code | symbol is used for the same structural part as 3rd Embodiment.

In the fourth embodiment, instead of the normally closed electromagnetic on / off valve 67 in the third embodiment, an electromagnetic open / close valve 67A of a normally open type is used. The upper type solenoid valve 67A opens in the non-energized state and closes in the energized state. In Fig. 10, the electromagnetic opening / closing valve 67A as the switching valve opens the inflow passage L in the non-energized state, and in Fig. 11A the electromagnetic opening / closing valve 67A closes the inflow passage L in the energized state. The electromagnetic open / close valve 67A and the check valve 68 constitute a working pressure applying unit.

The waveform W2 in the timing chart of FIG. 11B shows the timing of supply of current to the solenoid valve 67A. When the energization to the electromagnetic clutch 25 is started, the energization to the electromagnetic opening / closing valve 67A starts before the electricity supply to the electromagnetic clutch 25 (time t1 in the example of illustration) starts [time in the example of illustration] t3)], and after the energization of the electromagnetic clutch 25 is started, the energization of the solenoid on-off valve 67A is stopped (time t4 in the example of the figure).

When the operation of the compressor 10 is stopped, the discharge of the refrigerant is lost, so the check valve 68 is closed. As a result, the pressure balancing in the compressor 10 proceeds quickly. When the operation of the compressor 10 is stopped, the solenoid on-off valve 67A is in an open state, so that the inflow passage between the operating pressure chamber 412 and the communication port 401 and the solenoid on-off valve 67A ( The refrigerant corresponding to the discharge pressure remaining in the portion L) leaks to the portion 34A of the external refrigerant circuit 34 upstream from the check valve 68 via the solenoid valve 67A. For this reason, the pressure balancing in the working pressure chamber 412 also proceeds quickly. Therefore, the valve body 42 is arrange | positioned by the spring force of the 1st return spring 47 by the spring force of the 1st return spring 47 until the next time the electricity supply to the electromagnetic clutch 25 is started. The valve body 42 is in the shut off position from before the start of energization to the electromagnetic clutch 25 (before (t1-t3) in the example of illustration) to after the start of energization (after (t4-t1) in the example of illustration). The refrigerant in the suction chamber 142 does not flow into the shaft passage 31. Thereby, starting shock at the start of the compressor 10 is alleviated.

The check valve 68, the solenoid valve 67A, the working pressure chamber 412, and the valve body 42 constitute a switching unit. The switching section is switchable in a state in which the suction chamber 142 which is a part of the suction pressure region in the compressor 10 communicates with the outlet of the introduction passage, and in a state of blocking. In Fig. 10, the electromagnetic on / off valve 67A is in a first state (element state) capable of supplying the refrigerant of the portion 34A of the external refrigerant circuit 34, which is the discharge pressure region, to the working pressure chamber 412. In Fig. 11A, the solenoid valve 67 is in a second state (excitation state) in which the refrigerant of the portion 34A of the external refrigerant circuit 34 cannot be supplied to the working pressure chamber 412.

The fourth embodiment also has the same advantages as in the case of the first embodiment.

12A and 12B describe a fifth embodiment of the present invention. The same code | symbol is used for the same structural part as 1st Embodiment.

45 A of guide cylinders fitted to the cylindrical part 44 of the valve body 42 are cylindrical with a bottom, and are formed separately from the rear cylinder block 12, the rotating shaft 21, etc. . The bottom wall of the guide cylinder 45A abuts the end surface 122 of the rear cylinder block 12. The guide cylinder 45A is fitted to the cylindrical portion 44 of the valve body 42 so as to allow movement in the radial direction of the rotary shaft 21 with respect to the rotary shaft 21. The communication port 452 is formed in the bottom wall of the guide cylinder 45A so that the inner cylinder 451 of the guide cylinder 45A may communicate with the in-axis passage 31. The first return spring 47 is disposed between the bottom wall of the guide cylinder 45A and the piston portion 43. In FIG. 12A, the valve body 42 is disposed in the communication position, and in FIG. 12B, the valve body 42 is disposed in the shutoff position. The excitation element timing of the electromagnetic three-way valve 48 is the same as that of the first embodiment.

For example, assuming that the coolant leaks from between the valve body 42 and the cylinder 41 or between the valve body 42 and the guide cylinder when the valve body 42 is in the shut-off position, The mitigating effect is lowered.

However, 45 A of guide cylinders of this embodiment are fitted with the cylindrical part 44 of the valve body 42 so that movement in the radial direction of the rotating shaft 21 with respect to the rotating shaft 21 is permitted. For this reason, it is permissible that the shaft center 413 of the working pressure recessed part 411 matches the shaft center 453 of 45 A of guide cylinders. Therefore, the clearance between the cylindrical part 44 of the valve body 42 and the cylinder 41 and the clearance between the cylindrical part 44 of the valve body 42 and the guide cylinder 45A can be made small. Therefore, leakage of the refrigerant along the main surface of the cylindrical portion 44 of the valve body 42 can be prevented.

13 and 14 describe a sixth embodiment. The same code | symbol is used for the same structural part as 1st Embodiment.

A cylinder 69 is slidably fitted into the cylinder 41, and a transmission rod 70 is connected to the piston 69. The piston 69 partitions the working pressure chamber 412 in the working pressure recess 411. The transmission rod 70 deeply enters into the in-axis passageway 31A. The in-axis passage 31A includes a small diameter passage 314 and a larger diameter passage 315 having a larger diameter than the small diameter passage 314. In the portion of the transmission rod 70 located in the small-diameter passage 314, a cylindrical small cylindrical body 71 is mounted. The cylindrical cylindrical body 72 is attached to the part of the transmission rod 70 located in the large diameter passageway 315. The cylindrical prismatic body 71 is slidable in the direction of the rotation axis 210 of the rotary shaft 21, and is fitted into the small diameter passage 314 so that the front outlet 312 can be opened and closed. The large cylindrical body 72 of the shape is slidable in the direction of the rotation axis 210 of the rotary shaft 21, and is fitted into the large diameter passage 315 so that the rear outlet 313 can be opened and closed. The cylinder of the cylindrical cylindrical main body 72 has a part of the in-axis passage 31A between the main cylindrical body 71 and the large cylindrical body 72, and the entrance 311 and the member of the intra-axial passage 31A. It communicates with the part of the in-axis passageway 31A between the main surface 72.

The first return spring 73 is disposed between the step 316 between the small-diameter passage 314 and the large-diameter passage 315 and the large circumferential surface 72. The first return spring 73 has a small main body 71, a large main body 72, a transfer rod 70, and a piston 69 to push the piston 69 into the working pressure recess 411. Is elastically supported toward the working pressure chamber 412. The major circumferential body 71, the large circumferential body 72, the transmission rod 70, and the piston 69 constitute a valve body 42 that partitions the working pressure chamber 412 in the working pressure recess 411. do.

Fig. 14 shows a state where the main circumferential body 71 closes the front exit 312, and the major circumferential body 72 closes the rear exit 313, and the front exit 312 and the rear exit 313 are: It is blocked from the in-axis passageway 31A. Fig. 13 shows a state where the main circumferential body 71 opens the front outlet 312, and the major circumferential body 72 opens the rear outlet 313, and the front outlet 312 and the rear outlet 313 are It communicates with 31 A of in-axis passages. When energization to the electromagnetic three-way valve 48 is performed, the small circumferential body 71 and the large circumferential body 72 are moved from the communication position shown in FIG. 13 by the spring force of the first return spring 73. It is arranged in the blocking position shown in. The excitation element timing of the electromagnetic three-way valve 48 is the same as that of the first embodiment.

6th Embodiment has the same advantage as 1st Embodiment. In addition, in the sixth embodiment, the refrigerant that can flow into the front compression chamber 271 and the rear compression chamber 281 when the main circumferential body 71 and the large circumferential body 72 are in the blocking position is the front outlet 312. ), Only the refrigerant in the rear outlet 313, the inside of the front communication path 32, and the inside of the rear communication path 33 has a higher relaxation effect than the case of the first embodiment.

In addition, when the piston 69 is configured to be relatively rotatable with respect to the transmission rod 70, the piston 69 can prevent relative rotation between the first return spring 73 and the rotation shaft 21. Therefore, abrasion damage of the 1st return spring 73 or the rotation shaft 21 resulting from the relative rotation between the 1st return spring 73 and the rotating shaft 21 can be avoided. Alternatively, the large columnar body 72 may be configured to be relatively rotatable with respect to the first return spring 73.

15A and 15B describe the seventh embodiment. The same code | symbol is used for the same structural part as 6th Embodiment.

At the distal end of the transfer rod 70, a disc-shaped disc 74 is mounted. As shown in Fig. 15A, when the large columnar body 72 is in a position to close the rear outlet 313, the disc 74 is located upstream than the front outlet 312 in the in-axis passage 31A, and the in-axis The refrigerant in the passage 31A cannot flow into the front compression chamber 271 through the front outlet 312. As shown in FIG. 15B, when the large columnar body 72 is in a position to open the rear outlet 313, the disc 74 is located downstream of the front outlet 312 in the in-axis passage 31A, and in-axis The refrigerant in the passage 31A can flow into the front compression chamber 271 through the front outlet 312. When energization is performed to the electromagnetic three-way valve 48 (see Fig. 14), the disc 74 is disconnected from the communication position shown in Fig. 15B by the spring force of the first return spring 73, and shown in Fig. 15A. Is placed into position. The disc 74, the large cylindrical surface 72, the transmission rod 70, and the piston 69 constitute the valve body 42 which partitions the working pressure chamber 412 in the working pressure recess 411. As shown in FIG.

The seventh embodiment has the same advantages as the sixth embodiment.

16A and 16B describe an eighth embodiment. The same code | symbol is used for the same structural part as 6th Embodiment.

A cylinder 75 is connected to the piston 69 so as to be relatively rotatable with respect to the piston 69. The cylinder 75 is slidably fitted into the in-axis passageway 31A. An end wall 752 is formed at the tip of the cylinder 75. An angular pin 76 is mounted at the inner end of the shaft passage 31A, and the pin 75 is relatively slidably inserted into the end wall 752 of the barrel 75. do. The cylinder 75 and the square pin 76 are integrally rotated with the rotary shaft 21 and can slide in the shaft shaft passage 31A in a state where the square pin 76 is inserted through the end wall 752.

The cylinder 75 is equipped with the small diameter cylinder part 77 inserted into the small diameter passage 314, and the large diameter cylinder part 78 fitted into the large diameter passage 315. As shown in FIG. An introduction port 751 is formed in the part of the large diameter cylinder part 78 located in the suction chamber 142 so that the suction chamber 142 can communicate with the cylinder 750 of the cylinder 75.

The communication port 771 is formed in the small diameter cylinder part 77 in the small diameter passage part 314 so that the small diameter cylinder part 77 may communicate. A communication port 781 is formed in the large diameter barrel portion 78 so as to communicate with the large diameter cylinder portion 78.

The 1st return spring 73 is arrange | positioned between the step | step 753 between the small-diameter cylindrical part 77 and the large-diameter cylindrical part 78, and the step | step 316 of the rotating shaft 21. As shown in FIG. The first return spring 73 elastically supports the cylinder 75 toward the working pressure chamber 412 as if the piston 69 is pushed into the working pressure recess 411. The piston 69 and the cylinder 75 comprise the valve body which partitions the working pressure chamber 412 in the working pressure recess 411.

16B shows a state in which the small-diameter cylindrical portion 77 as the valve body closes the front outlet 312, and a state in which the large-diameter cylindrical portion 78 as the valve body closes the rear outlet 313. As a result, the front outlet 312 and the rear outlet 313 are cut off from the cylinder 750 of the cylinder 75. 16A shows a state in which the communication port 771 of the small-diameter cylindrical portion 77 communicates with the front outlet 312, and the communication port 781 of the large-diameter cylindrical portion 78 communicates with the rear outlet 313. The front outlet 312 and the rear outlet 313 communicate with the cylinder 750 in the state. The refrigerant in the suction chamber 142 can flow into the front compression chamber 271 through the introduction port 751, the cylinder 750, the communication port 771, the front outlet 312, and the front communication path 32. The refrigerant in the suction chamber 142 is introduced into the rear compression chamber 281 through the introduction port 751, the cylinder 750, the communication port 781, the rear outlet 313, and the rear communication path 33. Inflow is possible. When energization is performed to the electromagnetic three-way valve 48 (see FIG. 14), the cylinder 75 is blocked by the spring force of the first return spring 73 from the communication position shown in FIG. Is placed into position. The excitation element timing of the electromagnetic three-way valve 48 is the same as that of the first embodiment.

The eighth embodiment has the same advantages as the sixth embodiment.

17 to 18B describe a ninth embodiment. The same code | symbol is used for the same structural part as 5th Embodiment.

As shown in FIG. 17, in the part 34A of the external refrigerant circuit 34 upstream from the heat exchanger 37, the oil separator 79 with a built-in check valve is arrange | positioned.

As shown in FIGS. 18A and 18B, a refrigerant swirling cylinder 81 is fitted into and fixed in the housing 80 constituting the oil separator 79. The coolant swing cylinder 81 partitions the inside of the housing 80 into an oil separation chamber 82 and a valve accommodating chamber 83. The oil separation chamber 82 communicates with the portion 34A of the external refrigerant circuit 34 upstream from the oil separator 79, and the refrigerant in the portion 34A of the external refrigerant circuit 34 is the oil separation chamber 82. Flows into. The coolant flowing into the oil separation chamber 82 from the portion 34A of the external coolant circuit 34 rotates around the coolant turning cylinder 81. The refrigerant that has rotated around the refrigerant swirling cylinder 81 flows into the cylinder 812 from the communication port 811 of the refrigerant swinging cylinder 81 facing the oil separation chamber 82.

The valve body 85 is accommodated in the valve accommodation chamber 83. The valve body 85 can open and close the other communication port 813 of the refrigerant turning cylinder 81. The valve body 85 is elastically supported toward the position which closes the communication port 813 by the compression spring 86. As shown in FIG. When the pressure of the refrigerant in the cylinder 812 overcomes the spring force of the compression spring 86, the refrigerant in the cylinder 812 pushes the valve body 85 and flows out into the valve accommodation chamber 83. The coolant swing cylinder 81, the valve body 85, and the compression spring 86 constitute a check valve 87. The refrigerant in the valve storage chamber 83 flows into the heat exchanger 37.

A narrow hole 40 is formed through the end wall 40. The narrowing hole 402 as narrowing communicates the working pressure chamber 412 and the conduit 84. The oil separation chamber 82 communicates with the working pressure chamber 412 through the conduit 84 and the narrow hole 402. The pressure (discharge pressure) in the oil separation chamber 82 propagates to the working pressure chamber 412 through the conduit 84 and the narrowing hole 402. The narrowing hole 402 and the conduit 84 constitute a part of the inflow passage downstream from the oil separator 79.

 Oil is put into the circuit which consists of the compressor 10 and the external refrigerant circuit 34, and this oil flows with a refrigerant | coolant.

The refrigerant flowing into the oil separation chamber 82 from the portion 34A of the external refrigerant circuit 34 rotates around the refrigerant swirling cylinder 81, and mist-shaped oil flowing together with the refrigerant is Separation is carried out in the oil separation chamber 82. The refrigerant that has rotated around the refrigerant turning cylinder 81 flows into the cylinder 812, and the oil separated from the refrigerant flows into the working pressure chamber 412 via the conduit 84 and the narrowing hole 402. Inflow is possible. The conduit 84 and the narrow hole 402 constitute an inflow passage from the working pressure chamber 412 to the portion 34A of the external refrigerant circuit 34 serving as the discharge pressure region.

When the operation of the compressor 10 is stopped and the pressure in the compressor 10 is balanced, the valve body 42 is held at the cutoff position shown in FIG. 18B by the spring force of the first return spring 47. do. When the operation of the compressor 10 starts, since there is no refrigerant inflow from the suction chamber 142 into the in-axis passage 31, the starting shock is alleviated.

When the pressure in the oil separation chamber 82 rises with the start of the operation of the compressor 10, the pressure in the working pressure chamber 412 also rises, and the valve body 42 acts as the spring force of the first return spring 47. It is arrange | positioned at the communication position shown in FIG. 18A against resisting. Since the narrowing hole 402 narrows the cross-sectional area of the passage between the conduit 84 and the working pressure chamber 412, even if the pressure in the front discharge chamber 131 and the rear discharge chamber 141 rises, the working pressure chamber 412 Internal pressure does not rise suddenly. In addition, since the oil separated from the oil separator 79 enters the narrow hole 402 deeply, the oil deep into the narrow hole 402 becomes a passage resistance, contributing to suppression of the sudden rise of the pressure in the working pressure chamber 412. do. Since the sudden rise of the pressure in the working pressure chamber 412 is suppressed, the valve body 42 does not move instantly from the shutoff position to the communication position. Therefore, the mitigation effect of starting shock becomes high.

Since the ninth embodiment does not use the solenoid three-way valve 48 or the solenoid on-off valve 67, it is advantageous in cost as compared with the first to fifth embodiments.

19A and 19B describe a tenth embodiment. The same code | symbol is used for the same structural part as 1st Embodiment.

A communication chamber 88 and a valve hole 891 are formed in the rear housing 14, and a plate-shaped opening and closing plate 90 is accommodated in the communication chamber 88 so as to open and close the valve hole 891. The valve hole 891 is formed through a partition wall 89 separating the communication chamber 88 from the suction chamber 142. The inlet 311 of the in-axis passage 31 is located in the end surface of the rotating shaft 21 in the rear cylinder block 12, and opens in the communication chamber 88 in the rear housing 14. As shown in FIG.

The piston 91 is fitted into the working pressure recess 411, and the transmission rod 92 is integrally formed with the piston 91. The opening and closing plate 90 is mounted at the tip of the transfer rod 92. On the surface of the partition wall 89 facing the communication chamber 88, a flat valve seat surface 892 is formed. The opening / closing plate 90 comes into contact with and detaches from the valve seat surface 892. The seal surface 901 of the opening / closing plate 90 in contact with the valve seat surface 892 is formed in a plane. That is, when the open / close plate 90 closes the valve hole 891, the seal surface 901 of the open / close plate 90 is in surface contact with the valve seat surface 892. The piston 91, the transmission rod 92, and the opening / closing plate 90 partition the working pressure chamber 412 in the working pressure recess 411, and the valve body 93 opening and closing the valve hole 891. Configure

The first return spring 94 is disposed between the piston 91 and the partition wall 89. The 1st return spring 94 elastically supports in the direction which pushes the piston 91 to the working-pressure recessed part 411. The valve body 93 in Fig. 19B is in a communication position where the communication chamber 88 communicates with the suction chamber 142 by opening the valve hole 891, and the valve body 93 in Fig. 19A is a valve hole ( By closing 891, it is in the blocking position which isolate | connects the communication chamber 88 from the suction chamber 142. As shown in FIG. The 1st return spring 94 elastically supports the valve body 93 toward the said interruption position from the said communication position.

A plurality of stoppers 902 protrude from the rear surface of the opening / closing plate 90 opposite to the end face of the rotary shaft 21. The stopper 902 is capable of contacting and detaching from the tip of the cylindrical portion 123 protruding from the end face 122 of the rear cylinder block 12. In the state where the valve body 93 is disposed in the communication position shown in FIG. 19B, in the state where the stopper 902 abuts against the tip of the cylinder portion 123, and the valve body 93 is disposed in the shutoff position shown in FIG. 19A. , The stopper 902 is separated from the tip of the barrel 123.

In the state where the electromagnetic three-way valve 48 is excited, the valve body 93 is disposed at the cutoff position shown in Fig. 19A, and the refrigerant in the suction chamber 142 cannot flow into the communication chamber 88. In the state where the electromagnetic three-way valve 48 is elementary, the valve body 93 is disposed in the communication position shown in Fig. 19B, and the refrigerant in the suction chamber 142 is provided with the valve hole 891, the communication chamber 88, and the like. And the front compression chamber 271 (see FIG. 1) and the rear compression chamber 281 can be introduced via the in-axis passage 31.

The excitation element timing of the electromagnetic three-way valve 48 is the same as that of the first embodiment. Therefore, the tenth embodiment also obtains a relaxation effect of the starting shock. Moreover, since the volume of the communication chamber 88 which accommodates the plate-shaped opening-and-closing plate 90 can be made small, similar to the case of 1st Embodiment, the relaxation effect of starting shock is high.

20 shows a fixed displacement piston compressor 10A according to an eleventh embodiment. The compressor 10A has a plurality of migraine pistons 95. The same code | symbol is used for the same structural part as 1st Embodiment.

The entire housing of the compressor 10A includes the cylinder block 12, the front housing 13, and the rear housing 14. The swash plate 23 is accommodated in the swash plate chamber 24 partitioned between the cylinder block 12 and the front housing 13. The migraine piston 95 associated with the swash plate 23 reciprocates in the cylinder bore 28 with the rotation of the swash plate 23. The rotary valve 21 is provided with a rotary valve 36 corresponding to the cylinder block 12. The valve body 42 is formed in the rear housing 14 so as to partition the working pressure chamber 412.

The eleventh embodiment also has the same advantages as the first embodiment.

21 to 26 show a twelfth embodiment of the present invention.

As shown in FIG. 21, in the rotation shaft 21, the in-axis passage 31 is formed along the rotation axis 210 of the rotation shaft 21. As shown in FIG. In the rear housing 14, a communication chamber 88 and a valve hole 891 are formed, and in the communication chamber 88, a plate-shaped opening and closing plate 90 accommodates the valve hole 891 so as to be opened and closed. do. The valve hole 891 is formed through the partition 89 separating the communication chamber 88 and the suction chamber 142. The inlet 311 of the in-axis passage 31 is located in the end surface of the rotating shaft 21 in the rear cylinder block 12, and opens in the communication chamber 88 in the rear housing 14. As shown in FIG.

As shown in FIG. 23 and FIG. 24, the electromagnetic solenoid 248 as an electromagnetic drive part is attached to the end wall 40 of the aluminum rear housing 14 which forms the suction chamber 142. As shown in FIG. On the outer surface of the end wall 40, the mounting recessed portion 404 is formed in a depression. The electromagnetic solenoid 248 includes a fixed iron core 250, a movable iron core 251, a second return spring 252, and a coil 253.

The fixed iron core 250 is fitted to the mounting recess 404, and the coil 253 is embedded in the fixed iron core 250. The mounting recess 404 is connected to the suction chamber 142. In the fixed iron core 250, the pressure recess 260 as a pressure chamber formation recess is recessed and formed. The pressure recess 260 opens toward the suction chamber 142. The movable iron core 251 is slidably fitted into the pressure recess 260. The movable core 251 partitions the pressure chamber 262 in the pressure recess 260. The groove 254 is formed in the peripheral surface of the movable iron core 251. The groove 254 communicates the pressure recess 260 with the suction chamber 142. Therefore, the pressure in the pressure chamber 262 corresponds to the pressure in the suction chamber 142. The pressure of the suction chamber 142, that is, the suction pressure, opposes the pressure of the pressure chamber 262 via the movable iron core 251. The cover 258 attached to the outer surface of the end wall 40 holds the fixed iron core 250 and the coil 253 into the mounting recess 404.

The movable iron core 251 has an attachment hole 255 as a through hole. The attachment hole 255 penetrates through the movable iron core 251 so as to extend from the pressure recess 260 to the suction chamber 142. The transmission rod 92 is pressed into the attachment hole 255 from the opening of the attachment hole 255 toward the suction chamber 142, and is fixed. At the distal end of the transfer rod 92, an opening and closing plate 90 is mounted.

The movable iron core 251, the transfer rod 92, and the open / close plate 90 constitute a valve body 242 that opens and closes the valve hole 891. The valve body 242 partitions the pressure chamber 262 in the pressure recess 260.

A second return spring 252 is disposed between the transfer rod 92 and the bottom 261 of the pressure recess 260. The second return spring 252 elastically supports the transfer rod 92 in a direction away from the bottom 261. That is, the movable iron core 251 is elastically supported in the direction which protrudes from the pressure recessed part 260 toward the suction chamber 142 by the spring force of the 2nd return spring 252. As shown in FIG. The electromagnetic solenoid 248, the valve body 242, and the 2nd return spring 252 comprise a switching part. The switching section communicates with the suction chamber 142, which is a part of the suction pressure region in the compressor 10, in communication with the front outlet 312 and the rear outlet 313 of the in-axis passage 31, and the suction chamber 142. Can be switched to a blocking state for blocking the front exit 312 and the rear exit 313.

In Fig. 23, the valve body 242 is in a communication position in which the communication chamber 88 communicates with the suction chamber 142 by opening the valve hole 891. In FIG. In Fig. 24, the valve body 242 is in a shutoff position that closes the communication chamber 88 from the suction chamber 142 by closing the valve hole 891. The second return spring 252 elastically supports the valve body 242 from the blocking position toward the communication position. That is, the switching unit has a communication state (state shown in Fig. 23) in which the suction chamber 142 communicates with the front outlet 312 and the rear outlet 313 of the in-axis passage 31, and the suction chamber 142 is in-axis. It is possible to switch to a shutoff state (state shown in Fig. 24) to cut off from the front outlet 312 and the rear outlet 313 of the passage 31.

When the current is supplied to the coil 253, the fixed iron core 250 resists the spring force of the second return spring 252, and pulls the movable iron core 251. That is, the electromagnetic force generated by energization of the coil 253 drives the valve body 242 from the communication position toward the cutoff position. The electromagnetic solenoid 248 can be switched to the first state in which the valve body 242 is arranged in the communication position by being an element, and the second state in which the valve body 242 is arranged in the shutoff position by being excited.

The electromagnetic solenoid 248 and the electromagnetic clutch 25 are subjected to the excitation control of the control computer C. As shown in FIG.

The valve waveform VV in the timing chart of FIG. 26 indicates the supply timing of the current to the electromagnetic solenoid 248. The 1st electricity supply period part V1 in the valve waveform VV is set corresponding to the clutch start timing t1. The starting timing t3 of the first energizing period part V1 is before the clutch starting timing t1, and the ending timing t4 of the first energizing period part V1 is later than the clutch starting timing t1. to be. That is, when starting supply of electric current to the electromagnetic clutch 25, the control computer C first supplies electric current to the electromagnetic solenoid 248, and then supplies electric current to the electromagnetic clutch 25. FIG.

25 is a flowchart showing an operation control program for controlling the operation of the compressor 10. The control computer C controls the operation of the compressor 10 based on the operation control program shown in the flowchart. The operation control of the compressor 10 will be described below in accordance with the operation control program shown in the flowchart. 25 has steps S1 to S7 and S18. Steps S1 to S7 are the same as those in FIG. 5 except that the electromagnetic three-way valve 48 is replaced with the electromagnetic solenoid 248.

When the compressor 10 is in the stopped state and the solenoid 248 is in the element state, the valve body 242 is disposed at the communication position shown in Fig. 23 by the spring force of the second return spring 252. do.

As shown in Fig. 23, in step S1, in the case of YES, that is, in the compressor operation start mode, in step S2, the control computer C starts to energize the solenoid 248. When the electromagnetic solenoid 248 is supplied with electric current, the valve body 242 is disposed at the cutoff position shown in FIG. 24 against the spring force of the second return spring 252, and the valve hole 891 is closed. As a result, the suction chamber 142 is blocked from the communication chamber 88.

In the case of YES in step S3, that is, when time ta has elapsed from the start of energization to the electromagnetic solenoid 248, the control computer C is energized to the electromagnetic clutch 25 in step S4. Initiate. As a result, the electromagnetic clutch 25 shifts from the blocked state to the connected state, and the rotation shaft 21 and the swash plate 23 start rotation.

In the case of YES in step S5, that is, when time tb has elapsed from the energization start to the electromagnetic clutch 25, in step S6, the control computer C energizes the electromagnetic solenoid 248. Stop. When the current supply to the electromagnetic solenoid 248 is stopped, the valve body 242 is disposed from the cutoff position shown in FIG. 24 to the communication position shown in FIG. 23 by the spring force of the second return spring 252. Thereby, the valve hole 891 is opened and the communication chamber 88 communicates with the suction chamber 142. Therefore, the refrigerant in the suction chamber 142 flows into the in-axis passage 31 via the valve hole 891 and the communication chamber 88.

After stopping the energization to the electromagnetic solenoid 248, in step S7, the control computer C determines whether or not the compressor operation stop mode is based on the comparison between the detected temperature and the target temperature. In step S7, in the case of YES, that is, in the compressor operation stop mode, in step S18, the control computer C stops energization to the electromagnetic clutch 25. After the process of step S18, the control computer C shifts to step S1.

The torque waveform T1 in FIG. 26 is an example of torque fluctuations. When energization is started by the electromagnetic clutch 25, the torque fluctuates. However, when starting the energization of the electromagnetic clutch 25, the electromagnetic solenoid 248 is energized before this start, and after energizing the electromagnetic clutch 25, the electricity supply to the electromagnetic solenoid 248 is stopped, The sudden torque fluctuation (variation part T11 in the torque waveform T1) when the energization of the clutch 25 is started is suppressed.

12th Embodiment has the following advantages.

(2-1) In the state where the electromagnetic solenoid 248 is excited, the valve body 242 is arrange | positioned at the interruption | blocking position shown in FIG. When the valve body 242 is arrange | positioned at the interruption position, the suction chamber 142 which is the suction pressure area | region in the compressor 10 is cut off from the communication chamber 88. As shown in FIG. Therefore, when the operation of the compressor 10 is started, that is, when the rotation of the rotary shaft 21 is started, the rotation of the rotary shaft 21 is started after the valve body 242 has been disposed in advance in the blocking position. . For this reason, there is no inflow of refrigerant from the suction chamber 142 to the communication chamber 88 and the in-axis passageway 31. Therefore, sudden torque fluctuation is suppressed and starting shock is alleviated.

(2-2) The opening / closing plate 90 for blocking the suction chamber 142 in the compressor 10 from the communication chamber 88 has a plate shape. Therefore, the volume of the communication chamber 88 which accommodates the opening-closing plate 90 can be made small. Therefore, the amount of refrigerant compressed in the front compression chamber 271 or the rear compression chamber 281 when the valve body 242 is in the shutoff position is small. As a result, the effect of suppressing the torque fluctuation, that is, the effect of reducing the starting shock is high.

(2-3) When the electromagnetic solenoid 248 is demagnetized, the valve body 242 returns to the communication position by the spring force of the second return spring 252. The use of the second return spring 252 is a simple configuration for returning the valve body 242 to the communication position.

(2-4) For example, when the electromagnetic solenoid 248 cannot be excited, the valve body 242 is maintained in the communication position by the spring force of the second return spring 252 in the pressure chamber 262. do. For this reason, when the compressor 10 starts to operate, the refrigerant in the suction chamber 142 passes through the communication chamber 88 and the shaft passage 31 to the front compression chamber 271 and the rear compression chamber 281. Inflow. That is, even when the electronic solenoid 248 cannot be excited, cooling is performed normally.

(2-5) When the valve body 242 closes the valve hole 891, for example, when the refrigerant leaks from the suction chamber 142 to the communication chamber 88 through the valve hole 891, the starting shock is alleviated. Falls. However, in this embodiment, in the state where the flat sealing surface 901 of the opening / closing plate 90 is in surface contact with the flat valve seat surface 892, the communication chamber 88 is reliably shut off from the suction chamber 142. do. Therefore, when the valve body 242 closes the valve hole 891, the refrigerant is prevented from leaking from the suction chamber 142 to the communication chamber 88 through the valve hole 891.

27 describes a thirteenth embodiment. The device configuration is the same as in the case of the twelfth embodiment.

In the thirteenth embodiment, the device configuration is the same as in the case of the twelfth embodiment, but when the energization is started to the electromagnetic clutch 25 as indicated by the energization start section K21 in the clutch waveform K2. The point of gradually increasing the amount of energized to is different from that of the twelfth embodiment. After the supply current value to the electromagnetic clutch 25 becomes maximum, energization to the electromagnetic solenoid 248 is stopped. By such energization start to the electromagnetic clutch 25, the fluctuation | variation of the fluctuation part T21 in the torque waveform T2 which shows a torque fluctuation is suppressed rather than the case of 12th Embodiment.

For example, in the conventional fixed displacement piston compressor without a switching part, the torque at the start is large, that is, the load on the electromagnetic clutch 25 is large. For this reason, if the amount of energization gradually increases similarly to the present embodiment, slippage occurs in the electromagnetic clutch 25. Therefore, it is difficult to secure the reliability of the electromagnetic clutch 25.

In this embodiment, the torque at the start is small, that is, the load on the electromagnetic clutch 25 is small. For this reason, operation control which gradually increases the energization amount with respect to the electromagnetic clutch 25 is possible.

28A and 28B describe a fourteenth embodiment. The same code | symbol is used for the same structural part as 12th Embodiment.

The valve body 242A includes an opening / closing plate 90, a movable iron core 251A, and a transfer rod 92. The movable iron core 251A is slidably fitted into the pressure recess 260. The transfer rod 92 is integrally formed with the movable iron core 251A. The movable iron core 251A partitions the pressure chamber 262 in the pressure recess 260. The first return spring 94 is disposed between the movable iron core 251A and the partition wall 89. The first return spring 94 elastically supports the valve body 242A in the direction in which the movable iron core 251A is pushed into the pressure recess 260. When the electromagnetic solenoid 248 is excited, the electromagnetic driving force of the electromagnetic solenoid 248 drives the valve body 242A in the direction to push the movable core 251A into the pressure recess 260. The first return spring 94 functions as a holding spring that holds the valve body 242A in the shut off position.

In FIG. 28A, the valve body 242A is in the shutoff position in which the valve hole 891 is closed, and in FIG. 28B, the valve body 242A is in a communication position connecting the valve hole 891. When the electromagnetic solenoid 248 is in an excited state, the valve body 242A is in the blocking position shown in FIG. 28A by the electromagnetic force of the electromagnetic solenoid 248. The timing at which the electromagnetic solenoid 248 is excited is the same as in the case of the twelfth embodiment. When the operation of the compressor 10 is in the stopped state, the valve body 242A is held at the cutoff position shown in FIG. 28A by the spring force of the first return spring 94.

If the solenoid 248 is energized before the compressor 10 starts to operate, and then the operation of the compressor 10 starts, since the valve body 242A is in the cutoff position, the starting shock is in the case of the twelfth embodiment. Are equally relaxed.

When the solenoid 248 is demagnetized after the operation of the compressor 10 is started, the valve body 242A is released from the electromagnetic force of the solenoid 248. Since the refrigerant in the shaft passage 31 and the refrigerant in the communication chamber 88 are sucked into the front compression chamber 271 (see FIG. 21) and the rear compression chamber 281, the suction chamber 142 by this suction action. Differences occur between the pressure in the c) and the pressure in the communication chamber 88. Therefore, the opening / closing plate 90 resists the spring force of the first return spring 94 and falls off from the valve seat surface 892. When the open / close plate 90 is separated from the valve seat surface 892, the refrigerant in the suction chamber 142 is also sucked into the communication chamber 88 via the valve hole 891. Therefore, the pressure in the suction chamber 142 is lower than the pressure in the pressure chamber 262. That is, a difference occurs between the pressure in the suction chamber 142 and the pressure in the pressure chamber 262.

The spring force of the first return spring 94 is the first return spring 94 due to the differential pressure generated between the pressure in the suction chamber 142 and the pressure in the pressure chamber 262 when the compressor 10 is operated. It is set to the size that will shrink. That is, the spring force of the 1st return spring 94 is set so that it may yield by the said differential pressure. Therefore, when the compressor 10 is operated, the differential pressure generated between the pressure in the suction chamber 142 and the pressure in the pressure chamber 262 overcomes the spring force of the first return spring 94 and the valve body 242A. ) Is maintained at the communication position shown in Fig. 28B.

14th Embodiment has the same advantage as (2-1) and (2-4) in 12th Embodiment. When the electromagnetic solenoid 248 is excited, the valve body 242A can be reliably held in the cutoff position. By appropriately setting the spring force of the first return spring 94, when the electromagnetic solenoid 248 is in the element state, when the compressor 10 is operated, the valve body 242A is disposed in the communication position and the cooling is assuredly. Is done.

29A and 29B describe a fifteenth embodiment. The same code | symbol is used for the same structural part as 12th Embodiment.

In the end wall 40 of the rear housing 14, the spool-shaped valve body 342 is slidably fitted in the pressure recess 611 which is in the cylinder of the cylinder 41. As shown in FIG. The valve body 342 includes a disk-shaped piston portion 43, a cylindrical portion 44, and a movable iron core portion 345. The cylinder 442 is an internal passage of the valve body 342. The piston portion 43 partitions the pressure chamber 612 in the pressure recess 611.

The groove 443 is formed in the outer peripheral surface of the cylindrical part 44 so that the suction chamber 142 may communicate with the pressure chamber 612. The pressure in the pressure chamber 612 corresponds to the pressure in the suction chamber 142, and the pressure (suction pressure) in the suction chamber 142 is opposed to the pressure in the pressure chamber 612 via the valve body 342. do. An fitting hole 403 is formed through the end wall 40, and an accommodation cylinder 346 is fitted into the fitting hole 403. The fixed iron core 364 is accommodated in the accommodation barrel 346. The movable iron core portion 345 is fitted into the receiving cylinder 346 so as to face the fixed iron core 364. The coil 365 is disposed on the outer circumferential surface of the accommodation cylinder 346. When the coil 365 is energized, the movable iron core 345 is attracted to the fixed iron core 364. The fixed iron core 364, the movable iron core 345, and the coil 365 constitute an electromagnetic solenoid 347 as an electromagnetic drive unit.

The guide cylinder 45 surrounds the rotation axis 210. When the valve body 342 approaches the end wall 40, the volume of the pressure chamber 612 decreases. The electromagnetic solenoid 347, the valve body 342, and the 1st return spring 47 comprise a switching part. The switching section communicates with the suction chamber 142, which is a part of the suction pressure region in the compressor 10, in communication with the front outlet 312 and the rear outlet 313 of the in-axis passage 31, and the suction chamber 142. Can be switched to a blocking state for blocking the front exit 312 and the rear exit 313. The first return spring 47 functions as a retaining spring that holds the valve body 342 in the shut off position.

In the state shown in FIG. 29B, the entire inlet 441 is positioned at the position exposed to the suction chamber 142, and the shaft passage 31 of the cylinder 451 and the cylindrical portion 44 of the guide cylinder 45 is positioned. It communicates with the suction chamber 142 via the cylinder 442 and the inlet 441. In the state shown in FIG. 29A, the entire inlet 441 is in a position deep into the pressure recess 611, and the in-axis passage 31 is blocked from the suction chamber 142. Fig. 29B shows a state where the valve body 342 is in a communication position communicating with the in-axis passage 31 and the suction chamber 142, and Fig. 29A shows the valve body 342 with the in-axis passage 31 and the suction chamber. The state in the blocking position which blocks 142 is shown.

When the electromagnetic solenoid 347 is in an excited state, the valve body 342 is in the blocking position shown in FIG. 29A by the electromagnetic force of the electromagnetic solenoid 347. The timing with which the electromagnetic solenoid 347 is excited is the same as that of the twelfth embodiment. When the operation of the compressor 10 is in the stopped state, the valve body 342 is held at the cutoff position shown in Fig. 29A by the spring force of the first return spring 47. That is, the switching unit has a communication state (state shown in FIG. 29B) in which the suction chamber 142 communicates with the front outlet 312 and the rear outlet 313 of the in-cylinder passage 31, and the suction chamber 142 is in the shaft. It is possible to switch to a shutoff state (state shown in Fig. 29A) which cuts off from the front outlet 312 and the rear outlet 313 of the passage 31.

If the solenoid 347 is energized before the compressor 10 starts to operate, and then the operation of the compressor 10 starts, the starting shock is in the case of the twelfth embodiment because the valve body 342 is in the shut off position. Are equally relaxed.

When the solenoid 347 is demagnetized after the operation of the compressor 10 starts, the valve body 342 is released from the electromagnetic force of the solenoid 347. Since the refrigerant in the cylinder 451 and the shaft passage 31 is sucked into the front compression chamber 271 (see FIG. 21) and the rear compression chamber 281, the pressure in the suction chamber 142 is caused by this suction action. And a difference between the pressure in the pressure chamber 612. The spring force of the first return spring 47 is the first return spring 47 due to the differential pressure generated between the pressure in the suction chamber 142 and the pressure in the pressure chamber 612 when the compressor 10 is operated. It is set to the size that will shrink. Therefore, when the compressor 10 is operated, the differential pressure generated between the pressure in the suction chamber 142 and the pressure in the pressure chamber 612 overcomes the spring force of the first return spring 47 and the valve body. 342 is maintained at the communication position shown in Fig. 29B.

The fifteenth embodiment has the same advantages as the twelfth embodiment.

30A and 30B describe the sixteenth embodiment. The same code | symbol is used for the same structural part as 15th Embodiment.

The guide cylinder 45A fitted to the cylindrical portion 44 of the valve body 342 has a bottomed cylindrical shape and is formed separately from the rear cylinder block 12, the rotary shaft 21, and the like. The bottom wall of the guide cylinder 45A is in contact with the end face 122 of the rear cylinder block 12, and the guide cylinder 45A is allowed to move in the radial direction of the rotation shaft 21 with respect to the rotation shaft 21. It fits into the cylindrical part 44 of the valve body 342. A communication port 452 is formed in the bottom wall of the guide cylinder 45A so as to communicate the inside 451 of the guide cylinder 45A and the shaft passage 31, and the bottom wall of the guide cylinder 45A and the piston 43 The first return spring 47 is disposed therebetween. In FIG. 30A, the valve body 342 is disposed in the shut off position, and in FIG. 30B, the valve body 342 is disposed in the communicating position.

For example, when the coolant leaks from between the valve body 342 and the cylinder 41 or between the valve body 342 and the guide cylinder 45A when the valve body 342 is in the shut-off position, The mitigating effect is lowered.

However, in the present embodiment, the guide cylinder 45A is fitted to the cylindrical portion 44 of the valve body 342 so as to allow movement in the radial direction of the rotary shaft 21 with respect to the rotary shaft 21. . For this reason, the shaft core 413 of the pressure recess 611 is matched with the shaft core 453 of the guide cylinder 45A. Therefore, the clearance between the cylindrical part 44 of the valve body 342 and the cylinder 41 and the clearance between the cylindrical part 44 and the guide cylinder 45A of the valve body 342 can be made small. Therefore, leakage of the refrigerant along the main surface of the cylindrical portion 44 of the valve body 342 can be prevented.

31A and 31B describe the seventeenth embodiment. The same code | symbol is used for the same structural part as 15th Embodiment.

A piston 69 is slidably fitted in the cylinder 41, and a movable iron core 345 is integrally formed in the piston 69. The piston 69 partitions the pressure chamber 612 in the pressure recess 611. The transfer rod 70 is connected to the piston 69.

The small circumferential body 71, the large circumferential body 72, the transmission rod 70, and the piston 69 constitute a valve body that partitions the pressure chamber 612 in the pressure recess 611.

FIG. 31A shows a state where the main columnar body 71 closes the front outlet 312 and the major columnar body 72 closes the rear outlet 313. The front outlet 312 and the rear outlet 313 are shown in FIG. Is blocked from the in-axis passageway 31A. 31B shows a state in which the wish columnar body 71 opens the front outlet 312, and the major columnar body 72 opens the rear outlet 313, and the front outlet 312 and the rear outlet 313 are shown. Communicates with the in-axis passageway 31A. When the electromagnetic solenoid 347 is energized, the small circumferential body 71 and the large circumferential body 72 are blocked by the spring force of the first return spring 73 from the communication position shown in FIG. 31B and shown in FIG. 31A. Is placed. The 1st return spring 73 functions as a holding | maintenance spring which hold | maintains the small circumferential body 71 and the large circumferential body 72 in a interruption position.

The seventeenth embodiment has the same advantages as the twelfth embodiment. In addition, in the seventeenth embodiment, the refrigerant that can flow into the front compression chamber 271 and the rear compression chamber 281 when the main circumferential body 71 and the large circumferential body 72 are in the blocking position is the front outlet 312. ) And only the refrigerant in the rear outlet 313 and in the front communication path 32 and the rear communication path 33, the relaxation effect of the starting shock is higher than in the case of the twelfth embodiment.

In addition, when the piston 69 is configured to be relatively rotatable with respect to the transmission rod 70, the first return spring 73 can be prevented from being relatively rotated with respect to the rotation shaft 21. Therefore, wear damage of the first return spring 73 or the rotary shaft 21 due to the relative rotation between the first return spring 73 and the rotary shaft 21 can be avoided. Alternatively, the large columnar body 72 may be configured to be relatively rotatable with respect to the first return spring 73.

32A and 32B describe an eighteenth embodiment. The same code | symbol is used for the same structural part as 17th Embodiment.

As shown in FIG. 32A, when the large columnar body 72 is in a position to close the rear outlet 313, the disc 74 is located upstream of the front outlet 312 in the in-axis passage 31A. Therefore, the refrigerant in the shaft passage 31A cannot flow into the front compression chamber 271 through the front outlet 312. As shown in FIG. 32B, when the large columnar body 72 is in a position to open the rear outlet 313, the disc 74 is located downstream of the front outlet 312 in the in-axis passage 31A. Therefore, the refrigerant in the shaft passage 31A can flow into the front compression chamber 271 through the front outlet 312. When energization to the electromagnetic solenoid 347 is performed, the cylinder 75 is arrange | positioned by the spring force of the 1st return spring 73 from the communication position shown in FIG. 32B to the interruption | blocking position shown in FIG. 32A. The disc 74, the large cylindrical surface 72, the transfer rod 70, and the piston 69 constitute a valve body that partitions the pressure chamber 612 in the pressure recess 611.

The eighteenth embodiment has the same advantages as the seventeenth embodiment.

33A and 33B describe a nineteenth embodiment. The same code | symbol is used for the same structural part as 17th Embodiment.

In the state where the pin 76 was inserted into the end wall 752 of the cylinder 75, the cylinder 75 can slide in the in-axis passageway 31A. The cylinder 75 and the piston 69 comprise the valve body which partitions the pressure chamber 612 in the pressure recessed part 611. As shown in FIG.

FIG. 33B shows a state in which the small-diameter barrel portion 77 closes the front outlet 312, and a state in which the large-diameter barrel portion 78 closes the rear outlet 313. As a result, the front outlet 312 and the rear outlet 313 are cut off from the cylinder 750 of the cylinder 75. FIG. 33A shows a state where the communication port 771 of the small-diameter tubular portion 77 communicates with the front outlet 312, and the communication port 781 of the large-diameter tubular portion 78 communicates with the rear outlet 313. The front outlet 312 and the rear outlet 313 communicate with the cylinder 750. When the electromagnetic solenoid 347 is energized, the cylinder 75 is arrange | positioned by the spring force of the 1st return spring 73 from the communication position shown in FIG. 33A to the interruption position shown in FIG. 33B.

19th Embodiment has the same advantage as 17th Embodiment.

Fig. 34 shows a compressor 10A having a migraine piston 95 according to the twentieth embodiment. The solenoid 248 and the valve body 242 are formed in the rear housing 14. 20th Embodiment has the same advantage as 12th Embodiment.

You may change the said embodiment as follows.

3 and 4, the discharge refrigerant supplied to the working pressure chamber 412 may be introduced from a portion of the external refrigerant circuit upstream of the heat exchanger 37. As shown in FIG.

The electromagnetic three-way valve 48 shown in FIGS. 12 and 13 may be connected to the rear housing 14 to incorporate it.

The electromagnetic on-off valve 67 of FIGS. 8-9A and the electromagnetic on-off valve 67A of FIGS. 10-11A may be connected to the rear housing 14, and may be joined.

The check valve 68 of FIGS. 8-11A may be connected to the housing of the compressor 10, and may be joined.

The oil separator 79 of FIGS. 17-18B may be connected to the housing of the compressor 10, and may be joined.

In the case where the electromagnetic three-way valve 48 of Figs. 3 and 4 is excited, the valve body 42 is disposed at the communication position, and the valve body 42 is set to the element. It may be arranged in the blocking position.

In the case where the solenoid 248 of FIGS. 23 and 24 is excited, the valve body 242 is arranged in a communication position, and the valve body 242 is arranged in a shutoff position when the solenoid 248 is demagnetized. You may also

In the case where the solenoid 347 of FIGS. 29A and 29B is excited, the valve body 342 is disposed in the communication position, and when the solenoid 347 is demagnetized, the valve body 342 is disposed in the shut off position. You may also

The pressure chamber 262 of FIGS. 23 and 24 may be always cut off from the suction chamber 142, and the pressure chamber 262 may be in communication with the atmosphere.

You may form the 1st rotary valve 35 and the 2nd rotary valve 36 separately from the rotating shaft 21, respectively.

1 is a side sectional view of an entire compressor showing a first embodiment.

2A is a cross-sectional view taken along the line 2A-2A of FIG.

FIG. 2B is a cross-sectional view taken along the line 2B-2B of FIG.

3 is a partially enlarged view of FIG. 1.

4 is an enlarged view in which the valve body is moved from FIG. 3.

5 is a flowchart showing an operation control program of the compressor of FIG.

FIG. 6 is a timing chart showing torque fluctuation by the program of FIG.

7 is a timing chart showing a second embodiment.

Fig. 8 is a side sectional view of the entire compressor of the third embodiment.

9A is a partially enlarged view of the solenoid valve switched from FIG.

9B is a timing chart of the compressor of FIG.

10 is a partially enlarged side sectional view of the compressor of the fourth embodiment.

FIG. 11A is a sectional view of the solenoid valve switched from FIG. 10. FIG.

11B is a timing chart of the compressor of FIG.

12A is a partially enlarged side sectional view of the compressor of the fifth embodiment.

Fig. 12B is a sectional view of the solenoid valve switched from Fig. 12A.

Fig. 13 is a side sectional view of the entire compressor of the sixth embodiment.

FIG. 14 is a sectional view of the solenoid valve switched from FIG.

Fig. 15A is a partially enlarged side sectional view of the compressor of the seventh embodiment.

15B is a cross-sectional view of the valve body moved from FIG. 15A.

Fig. 16A is a partially enlarged side sectional view of the compressor of the eighth embodiment.

16B is a cross-sectional view of the valve body moved from FIG. 16A.

Fig. 17 is a side sectional view of the entire compressor of the ninth embodiment.

18A is an enlarged partial view of FIG.

FIG. 18B is a cross-sectional view of the valve body moved from FIG. 18A. FIG.

Fig. 19A is a partially enlarged side sectional view of the compressor of the tenth embodiment.

Fig. 19B is a sectional view of the solenoid valve switched from Fig. 19A.

20 is a side cross-sectional view of the entire migrating piston compressor of the eleventh embodiment.

21 is a side sectional view of the entire compressor of a twelfth embodiment;

FIG. 22A is a cross-sectional view taken along the line 22A-22A in FIG.

Fig. 22B is a cross sectional view along the 22B-22B line in Fig. 21;

FIG. 23 is a partially enlarged cross-sectional view of FIG.

24 is an enlarged view in which the valve body is moved from FIG.

FIG. 25 is a flow chart showing an operation control program of the compressor of FIG.

FIG. 26 is a timing chart showing torque fluctuation by the program of FIG.

27 is a timing chart showing a thirteenth embodiment.

Fig. 28A is a partially enlarged sectional view of the compressor of the fourteenth embodiment.

FIG. 28B is a sectional view in which the valve body is moved from FIG. 28A.

29A is a partially enlarged cross-sectional view of a compressor of a fifteenth embodiment.

FIG. 29B is a sectional view of the valve body moved from FIG. 29A; FIG.

30A is a partially enlarged cross-sectional view of the compressor of the sixteenth embodiment.

30B is a cross-sectional view of the valve body moved from FIG. 30A.

Fig. 31A is a partially enlarged side sectional view of the compressor of the seventeenth embodiment.

FIG. 31B is a sectional view in which the valve body is moved from FIG. 31A.

32A is a partially enlarged side sectional view of the compressor of the eighteenth embodiment;

32B is a cross-sectional view of the valve body moved from FIG. 32A.

33A is a partially enlarged side sectional view of the compressor of the nineteenth embodiment;

33B is a sectional view of the valve body moved from FIG. 33A.

34 is a side sectional view of the entire compressor of the twentieth embodiment;

Claims (28)

A refrigerant suction structure in a fixed displacement piston type compressor, wherein the compressor is accommodated in a rotary shaft connected to an external drive source via a clutch, a plurality of cylinder bores arranged around the rotary shaft, and the cylinder bore, respectively. A plurality of pistons defining a compression chamber in each of the cylinder bores, respectively, and a cam body integrated with the rotary shaft, the cam body interlocking rotation of the rotary shaft to each of the pistons. And a rotary valve having an intake pressure region and an introduction passage for introducing refrigerant into the respective compression chambers from the intake pressure region, wherein the rotary valve rotates integrally with the rotary shaft, Has a portion in the compressor, and the introduction passages deliver refrigerant toward each of the compression chambers. Have one outlet, The coolant suction structure has a switching part that can be switched to a communication state and a cutoff state, The switching portion in the communicating state allows a portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage, The switching unit in the shut-off state blocks a portion of the suction pressure region in the compressor from the outlet of the inlet passage, The switch unit, A valve body which can be arranged to be switched between a communication position and a shut-off position, wherein the valve body in the communication position allows a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage, The valve body is for blocking a part of the suction pressure region in the compressor from the outlet of the introduction passage; A working pressure chamber for introducing an operating pressure for acting on the valve body for disposing the valve body in the communication position; It is provided with an operating pressure providing unit for imparting the operating pressure to the working pressure chamber, The pressure in the suction pressure region is opposed to the pressure in the working pressure chamber through the valve body. The method of claim 1, The switching portion has a working pressure recess, and the valve body is slidably fitted in the working pressure recess, whereby the valve body partitions the working pressure chamber in the working pressure recess, The pressure in the portion of the suction pressure region in the compressor is opposed to the pressure in the working pressure chamber through the valve body, And the switching section includes a first return spring for returning the valve body from the communication position to the shutoff position. The method of claim 2, The introduction passage has an inlet for receiving refrigerant from the suction pressure region, And the valve body is arranged to block the inlet of the inlet passage from a portion of the suction pressure region in the compressor when the switch is in the shutoff state. The method of claim 3, The inlet of the introduction passage is located at an end surface of the rotary valve, the outlet of the introduction passage is located at a peripheral surface of the rotary valve, The axis of rotation of the rotary valve crosses the cross section, The refrigerant suction structure, A valve accommodating chamber for rotatably accommodating the rotary valve; It has a guide cylinder which surrounds the said rotating axis in the exterior of the said valve accommodation chamber, The inside of the guide cylinder communicates with the inlet of the introduction passage, The valve body is slidably fitted to the guide cylinder, the valve body has an internal passage communicating with the cylinder of the guide cylinder, and the inner passage has an inlet for receiving refrigerant from the suction pressure region. Have, When the valve body is in the shutoff position, the inlet of the inner passage is shielded by entering into the working pressure recess, And the inlet of the inner passage is exposed outside the working pressure recess to expose a portion of the suction pressure region in the compressor when the valve body is in the communication position. The method of claim 4, wherein The guide cylinder is formed separately from the members of the compressor other than the valve body, and is configured to allow movement in the radial direction of the rotation shaft with respect to the members of the compressor other than the valve body. The method of claim 2, The introduction passage has an inlet for receiving refrigerant from the suction pressure region, the inlet of the introduction passage is located at the end face of the rotary valve, The outlet of the introduction passage is located on the main surface of the rotary valve, The valve body is fitted into the introduction passage from the inlet of the introduction passage, And the valve body is arranged to block an outlet of the introduction passage from a portion of the suction pressure region in the compressor in the inside of the introduction passage when the switching section is in the blocking state. The method of claim 6, The introduction passage has an in-axis passage located inside the rotation shaft, the in-axis passage extending in the direction of the rotation axis of the rotation shaft, The outlet of the introduction passage communicates with the in-axis passage through the main surface of the rotary shaft, The valve body is fitted into the in-axis passage so as to be slidable in the direction of the rotational axis in the introduction passage. The valve body can be arranged to be switched to the communication position and the cutoff position by being moved in the direction of the rotation axis in the in-axis passage, The valve body in the cutoff position blocks the outlet of the introduction passage with respect to the in-axis passage. The method of claim 3, The switching portion has a flat valve seat surface, the valve body has a flat seal surface, and the seal surface is formed on the valve seat surface in a state where the valve body is in the shutoff position. Refrigerant suction structure in surface contact. The method according to any one of claims 1 to 8, The compressor has a discharge pressure region, The operating pressure applying unit has an inflow passage from the discharge pressure region to the operating pressure chamber, And a refrigerant in the discharge pressure region is introduced into the working pressure chamber through the inflow passage. The method of claim 9, An oil separator is formed on the inflow passage, and the oil separator separates oil from the refrigerant in the discharge pressure region. A constriction is formed in a portion of the inflow passage downstream from the oil separator, A portion of the inflow passage downstream from the oil separator functions as an oil passage for guiding oil separated by the oil separator to the narrowing portion. The method of claim 9, The discharge pressure region has a portion in the compressor, A portion of the discharge pressure region in the compressor is connected to a portion of the suction pressure region in the compressor via an external refrigerant circuit, and the external refrigerant circuit has a portion of the discharge pressure region, The inflow passage is connected to a portion of the discharge pressure region of the external refrigerant circuit, The operating pressure providing unit includes an electromagnetic opening / closing valve and a check valve for opening and closing the inflow passage, And the check valve is disposed in a portion of the external refrigerant circuit downstream of the connection portion between the portion of the discharge pressure region and the inflow passage in the external refrigerant circuit. The method according to any one of claims 1 to 8, The operating pressure providing unit has an electromagnetic three-way valve (3-way), The working pressure chamber is connected to the electromagnetic three-way valve through a common passage, The electromagnetic three-way valve is connected to the discharge pressure region through a supply passage, The electromagnetic three-way valve is connected to the suction pressure region through the discharge passage, The electromagnetic three-way valve is configured to be switchable in a first state in which the common passage is in communication with the supply passage, and in a second state in which the common passage is in communication with the discharge passage. The method according to any one of claims 1 to 8, The compressor, A cylinder block having the cylinder bore; And a rear housing connected to the cylinder block, And the rear housing has a suction chamber therein, and the working pressure chamber is partitioned within the rear housing. A refrigerant suction structure in a fixed displacement piston type compressor, wherein the compressor is accommodated in a rotary shaft connected to an external drive source via a clutch, a plurality of cylinder bores arranged around the rotary shaft, and the cylinder bore, respectively. Thereby, a plurality of pistons respectively partitioning the compression chamber in each of the cylinder bores, the cam body integrated with the rotary shaft, the cam body interlocks rotation of the rotary shaft to each of the pistons, the suction pressure region, and A rotary valve having an introduction passage for introducing refrigerant from the suction pressure region into each of the compression chambers, the rotary valve integrally rotating with the rotary shaft, the suction pressure region having a portion in the compressor, and The introduction passage has an outlet for delivering refrigerant toward each of the compression chambers, The coolant suction structure has a switching unit that can be switched between a communicating state and a blocked state, The switching portion in the communicating state allows a portion of the suction pressure region in the compressor to communicate with the outlet of the introduction passage, The switching unit in the shut-off state blocks a portion of the suction pressure region in the compressor from the outlet of the inlet passage, The switch unit, A valve body which can be arranged to be switched between a communication position and a shut-off position, wherein the valve body in the communication position allows a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage, The valve body is for blocking a part of the suction pressure region in the compressor from the outlet of the introduction passage; A refrigerant suction structure comprising an electromagnetic drive unit for driving the valve body by an electromagnetic force. The method of claim 14, The switching section includes a second return spring for returning the valve body to the communication position, And the electromagnetic drive unit drives the valve body from the communication position toward the blocking position. The method of claim 15, The switching portion has a pressure recess, and the valve body is slidably accommodated in the pressure recess, whereby the valve body partitions a pressure chamber in the pressure recess, The pressure chamber communicates with a portion of the suction pressure region in the compressor, The pressure in the portion of the suction pressure region in the compressor is opposed to the pressure in the pressure chamber through the valve body, The second return spring is accommodated in the pressure chamber, the second return spring elastically supports the valve body in a direction protruding from within the pressure recess, And the electromagnetic drive unit drives the valve body to push into the pressure recess. The method of claim 14, The switching portion has a pressure recess, and the valve body is slidably accommodated in the pressure recess, whereby the valve body partitions a pressure chamber in the pressure recess, The pressure chamber communicates with a portion of the suction pressure region in the compressor, The pressure in the portion of the suction pressure region in the compressor is opposed to the pressure in the pressure chamber through the valve body, The switching section includes a holding spring which tries to retain the valve body in the shut-off position by pushing the valve body into the pressure recess, And the electromagnetic drive unit drives the valve body from the communication position toward the blocking position. The method of claim 17, The introduction passage has an inlet for receiving refrigerant from the suction pressure region, And the valve body is arranged to block the inlet of the inlet passage from a portion of the suction pressure region in the compressor when the switch is in the shutoff state. The method of claim 18, The switch portion has a flat valve seat surface, the valve body has a flat seal surface, and the seal surface is in surface contact with the valve seat surface in a state where the valve body is in the shutoff position. . The method of claim 17, The introduction passage has an inlet for receiving refrigerant from the suction pressure region, the inlet of the introduction passage is located at the end face of the rotary valve, The outlet of the introduction passage is located on the main surface of the rotary valve, The axis of rotation of the rotary valve crosses the cross section, The refrigerant suction structure, A valve accommodating chamber for rotatably accommodating the rotary valve; It has a guide cylinder which surrounds the said rotating axis in the exterior of the said valve accommodation chamber, The inside of the guide cylinder communicates with the inlet of the introduction passage, The valve body is slidably fitted to the guide cylinder, the valve body has an internal passage communicating with the cylinder of the guide cylinder, and the inner passage has an inlet for receiving refrigerant from the suction pressure region. Have, When the valve body is in the shutoff position, the inlet of the inner passage is shut off by entering into the pressure recess, And the inlet of the inner passage is located outside of the pressure concave portion when the valve body is in the communication position, thereby exposing it into a portion of the suction pressure region in the compressor. The method of claim 20, The guide cylinder is formed so as to be separate from the members of the compressor other than the valve body, so that the movement of the rotary shaft in the radial direction with respect to the members of the compressor other than the valve body is permitted. Refrigerant suction structure. The method according to any one of claims 14 to 17, The introduction passage has an inlet for receiving refrigerant from the suction pressure region, the inlet of the introduction passage is located at the end face of the rotary valve, The outlet of the introduction passage is located on the main surface of the rotary valve, The valve body is fitted into the introduction passage from the inlet of the introduction passage, And the valve body is arranged to block the outlet of the introduction passage from a portion of the suction pressure region in the compressor when the switching section is in the blocking state. The method of claim 22, The introduction passage has an in-axis passage located inside the rotation shaft, the in-axis passage extending in the direction of the rotation axis of the rotation shaft, The outlet of the introduction passage communicates with the in-axis passage through the main surface of the rotary shaft, The valve body is fitted into the in-axis passage so as to be slidable in the direction of the rotational axis in the introduction passage. The valve body can be arranged to be switched to the communication position and the cutoff position by being moved in the direction of the rotation axis in the in-axis passage, The valve body in the cutoff position blocks the outlet of the introduction passage with respect to the in-axis passage. The method according to any one of claims 14 to 17, The compressor, A cylinder block having the cylinder bore; And a rear housing connected to the cylinder block, And the rear housing has a suction chamber therein, and the valve body is disposed in the rear housing. As a operation control method in a fixed displacement piston compressor, The compressor includes a rotary shaft connected to an external drive source through a clutch, a plurality of cylinder bores arranged around the rotary shaft, and the cylinder bore, respectively, to define a compression chamber in each of the cylinder bores. A plurality of pistons and a cam body integrated with the rotary shaft, the cam body interlocks rotation of the rotary shaft to each of the pistons, and introduces refrigerant into the respective compression chambers from the suction pressure region and the suction pressure region. A rotary valve having an introduction passage therein, and a discharge pressure region, the rotary valve rotates integrally with the rotary shaft, the suction pressure region has a portion in the compressor, and the introduction passage has a respective Has an outlet for delivering refrigerant toward the compressor, The operation control method is to prepare a switching unit that can be switched between a communicating state and a blocked state, wherein the switching unit in the communicating state allows a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage. And the switching unit in the shut-off state blocks a part of the suction pressure region in the compressor from an outlet of the introduction passage, and the switching unit includes a valve body, an operating pressure chamber, and an operating pressure granting unit. A communication position allowing a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage, and a cutoff position for blocking a portion of the suction pressure region in the compressor from an outlet of the introduction passage. And the actuating pressure chamber is actuated on the valve body to arrange the valve body in the communication position. An operating pressure is introduced, the operating pressure applying unit applies the operating pressure to the operating pressure chamber, and the operating pressure providing unit includes a first state capable of supplying the refrigerant in the discharge pressure region to the operating pressure chamber and an undeliverable agent. Having a switching valve arranged to be switched in two states; When switching the clutch from the cutoff state to the connected state, the clutch is put into the connected state after the switching valve is set to the second state; And switching said switching valve to said first state after bringing said clutch into a connected state. The method of claim 25, The clutch is an electromagnetic clutch that is in a connected state connecting the rotary shaft to the external drive source by being magnetized, The driving control method, When switching the electromagnetic clutch from the demagnetization state to the excited state, gradually increasing the current supplied to the electromagnetic clutch to excite the electromagnetic clutch; And switching the switching valve from the second state to the first state after the value of the current becomes maximum. As a operation control method in a fixed displacement piston compressor, The compressor includes a rotary shaft connected to an external drive source through a clutch, a plurality of cylinder bores arranged around the rotary shaft, and each of the cylinder bores, each of which is formed in each of the cylinder bores by being accommodated in the cylinder bore. A plurality of pistons and a cam body integrated with the rotary shaft, the cam body interlocks rotation of the rotary shaft to each of the pistons, a suction pressure region, and a refrigerant in each of the compression chambers from the suction pressure region. A rotary valve having an introduction passage for introduction, the rotary valve integrally rotating with the rotary shaft, the suction pressure region having a portion in the compressor, the introduction passage directed toward each of the compressors Has an outlet for delivering the refrigerant, The operation control method is to prepare a switching unit that can be switched between a communicating state and a blocked state, wherein the switching unit in the communicating state allows a portion of the suction pressure region in the compressor to communicate with an outlet of the introduction passage. And the switching unit in the shut-off state blocks a part of the suction pressure region in the compressor from an outlet of the inlet passage, and the switching unit includes a valve body and an electromagnetic drive unit, and the valve body includes the It is possible to switch between a communication position allowing a portion of the suction pressure region to communicate with an outlet of the introduction passage, and a blocking position for blocking the portion of the suction pressure region in the compressor from an outlet of the introduction passage, The electromagnetic drive unit is capable of driving the valve body by an electromagnetic force, and the electromagnetic drive unit raises the valve body. Can be switched to the first state, and the valve body placed in the communication position to the second state to place the blocking position, The driving control method includes, when switching the clutch from the shutoff state to the connected state, putting the clutch in the connected state after setting the electromagnetic drive unit to the second state; And putting said electromagnetic drive part into said first state after bringing said clutch into a connected state. The method of claim 27, The clutch is an electromagnetic clutch that is in a connected state connecting the rotary shaft to the external drive source by being excited, The driving control method, When switching the electromagnetic clutch from the element state to the excited state, gradually increasing the current supplied to the electromagnetic clutch to excite the electromagnetic clutch; And operating the electronic drive unit after the value of the current reaches a maximum.

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