JP2008050962A - Variable displacement type gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure operation performance equivalent to conventional compressors while relaxing severity of control of shape accuracy of a bypass passage opening-closing means for varying displacement in a variable displacement gas compressor. <P>SOLUTION: The variable displacement gas compressor is provided with a compressor main body compressing refrigerant gas G sucked from a low pressure space such as a suction chamber or the like in a compression chamber 22, has the compression chamber 22 corresponding to a compression stroke and bypass passages 41, 42, 43 communicating with the low pressure space formed therein, and is provided with a flat spring member 46 displacing a plate surface 46a energized to a side of a condition blocking passage between the bypass passages 41, 42 to a side of a condition permitting passage between the bypass passages 41, 42 according to difference of pressure acting on a front and a reverse plate surface 46a, 46b. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a capacity variable type gas compressor, and more particularly to improvement of bypass passage opening / closing means for capacity switching.

  Conventionally, a gas compressor (compressor) for compressing a gas such as a refrigerant gas and circulating the gas through the air conditioning system is used in an air conditioning system (hereinafter referred to as an air conditioning system).

  Here, for example, a vane rotary type compressor is known as one of general compressors.

  This vane rotary type compressor is compressed inside a housing having a substantially cylindrical case with one end open and a head connected to one end surface of the case so as to close the one open end of the case. The machine body is housed.

  The compressor main body is a cylindrical rotor that rotates integrally with the rotation shaft, a cylinder that surrounds the outer peripheral surface of the rotor, a cylinder having an inner peripheral surface with a substantially elliptical cross-sectional contour, and projects from the outer peripheral surface of the rotor, A plurality of plate-like vanes provided on the rotor at equal angular intervals around the rotation axis, the rotor and the cylinder, which can be moved forward and backward so as to maintain the protruding tip in contact with the inner peripheral surface of the cylinder The two side blocks (front side block and rear side block) arranged so as to sandwich the rotor and cylinder from the both end face sides, respectively, and the two side blocks and rotor according to the rotation of the rotating shaft The volume of the plurality of compression chambers defined by the two vanes that follow each other in the rotational direction of the cylinder and the rotor repeats increasing and decreasing, respectively. Inhaled gas chamber (e.g., refrigerant gas) to compress, and is configured to discharge to the outside of the compressor body.

  In addition, some of these gas compressors can change the discharge amount when the compressed gas is discharged to the outside.

  For example, in a variable capacity compressor having the above-described vane rotary type compressor body, the side block portion of the components defining the compression chamber corresponding to the refrigerant gas compression stroke is used in the compression stroke. A bypass passage is formed to connect the corresponding compression chamber and a space relatively lower in pressure than the pressure in the compression chamber (for example, a suction chamber into which gas is introduced), and gas is bypassed in the bypass passage. A spool valve that selectively switches between a state that allows passage through the passage and a state that prevents passage is provided.

  When the spool valve closes the bypass passage to prevent passage, the gas is compressed at the rated compression ratio in the compression chamber, and a predetermined amount is discharged from the outlet (discharge port) of the compression chamber. Gas is discharged.

  On the other hand, when the spool valve opens the bypass passage and permits passage, a part of the gas in the compression chamber in the compression stroke flows out from the compression chamber in the compression stroke to the low pressure space via the bypass passage. However, the amount of gas in the compression chamber decreases, and the amount of gas discharged from the outlet (discharge port) of the compression chamber becomes less than a prescribed amount.

  Therefore, by appropriately controlling the operation of the spool valve, the gas discharge amount can be appropriately changed.

The spool valve described above has a pressure acting on the surface facing the compression chamber (internal pressure of the compression chamber) and a pressure acting on the opposite surface (back surface) (the high-pressure gas discharged from the compression chamber temporarily It is operated according to the difference with the hydraulic pressure of the lubricating oil or hydraulic oil that is stored in the discharge chamber and applied with high pressure in the discharge chamber, but the solenoid valve is used to switch whether the high-pressure lubricating oil is applied to the back side Thus, the state of allowing the passage of the bypass passage and the state of preventing the passage are switched (Patent Document 1).
Japanese Utility Model Publication No. 57-123991 (Japanese Utility Model Application No. 56-10017)

  By the way, the accuracy of the operation performance of the above-described spool valve as the bypass passage opening / closing means largely depends on the accuracy of the clearance between the spool valve body itself and the side block through which the valve body is inserted. It is necessary to strictly manage the accuracy of the combination of both.

  And, strict management of such component accuracy in order to ensure the desired operation performance leads to an increase in the manufacturing cost of the gas compressor, while strict management of such component accuracy is performed. Otherwise, the manufacturing cost can be suppressed, but the desired operation performance cannot be ensured.

  The present invention has been made in view of the above circumstances, and has a variable capacity capable of ensuring the same operational performance as the conventional one while relaxing the strict control of the shape accuracy of the bypass passage opening / closing means for switching capacity. An object is to provide a gas compressor.

  The gas compressor according to the present invention, as a bypass passage opening / closing means, is not a conventional spool valve whose operating performance is highly dependent on the shape and dimensional accuracy of parts, but to the extent that it depends on the quality of the material rather than the shape and dimensional accuracy. By applying a high leaf spring member, operational performance is ensured while alleviating the strictness of dimensional accuracy management of parts.

  That is, the variable capacity gas compressor according to the present invention includes a compressor body that compresses the gas sucked from the low-pressure space in the internal space (compression chamber), and corresponds to the compression process for the gas in the internal space. A bypass passage that connects the space portion and the low-pressure space is formed, and a bypass passage opening / closing means that switches between a state that allows passage of the bypass passage and a state that blocks passage is provided, and the state of the bypass passage opening / closing means In the variable capacity type gas compressor in which the discharge amount of the compressed gas is variable according to the above, the bypass passage opening / closing means is a biasing force based on the elastic force according to the difference in pressure acting on each of the front and back surfaces. Therefore, the plate surface is displaced between the state of blocking the bypass passage and blocking, and the allowable state of elastic deformation against the biasing force. Characterized by comprising a leaf spring member which is deformed.

  According to the capacity variable type gas compressor according to the present invention configured as described above, when the leaf spring member is biased by its own elastic force so that its plate surface closes the bypass passage, the bypass passage is Since it is closed, gas does not flow out of the compression chamber to the bypass passage even if the compression chamber moves to the compression stroke. Therefore, the gas is compressed at a predetermined compression ratio in the compression chamber, and is discharged from the compression chamber. A prescribed maximum amount of gas is discharged from the (discharge port).

  On the other hand, the bypass passage is closed by elastically deforming the leaf spring member against the biasing force based on its own elastic force according to the difference in pressure acting on the front and back plate surfaces of the leaf spring member. Away from and displaceable or deformed to allow passage of the bypass passage. At this time, part of the gas in the compression chamber in the compression stroke leaks to the low-pressure space via the bypass passage, and the amount of gas in the compression chamber decreases, and is discharged from the outlet (discharge port) of the compression chamber. The amount of gas produced will be less than the prescribed maximum amount.

  Therefore, the gas discharge amount can be appropriately changed by appropriately controlling the pressures acting on the front and back plate surfaces of the leaf spring member.

  Since the degree of dependence on the shape and dimensional accuracy of the switching performance of the operation by the leaf spring member is not as great as the conventional spool valve, the dimensional accuracy management of the parts can be made easier than before. The operation performance can be ensured while relaxing the accuracy control.

  According to the capacity variable type gas compressor according to the present invention, it is possible to ensure the operational performance while relaxing the dimensional accuracy management of the parts of the bypass passage opening / closing means for capacity switching.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the best embodiment according to the capacity variable type gas compressor of the present invention will be described with reference to the drawings.
(Embodiment 1)
FIG. 1 is a schematic longitudinal sectional view showing a vane rotary compressor 10 which is an embodiment of a variable capacity gas compressor according to the present invention, and FIG. 2 is a sectional view showing a cross section along line AA in FIG. FIG. 3 is an enlarged view of the front side block 15 and the vicinity thereof in FIG.

  The illustrated compressor 10 is configured, for example, as a part of an air conditioning system that performs cooling using the heat of vaporization of a cooling medium, and includes other components such as a condenser, an expansion valve, and an evaporator (any one) Are also provided on the circulation path of the cooling medium.

  And the compressor 10 compresses the gaseous cooling medium taken in from the evaporator of an air conditioning system, ie, refrigerant gas G, and supplies this compressed refrigerant gas G to the condenser of an air conditioning system. The condenser liquefies the compressed refrigerant gas G and sends it to the expansion valve as a high-pressure liquid refrigerant (liquid).

  The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

  In addition, the compressor 10 is attached to the housing 11 which is an exterior, the compressor main body 12 accommodated in the housing 11, and the housing 11, and transmits a driving force from a driving source (not shown) to the compressor main body 12. And a mechanism 13.

  The housing 11 has a case 11a made of a cylindrical body that is open at one end, and a front head 11b that is attached so as to cover an open portion of the case 11a, and thereby an internal space in which the compressor body 12 is accommodated. Is formed. The front head 11b is formed with a suction port (not shown) through which low-pressure refrigerant gas G is drawn from the evaporator, and the case 11a receives high-pressure refrigerant gas G compressed by the compressor body 12. A discharge port 31a for discharging to the condenser is formed. The transmission mechanism 13 is rotatably supported by the front head 11b via a radial ball bearing.

  The compressor main body 12 accommodated in the housing 11 includes a rotary shaft 19 that is driven to rotate about an axis by the transmission mechanism 13, a rotor 18 that rotates integrally with the rotary shaft 19, and an outer peripheral surface of the rotor 18. The cylinder 14 has a substantially elliptical inner peripheral surface 14a (see FIG. 2) and is open at both ends, and is embedded so as to protrude freely from the outer peripheral surface of the rotor 18. Five plate-like vanes 21 provided on the rotor 18 at equal angular intervals around the rotary shaft 19 that are in contact with the peripheral surface 14a, and open end surfaces 14b and 14c from the outside of both open end surfaces 14b and 14c of the cylinder 14, respectively. The front side block 15 and the rear side block 16 are fixed so as to cover them.

  Each of the two side blocks 15 and 16, the rotor 18, the cylinder 14, and the two vanes 21 and 21 defined by the two vanes 21 and 21 that follow each other along the rotation direction of the rotor 18 (counterclockwise direction in FIG. 2). The volume of the compression chamber 22 is repeatedly increased and decreased according to the rotation of the rotary shaft 19, whereby the refrigerant gas G sucked into each compression chamber 22 is compressed and discharged.

  One of the portions of the rotating shaft 19 protruding from the both end faces 18a and 18b of the rotor 18 is pivotally supported by the bearing portion 15b of the front side block 15 and penetrates the front head 11b. The penetrating portion is pivotally supported by the front head 11 b, and the portion extending outward is connected to the transmission mechanism 13. Similarly, the other side of the protruding portion of the rotating shaft 19 is pivotally supported by the bearing portion 16 b of the rear side block 16.

  The compressor body 12 is supported by supporting the rotary shaft 19 by the front head 11b and holding the outer peripheral portions of the side blocks 15 and 16 on the inner peripheral surfaces of the case 11a and the front head 11b by O-rings or the like. It is held at a predetermined position in the housing 11.

  Further, in a state where the compressor main body 12 is accommodated inside the case 11a, the discharge chamber 31 is formed by the rear side block 16 and the case 11a, while the suction chamber 24 is formed by the front side block 15 and the front head 11b. The discharge chamber 31 communicates with the discharge port 31a, and the suction chamber 24 communicates with a suction port (not shown) (located behind the electromagnetic valve 40 in FIG. 1).

  The suction chamber 24 and the discharge chamber 31 are hermetically isolated by the O-ring or the like described above. Further, a cyclone block 30 to be described later is attached to the rear side block 16, and the cyclone block 30 is exposed in the discharge chamber 31.

  Further, at the lower part of the discharge chamber 31, the sliding portion of the compressor 10 is lubricated, cooled and cleaned, and a back pressure is applied to the vane 21 so that the vane 21 protrudes in the direction of the inner peripheral surface 14 a of the cylinder 14. Refrigerating machine oil R to be stored is stored.

  That is, the rotor 18 is formed with five slit-like vane grooves 20 radially and at equiangular intervals around the rotation center of the rotor 18, and the vanes 21 are inserted into the vane grooves 20. The vane 21 is directed in the direction of the inner peripheral surface 14a of the cylinder 14 by the centrifugal force generated by the rotation of the rotor 18 and the oil pressure of the refrigerating machine oil R applied to the back pressure chamber 18c defined by the vane groove 20 and the bottom surface of the vane 21. And follow the contour shape of the inner peripheral surface 14a so that the protruding tip of the vane 21 is kept in contact with the inner peripheral surface 14a of the cylinder 14.

  Thereby, each compression chamber 22 repeats a change in volume as the rotor 18 rotates.

  Further, as shown in FIG. 2, the front side block 15 has a front side suction port 25 that allows the suction chamber 24 and the compression chamber 22 to communicate with each other, and the refrigerant gas introduced into the suction chamber 24 from the suction port. G is sucked into the compression chamber 22 through the front suction port 25.

  On the other hand, a recess is formed in a part of the outer periphery of the cylinder 14, and this recess forms a discharge chamber 26 surrounded by the inner end surfaces 15a, 16a of both side blocks 15, 16 and the inner peripheral surface of the case 11a. is doing.

  A discharge port 27 that allows the compression chamber 22 and the discharge chamber 26 to communicate with each other is formed in the thinned portion of the cylinder 14 where the discharge chamber 26 is formed, and the discharge port 27 is formed on the discharge chamber 26 side. A reed valve 28 (valve body 28a and valve support 28b) to be opened is provided.

  The high-pressure refrigerant gas G discharged from the compression chamber 22 through the discharge port 27 and the reed valve 28 to the discharge chamber 26 is connected to a communication hole (not shown) formed in the rear side block 16 and the rear side block 16. The oil is discharged into the discharge chamber 31 through the oil separator 30a of the fixed cyclone block 30.

  On the other hand, the refrigerating machine oil R separated from the refrigerant gas G by the oil separator 30a is dropped on the bottom of the discharge chamber 31, and is stored in the bottom as described above.

  Further, the compressor 10 includes lubrication between the rotary shaft 19 and the bearing portions 15b and 16b, lubrication between the end surfaces 18a and 18b of the rotor 18 and the inner end surfaces 15a and 16a of the side blocks 15 and 16, In order to supply vane urging hydraulic pressure to the back pressure chamber 18c, a structure for guiding the refrigerating machine oil R stored in the lower portion of the discharge chamber 31 to each part is provided.

  That is, a horizontal oil passage 51 and a vertical oil passage 32c communicating with the oil passage 51 and the bearing portion 16b are formed in a portion of the rear side block 16 that is immersed in the refrigerating machine oil R accumulated at the bottom of the discharge chamber 31. Further, the inner end surface 16a of the rear side block 16 communicates with the back pressure chamber 18c of the rotor 18 through an opening in the bearing portion 16b of the oil passage 32c through a minute gap between the bearing portion 16b and the rotary shaft 19. The refrigerating machine oil R stored in the bottom portion passes through the oil passages 51 and 32c and the bearing portion 16b by the pressure of the refrigerant gas G in the discharge chamber 31, and the salai groove is formed. 16c.

  The front side block 15 is also provided with a salai groove 15 c similar to the saray groove 16 c of the rear side block 16, and further, a through hole 32 connected to the oil passage 51 is formed at the bottom of the cylinder 14. Is formed with an oil passage 32b that communicates the opening on the front side block 15 side of the through hole 32 with the bearing portion 15b, and the refrigerating machine oil R stored at the bottom of the discharge chamber 31 is also supplied to the bearing portion 15b. .

  The refrigerating machine oil R passes through a minute gap between the bearing portion 15b and the rotary shaft 19, and is guided to the salai groove 15c formed on the inner end surface 15a of the front side block 15.

  A filter 57 for preventing dust mixed in the refrigeration oil R from being supplied to the oil passage 51 together with the refrigeration oil R is provided at the inlet portion of the oil passage 51. The filter 57 is not necessary from the viewpoint of the above-described lubrication function by the refrigerating machine oil R and the back pressure supply function of the vane 21, but is necessary from the viewpoint of appropriately ensuring the operation of the bypass check valve 49 described later. This prevents the bypass check valve 49 from malfunctioning caused by dust biting into the check valve 49.

  Further, since the compressor 10 is a variable capacity compressor that makes the discharge amount of the refrigerant gas G to the outside variable, as shown in the partially enlarged view of FIG. The compression chamber 22 corresponding to the compression stroke communicates with the compression chamber 22 of the compression stroke and a suction chamber 24 that is a space (low pressure space) that is relatively lower in pressure than the internal pressure of the compression chamber 22. Bypass passages 41, 42, 43, 44, 45 for allowing the refrigerant gas G inside the compression chamber 22 to flow into the suction chamber 24 are formed, and between the bypass passages 41, 42 between the bypass passages 41, 42. By switching between a state that allows passage and a state that prevents passage, a leaf spring member (bypass bar) as bypass passage opening / closing means that varies the discharge amount of the refrigerant gas G in accordance with the switching state. Bed) 46 is disposed.

  Here, the bypass passages 41, 42, 43, 44 are formed in the front side block 15, and one end of the bypass passage 41 is opened facing the compression chamber 22 corresponding to the compression stroke.

  The bypass passage 44 is formed on the outer peripheral surface of the front side block 15, and is formed over a substantially half circumference of the outer peripheral surface so as to connect the upper bypass passage 43 and the lower bypass passage 43 shown in FIG. Has been.

  One end of the bypass passage 45 is opened through the electromagnetic valve 40 so as to face the suction chamber 24 which is a low pressure space.

  Specifically, the leaf spring member 46 has one plate surface 46a formed in the bypass passage 41 as shown in FIG. 4B, which is a cross section taken along line CC in FIG. They are in close contact with each other and are urged to prevent passage of the refrigerant gas G between the bypass passages 41 and 42.

  The leaf spring member 46 has a pressure acting on one plate surface 46a (pressure of the refrigerant gas G in the compression chamber 22) and a pressure acting on the other plate surface 46b (the back surface of the one surface 46a). Depending on the difference from (the internal pressure in the bypass passage 42), as shown in FIG. 4C, one plate surface 46a is elastically deformed so as to be separated from the bypass passage 41, and the flow of the bypass passages 41 to 46 is increased. Switch to an acceptable state.

  Here, the pressure in the bypass passage 42 is supplied to the oil passage 51 formed in the rear side block 16 through the filter 57 and the supply passage 14 d formed in the thick portion of the cylinder 14 as a passage different from the oil passage 32. This is due to the refrigerating machine oil R supplied through.

  The pressure (high pressure) of the refrigerating machine oil R supplied to the bypass passage 42 via the supply passage 14d, the bypass check valve 49, the bypass passage 43, and the bypass passages 44, 43 is the other plate surface 46b of the leaf spring member 46. It is acting on.

  The pressure acting on the refrigerating machine oil R in the discharge chamber R is very high because it depends on the pressure of the refrigerant gas G discharged from the compression chamber 22 at a very high pressure. The pressure acting on the other plate surface 46b is very high.

  On the other hand, the pressure acting on one plate surface 46a of the leaf spring member 46 is the pressure in the compression chamber 22, but this compression chamber 22 only corresponds to the initial stage of compression of the compression stroke, so The pressure in the chamber 22 is relatively small. Therefore, the pressing force acting on one plate surface 46a is smaller than the pressing force acting on the other surface 46b, and the leaf spring member 46 is in a state of closing the bypass passage 41. (The state shown in FIG. 4B).

  The leaf spring member 46 is fastened together with the front side block 15 by a screw member 48 together with a valve support 47 that prevents the leaf spring member 46 from being greatly deformed.

  An electromagnetic valve 40 is provided between the bypass passage 45 and the suction chamber 24. The electromagnetic valve 40 is also one of bypass passage opening / closing means, and switches between permitting flow and blocking the flow between the bypass passage 45 and the suction chamber 24.

  That is, when the flow between the bypass passage 45 and the suction chamber 24 is blocked, the bypass passages 42, 43, 44, 45 are maintained at a high pressure by the high-pressure refrigeration oil R, and the leaf spring member 46 is bypassed. The passage 41 is closed, and the refrigerant gas G having the maximum capacity is discharged from the compression chamber 22 into the discharge chamber 26.

  On the other hand, when the electromagnetic valve 40 permits the flow between the bypass passage 45 and the suction chamber 24, the high-pressure refrigeration oil R supplied to the bypass passage 42 passes through the bypass passages 43, 44, 45. Then, it flows out to the suction chamber 24 which is a low pressure. Therefore, as shown in FIG. 4C, the pressure acting on one plate surface 46a of the leaf spring member 46 exceeds the pressure acting on the other plate surface 46b, and the leaf spring member 46 is bypassed by the bypass passages 41, 42. The refrigerant gas G at the initial stage of the compression stroke flows from the compression chamber 22 into the bypass passage 42, passes through the bypass passages 43, 44, 45, and the electromagnetic valve 40, and is sucked into the suction chamber 24. To leak.

  Therefore, in the compression chamber 22, the vane 21 on the rear side in the rotation direction among the two vanes 21 and 21 defining the compression chamber 22 reaches a rotation angle position passing through the bypass passage 41 opened in the compression chamber 22. The compression action is not substantially started, and therefore, the discharge amount of the compressed refrigerant gas G to the discharge chamber 26 is reduced as compared with the maximum capacity discharge mode in which the compression action is already started at this time. Will be.

  Here, when the discharge amount of the refrigerant gas G is smaller than the maximum discharge amount, the bypass passages 41 to 45 are in communication with the suction chamber 24, and the bypass passages 43, 44, 45 Not only the refrigerant gas G flowing out of the compression chamber 22 via the bypass passages 41 and 42 but also the refrigerating machine oil R supplied from the supply passage 14d may continue to flow out into the suction chamber 24.

  Therefore, a bypass for preventing the refrigerating machine oil R from flowing infinitely into the bypass passage 43 between the supply passage 14d and the bypass passage 43 even during the period in which the discharge amount of the refrigerant gas G is reduced. A check 49 is provided.

  That is, when the bypass passages 41 to 45 are not in communication with the suction chamber 24, the valve body 49a of the bypass check valve 49 is within the range of the bypass check valve space 49c by the biasing force of the string spring 49b as shown in FIG. Among them, it is displaced to the left end in the figure, and the refrigerating machine oil R is allowed to flow between the supply passage 14 d and the bypass passage 43.

  On the other hand, in a state where the bypass passages 41 to 45 are in communication with the suction chamber 24, the pressure in the bypass passages 43, 44, and 45 decreases, so that the valve body 49a of the bypass check valve 49 is as shown in FIG. The refrigeration oil R is prevented from flowing between the supply passage 14d and the bypass passage 43 by displacing to the right end portion of the bypass check valve space 49c against the urging force of the string spring 49b.

  Thereby, it is possible to prevent the refrigerating machine oil R from flowing infinitely from the supply passage 14d into the bypass passage 43.

  Even in the state where the flow of the refrigerating machine oil R shown in FIG. 6 is inhibited, there is a slight gap for sliding between the outer peripheral surface of the valve body 49a and the wall surface defining the bypass check valve space 49c. Therefore, in actuality, a small amount of refrigerating machine oil R flows out from the supply passage 14d into the bypass passage 43.

  The refrigeration oil R that has flowed out is discharged to the suction chamber 24 through the bypass passages 43 to 45 when the bypass passages 41 to 45 are in communication with the suction chamber 24.

  On the other hand, when the bypass passages 41 to 45 are not in communication with the suction chamber 24, that is, by switching the electromagnetic valve 40, the bypass passages 41 to 45 are not in communication with the suction chamber 24. When switched, the valve body 49a of the bypass check valve 49 remains as it is in the position where the bypass passages 41 to 45 are not yet communicated with the suction chamber 24 (the right end portion in the drawing in the range of the bypass check valve space 49c). ing.

  However, as shown in FIG. 7, the pressure in the bypass passages 43 to 45 increases little by little as the small amount of the refrigerating machine oil R continues to flow out from the supply passage 14d to the bypass passage 43 through the small gap described above. When the valve body 49a of the bypass check valve 49 is slightly displaced to the left in the drawing and the supply passage 14d and the bypass passage 43 communicate with each other, the supply passage 14d is moved to the bypass passage 42 via the bypass passages 43 and 44. The refrigerating machine oil R suddenly flows in, the leaf spring member 46 is in a state of closing the bypass passage 41 (the state of FIG. 4B), the compression chamber 22 is switched to the maximum capacity, and the refrigerant gas G is discharged. The amount is returned to the maximum. At this time, the valve body 49a of the bypass check valve 49 is returned to the left end position of the bypass check valve space 49c shown in FIG.

  According to the compressor 10 according to the present embodiment configured as described above, one plate surface 46a of the leaf spring member 46 closes the space between the bypass passages 41 and 42 and prevents passage between the bypass passages 41 to 45. When the compression chamber 22 shifts to the compression stroke, the refrigerant gas G is compressed at a predetermined maximum compression ratio in the compression chamber 22 and the outlet of the compression chamber 22 is discharged. A predetermined maximum amount of the refrigerant gas G is discharged from the discharge port 27.

  On the other hand, the leaf spring member 46 is elastically deformed against the biasing force based on the elastic force according to the difference in pressure acting on the front and back plate surfaces 46a and 46b of the leaf spring member 46, and the one plate When the surface 46a is displaced (deformed) to open between the bypass passages 41 and 42 and to allow the passage of the bypass passages 41 to 45, a part of the refrigerant gas G in the compression chamber 22 in the compression stroke is Then, the refrigerant gas G flows into the suction chamber 24 which is a low pressure space via the bypass passages 41 to 45, and the amount of the refrigerant gas G in the compression chamber 22 decreases, and the refrigerant gas G discharged from the discharge port 27 of the compression chamber 22 The amount is less than the maximum amount.

  Therefore, the discharge amount of the refrigerant gas G can be appropriately changed by appropriately controlling the pressure acting on the front and back plate surfaces 46a and 46b of the leaf spring member 46, respectively.

The switching performance of the operation by the leaf spring member 46 is less dependent on the shape dimensional accuracy than the conventional spool valve, so that the dimensional accuracy management of the parts can be made easier than before. Operational performance can be ensured while relaxing management.
(Modification 1)
In the compressor 10 according to the above-described embodiment, the leaf spring member 46 is, as shown in FIG. 4B and FIG. However, the variable capacity type gas compressor according to the present invention is not limited to this form, and as shown in FIG. 8, a leaf spring member is used. 46 may be tightened by a screw member 48 along a direction orthogonal to the approximate thickness direction of the front side block 15, that is, a direction orthogonal to the approximate length direction from the boundary with the compression chamber 22. .

  Also in this case, since the valve support 47 is fastened together with the valve 46, both the valve support 47 and the leaf spring member 46 are formed in a substantially L shape.

  And the leaf | plate spring member 46 exhibits the effect | action and effect similar to the compressor 10 which concerns on Embodiment 1 mentioned above also by the compressor of Embodiment formed in this way.

  That is, the discharge amount of the refrigerant gas G can be appropriately changed by appropriately controlling the pressures acting on the front and back plate surfaces 46a and 46b of the leaf spring member 46, respectively.

The switching performance of the operation by the leaf spring member 46 is less dependent on the shape dimensional accuracy than the conventional spool valve, so that the dimensional accuracy management of the parts can be made easier than before. Operational performance can be ensured while relaxing management.
(Modification 2)
In the compressor 10 of the first embodiment and the first modification described above, the leaf spring member 46 is disposed on the front side block 15, but the variable capacity type gas compressor according to the present invention is in this form. The leaf spring member 66 and the valve support 67 corresponding to the leaf spring member 46 and the valve support 47 in Embodiment 1 and Modification 1, respectively, are not limited to the lead in the discharge chamber 26 as shown in FIG. You may provide in the cylinder 14 as the structure similar to the valve | bulb 28a and the valve | bulb support 28b.

  The bypass passage 61 corresponding to the bypass passage 41 in the first embodiment and the modified example 1 has the same configuration as the discharge port 27 in the discharge chamber 26, and the same rotation angle position as the rotation angle position where the bypass passage 41 was opened. The bypass passage 62 corresponding to the bypass passage 42 is formed in the thick portion of the cylinder 14 with the same configuration as the discharge chamber 26, and the bypass passage 63 corresponding to the bypass passage 43 is the bypass shown in FIG. It is formed so as to communicate with a bypass passage formed in the same configuration as the passage 44.

  Also, the compressor of the embodiment in which the leaf spring member 66 is provided in the cylinder 18 in this way also exhibits the same operations and effects as the compressor 10 of the first embodiment and the first modification described above.

  That is, the discharge amount of the refrigerant gas G can be appropriately changed by appropriately controlling the pressure acting on the front and back plate surfaces of the leaf spring member 66.

  And, the switching performance of the operation by the leaf spring member 66 is less dependent on the shape dimensional accuracy than the conventional spool valve, so that the dimensional accuracy management of the parts can be made easier than before. Operational performance can be ensured while relaxing management.

  In the second modification, when the discharge chamber 26 remains open in the radial direction as shown in FIG. 2, the refrigerating machine oil R passes from the bypass passage 62 through the gap between the case 11 a and the outer periphery of the cylinder 14. Since there is a risk of wrapping around the discharge chamber 26, the radially outer portion of the discharge chamber 26 is surrounded by the cylinder 14 as shown in FIG. It is preferable that the one part is surrounded by the cylinder 14.

  Of course, it is not limited to the one in which the surrounding wall is formed by the cylinder 14, and it is also possible to adopt a configuration in which the discharge chamber 26 or the bypass passage 62 is hermetically partitioned so as not to communicate with each other by an O-ring or the like.

It is a schematic longitudinal cross-sectional view which shows the vane rotary type variable displacement compressor which is one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing showing the cross section along the AA in FIG. It is the enlarged view to which the front side block in FIG. 1 and its vicinity part were expanded. It is a figure which shows the detail of the front side block in FIG. 1, (a) is a figure at the time of seeing through a front side block by the arrow B shown in FIG. 1, (b) is CC line in (a). It is sectional drawing which shows the cross section along, and is the state which closed the bypass channel, (c) is sectional drawing which shows the cross section along CC line of (a) like (b), and opens a bypass channel Each state. It is detail drawing (the 1) explaining operation | movement with a bypass check valve and a leaf | plate spring member. It is detail drawing (the 2) explaining operation | movement with a bypass check valve and a leaf | plate spring member. It is detail drawing (the 3) explaining operation | movement with a bypass check valve and a leaf | plate spring member. It is a figure equivalent to Drawing 4 (b) showing a modification of a leaf spring member. It is a figure equivalent to FIG. 2 which shows the modification which provided the leaf | plate spring member in the cylinder.

Explanation of symbols

10 Compressor (Capacity variable type gas compressor)
DESCRIPTION OF SYMBOLS 11 Housing 12 Compressor main body 14 Cylinders 15 and 16 Side block 18 Rotor 19 Rotating shaft 22 Compression chamber 24 Suction chamber (low pressure space)
31 Discharge chamber 40 Electromagnetic valves 41 to 45 Bypass passage 46 Leaf spring member (bypass passage opening / closing means)
47 Valve support G Refrigerant gas R Refrigerating machine oil

Claims (4)

It has a compressor body that compresses the gas sucked from the low-pressure space in the internal space,
A bypass passage is formed which communicates the space portion corresponding to the compression stroke of the gas in the internal space and the low-pressure space, and the bypass is switched between a state allowing the passage of the bypass passage and a state blocking the passage. In a variable capacity type gas compressor provided with a passage opening / closing means and capable of varying the discharge amount of the compressed gas according to the state of the bypass passage opening / closing means,
The bypass passage opening / closing means has a state in which the plate surface blocks the bypass passage by the biasing force based on the elastic force according to the difference in pressure acting on each of the front and back surfaces, and the biasing force. A variable capacity gas compressor comprising a leaf spring member that is displaced or deformed between the permissible state due to elastic deformation against the above. The gas compressor is
A cylindrical rotor that rotates integrally with the rotating shaft, a cylinder that surrounds the outer periphery of the rotor, and a protrusion from the outer periphery of the rotor so that the protruding tip follows the contour shape of the cylinder A plurality of plate-shaped vanes provided at equiangular intervals around the rotation axis, the amount of which is variable, and the rotor and the cylinder are disposed so as to sandwich the rotor and the cylinder from the both end surface sides, respectively. A compression chamber defined by the two side blocks, the rotor, the cylinder, and the two vanes that follow each other in the rotation direction of the rotor, according to the rotation of the rotating shaft. It is a vane rotary type compressor body that repeatedly increases and decreases in volume,
The bypass passage is formed such that one end is an opening facing the space corresponding to the compression stroke and the other end is an opening facing the low-pressure space, and the bypass passage opening / closing means includes the side block. The variable capacity gas compressor according to claim 1, wherein the capacity variable type gas compressor is disposed in the air compressor. The gas compressor is
A cylindrical rotor that rotates integrally with the rotating shaft, a cylinder that surrounds the outer periphery of the rotor, and a protrusion from the outer periphery of the rotor so that the protruding tip follows the contour shape of the cylinder A plurality of plate-shaped vanes provided at equiangular intervals around the rotation axis, the amount of which is variable, and the rotor and the cylinder are disposed so as to sandwich the rotor and the cylinder from the both end surface sides, respectively. A compression chamber defined by the two side blocks, the rotor, the cylinder, and the two vanes that follow each other in the rotation direction of the rotor, according to the rotation of the rotating shaft. It is a vane rotary type compressor body that repeatedly increases and decreases in volume,
The bypass passage is formed such that one end is an opening facing the space corresponding to the compression stroke and the other end is an opening facing the low pressure space, and the bypass passage opening / closing means is connected to the cylinder. The variable capacity gas compressor according to claim 1, wherein the variable capacity gas compressor is provided.   4. The capacity according to claim 1, wherein, of the front and back plate surfaces of the leaf spring member, the one plate surface faces a space corresponding to the compression stroke. 5. Variable gas compressor.

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