JP2013245638A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor configured to prevent a valve element of a pressure regulation valve element part from being closed on early stage during an initial term of activation.SOLUTION: A pressure regulation valve element part 90 is provided between a discharge chamber 21 and a vane back pressure space 69. In the case where a pressure between both is substantially uniform, a valve element 93 of the pressure regulation valve element part 90 is located in a position where a coolant passage groove 93a communicates with a coolant introduction passage 92, and a valve open state is provided where a liquid coolant (fluid) is introduced from the discharge chamber 21 through the coolant introduction passage 92 into the vane back pressure space 69. In the case where a pressure at the discharge chamber 21 side increases and a differential pressure between the discharge chamber 21 and the vane back pressure space 69 becomes greater, the valve element 93 is located in a position where its outer peripheral surface closes the coolant introduction passage 92, and a valve closed state is provided where introduction of the liquid coolant from the discharge chamber 21 through the coolant introduction passage 92 to the vane back pressure space 69 is stopped.

Description

  The present invention relates to a gas compressor, and more particularly to an improvement of a vane rotary type gas compressor.

  For example, vehicles such as automobiles are provided with an air conditioner for adjusting the temperature in the passenger compartment. Such an air conditioner has a loop-shaped refrigerant cycle in which refrigerant (cooling medium) is circulated, and this refrigerant cycle is provided with an evaporator, a compressor, a condenser, and an expansion valve in this order. Yes.

  The compressor (compressor) of the air conditioner compresses the gaseous refrigerant (refrigerant gas) evaporated by the evaporator into a high-pressure refrigerant gas and sends it to the condenser.

  As such a compressor, a rotor having a plurality of vanes provided so as to protrude and be housed in a cylinder having a substantially elliptical inner peripheral surface, the tip of which is slidably in contact with the inner peripheral surface of the cylinder has been rotated. A vane rotary type gas compressor that is freely supported is known.

  This vane rotary type gas compressor has a compression chamber whose volume changes due to sliding contact with the inner peripheral surface of the rotating vane as the rotor rotates, and the suction port is provided as the volume of the compression chamber increases. The refrigerant gas is sucked in through the compression chamber, the sucked refrigerant gas is compressed as the volume of the compression chamber decreases, and the high-pressure refrigerant gas is discharged into the discharge chamber through the discharge port. Then, high-pressure refrigerant gas is sent from the discharge chamber to the condenser side.

  By the way, the vane is slidably disposed in a slit-like vane groove exposed on the surface from the inside of the rotor. And this vane protrudes from the rotor surface by the back pressure (vane back pressure) by the oil supplied to the bottom of the vane groove through the vane back pressure space and the centrifugal force of the rotating rotor, and the tip of the vane Is maintained in contact with the inner peripheral surface of the cylinder.

  Part of the oil that causes the back pressure to act on the vane leaks from the vane groove into the compression chamber, mixes with the refrigerant gas, and is discharged into the discharge chamber through the discharge port. Therefore, the oil separator removes oil from the refrigerant gas. Separated and recovered, the recovered oil is stored at the bottom of the discharge chamber. Oil (including recovered oil) stored in the bottom of the discharge chamber is supplied to the bottom of the vane groove through a passage or the like by the pressure in the discharge chamber (pressure by high-pressure refrigerant gas), and back pressure (vane) is applied to the vane. Apply back pressure.

  By the way, in this vane rotary type gas compressor, when the stop state (non-operating state) continues for a long time, the internal pressure of the discharge chamber decreases, so that the vane back pressure decreases. The vane groove falls into a state where no compression chamber is formed.

  When the gas compressor is started under such circumstances, the vane has a necessary vane back pressure at the initial stage because the tip of the vane protrudes from the rotor surface only by the centrifugal force of the rotating rotor and a slight vane back pressure. Therefore, there is a problem that it takes time to obtain a desired high-pressure refrigerant gas from the compression chamber.

  Therefore, immediately after the start of the gas compressor, a pressure regulating valve body portion is provided for directly introducing a fluid having a relatively high pressure in the discharge chamber into the vane back pressure space communicating with the vane groove through a passage or the like. Thus, a technique for rapidly increasing the vane back pressure has been proposed (see, for example, Patent Document 1).

  The pressure regulating valve body portion has a passage through the vane back pressure space (intermediate pressure communication space in Patent Document 1) and the discharge chamber, and a pressure difference between the pressure in the vane back pressure space and the pressure in the discharge chamber. When the pressure difference between the two is small, such as immediately after starting the gas compressor, the valve body is opened by the biasing force of the spring. As a result, a relatively high-pressure fluid in the discharge chamber is introduced into the vane back pressure space through the passage to increase the vane back pressure, and the tip side of the vane is rapidly protruded from the rotor surface.

  Then, when a predetermined time (time until a predetermined vane back pressure is obtained) elapses after the gas compressor is started, a pressure difference between the pressure in the vane back pressure space and the pressure in the discharge chamber increases (discharge chamber). Further, the valve element closes against the biasing force of the spring by the dynamic pressure of the fluid in the discharge chamber. As a result, the fluid in the discharge chamber is not introduced into the vane back pressure space through the passage, so that the vane back pressure is prevented from being excessively increased, and the vane tip and the cylinder inner peripheral surface abut against each other excessively strongly. Is suppressed.

JP 2008-223526 A

  By the way, when this gas compressor is started after the gas compressor has been in a stopped state (non-operating state) for a long time, liquid refrigerant (fluid) in a state where the refrigerant gas is liquefied is accumulated in the discharge chamber at the initial start-up time. Yes. For this reason, as described above, since the valve body of the pressure regulating valve body portion is open at the initial stage of the start of the gas compressor, the vane back pressure space passes through the passage from the valve body in which the liquid refrigerant in the discharge chamber is open. Will be introduced.

  However, since the liquid refrigerant has a larger viscous resistance acting on the valve body than the refrigerant gas in a gaseous state, a larger dynamic pressure acts on the valve body and the force for closing the valve body is increased, which is earlier than usual. In some cases, the valve body may be closed.

  Thus, if the valve body closes earlier than usual at the initial stage of startup, the predetermined vane back pressure has not yet been obtained, so that the behavior of the vane becomes unstable and vane chattering may occur.

  Therefore, an object of the present invention is to provide a gas compressor capable of preventing the valve body of the pressure regulating valve body portion from closing earlier than usual at the initial stage of startup.

  In order to achieve the above object, a gas compressor according to the present invention includes a cylinder having a substantially elliptical inner wall surface, a rotor rotatably disposed in the cylinder, and a vane groove formed in the rotor. A plurality of vanes whose front end side is held so as to protrude freely from the rotor surface, and a vane back pressure that causes the vane to protrude from the rotor surface with respect to the bottom of the vane groove, with the tips in the protruding state coming into contact with the inner wall surface of the cylinder. A vane back pressure space for acting, and by rotating the rotor, the tip of the vane protruding from the rotor surface slides on the inner wall surface of the cylinder, whereby the inner wall surface of the cylinder and the rotor A gas that compresses the fluid introduced into the compression chamber to a high pressure and discharges the compressed high-pressure fluid into the discharge chamber by changing the volume of the compression chamber formed between In the compressor, a pressure regulating valve body portion is provided between the discharge chamber and the vane back pressure space, and the pressure regulating valve body portion communicates between the discharge chamber and the vane back pressure space. And a valve body in which an outer peripheral surface is slidably disposed with respect to an inner peripheral surface on the discharge chamber side of the communication passage, and a fluid passage groove is formed in a direction substantially orthogonal to the communication passage in an intermediate portion; A fluid introduction passage formed to be able to communicate between the discharge chamber and the vane back pressure space through a fluid passage groove of the valve element disposed in the communication passage and a flow path different from the communication passage. And when the pressure between the discharge chamber and the vane back pressure space is substantially equal, the valve body is in a position where the fluid passage groove communicates with the fluid introduction passage, and the discharge chamber From which the fluid is introduced into the vane back pressure space through the fluid introduction passage. When the pressure on the discharge chamber side increases and the differential force between the discharge chamber and the vane back pressure space increases, the valve body is in a position where its outer peripheral surface closes the fluid introduction passage. Thus, the valve is closed to stop the introduction of fluid from the discharge chamber to the vane back pressure space through the fluid introduction passage.

  According to the gas compressor according to the present invention, it is possible to prevent the valve body of the pressure regulating valve body portion from closing earlier than usual at the initial start time of the gas compressor. However, a stable vane back pressure can be obtained and the occurrence of vane chattering can be prevented.

1 is a longitudinal sectional view showing a gas compressor (vane rotary type gas compressor) according to an embodiment of the present invention. AA sectional view taken on the line AA of FIG. Schematic which showed the oil separator and pressure regulation valve body part in the discharge chamber by arrow B in FIG. Sectional drawing which showed the structure of the pressure regulation valve body part. (A) is a perspective view which shows the valve body of a pressure regulation valve body part, (b) is a side view of a valve body. (A) is a figure which shows the time of valve opening of the pressure regulation valve body part, (b) is a figure which shows the time of valve closing of the valve body of a pressure regulation valve body part.

  Hereinafter, the present invention will be described based on the illustrated embodiments. FIG. 1 is a longitudinal sectional view showing a vane rotary type gas compressor (hereinafter referred to as “compressor 100”) as an embodiment of the gas compressor according to the present invention, and FIG. 2 is a line AA in FIG. It is a figure which shows the cross section along line.

(Overall configuration and operation of compressor 100)
The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter referred to as an “air conditioning system”) that performs cooling by using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. It is provided on the circulation path of the cooling medium together with a condenser, an expansion valve, an evaporator, etc. (all not shown). In addition, as such an air conditioning system, the air conditioning apparatus for adjusting the temperature in the vehicle interior of a vehicle (automobile etc.) is mentioned, for example.

  The compressor 100 compresses the refrigerant gas as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas to the condenser of the air conditioning system. The condenser liquefies the compressed refrigerant gas and sends it to the expansion valve as a high-pressure liquid refrigerant. The high-pressure and 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.

  As shown in FIG. 1, the compressor 100 is attached to the compressor main body 70, the oil separator 60, and the front head 12 housed in the housing 10 including the case 11 and the front head 12. A driving force transmission mechanism 80 that transmits a driving force from a source (for example, a vehicle engine) to the compressor body 70 side is provided.

  The case 11 has a cylindrical body with one end closed, and the front head 12 is assembled so as to cover the end of the case 11 on the opened side. The front head 12 is formed with a suction port (not shown) through which low-pressure refrigerant gas is sucked from the evaporator, while the case 11 condenses the high-pressure refrigerant gas compressed by the compressor body 70. A discharge port (not shown) for discharging to the container side is formed.

  Inside the housing 10, a suction chamber 31 that is a space communicating with the suction port and a discharge chamber 21 that is a space communicating with the discharge port are defined by an inner surface of the housing 10 and an outer surface of the compressor body 70. Yes. An oil separator 60 described later is provided in the discharge chamber 21.

  The compressor body 70 includes a rotating shaft 51, a rotor 50, a cylinder 40, five vanes 58 (see FIG. 2), a front side block 30, and a rear side block 20.

  The rotating shaft 51 is rotationally driven around the axis by the driving force transmitted by the driving force transmitting mechanism 80. The rotor 50 has a cylindrical shape coaxial with the rotation shaft 51 and rotates integrally with the rotation shaft 51. The cylinder 40 has an inner peripheral surface 49 (see FIG. 2) having a substantially elliptical cross-sectional outline surrounding the outer periphery of the rotor 50, and has a shape in which both ends are open.

  As shown in FIG. 2, the vane 58 is embedded in a vane groove 59 extending to both end faces of the rotor 50, and the vane is formed by refrigerating machine oil supplied through portions of the vane groove 59 that are open at both end faces of the rotor 50. Under the back pressure, the rotor 50 can protrude outward (toward the inner peripheral surface 49 of the cylinder 40) from the outer peripheral surface of the rotor 50, and the tip of the protruding side is the contour shape of the inner peripheral surface 49 of the cylinder 40. The amount of protrusion is variable so as to follow, and five are arranged around the rotation shaft 51 at predetermined intervals.

  The front side block 30 is fixed so as to cover the end surface on the suction chamber 31 side among the both end surfaces of the cylinder 40, and the rear side block 20 is fixed so as to cover the end surface on the discharge chamber 21 side among the both end surfaces of the cylinder 40. ing. A through hole serving as a bearing that rotatably supports portions of the rotating shaft 51 protruding from both end faces of the rotor 50 is formed in the substantially central portion of the two side blocks 20 and 30.

  The compression chambers 48 a and 48 b formed in the space between the inner peripheral surface 49 of the cylinder 40 and the outer peripheral surface of the rotor 50 are partitioned in the circumferential direction of the rotor 50 by the vanes 58 disposed in the rotor 50. Divided into multiple pieces. Each of the compression chambers 48 a and 48 b repeatedly increases and decreases in volume in the refrigerant gas suction process and the compression process as the rotor 50 rotates. Note that the compressor 100 of the present embodiment has two suction steps and compression steps while the rotor 50 makes one rotation.

  The cylinder 40 has suction ports (not shown) for sucking refrigerant gas into the compression chambers 48a and 48b, and discharge ports 40a and 40a for discharging the refrigerant gas compressed in the compression chambers 48a and 48b. 40b is provided.

  Specifically, in the process of increasing the volume of the compression chambers 48a and 48b, the refrigerant gas in the suction chamber 31 is sucked into the compression chambers 48a and 48b through the respective suction ports (not shown) formed in the front side block 30. In the process of decreasing the volume, the refrigerant gas confined in the compression chambers 48a and 48b is compressed, whereby the refrigerant gas becomes high temperature and high pressure. The high-temperature and high-pressure refrigerant gas is discharged through the discharge ports 40a and 40b into a discharge chamber 43 that is a space surrounded by the cylinder 40, the case 11, and the two side blocks 20 and 30.

  In FIG. 2, arrow a1 indicates the refrigerant gas sucked from the suction port (not shown) into the compression chamber 48a, arrow b1 indicates the refrigerant gas discharged from the compression chamber 48a to the discharge port 40a, and arrow a2 indicates The refrigerant gas drawn into the compression chamber 48b from the suction port (not shown), and the arrow b2 shows the refrigerant gas discharged from the compression chamber 48b to the discharge port 40b.

  Each discharge port 40a, 40b is provided with a discharge valve 41 for preventing the reverse flow of the discharged refrigerant gas toward the compression chambers 48a, 48b, and a valve support 42 for preventing excessive deformation of the discharge valve.

  The high-temperature and high-pressure refrigerant gas discharged into the discharge chamber 43 is discharged through a chamber hole 44 formed in a portion of the rear side block 20 that defines the discharge chamber 43.

  The discharged refrigerant gas is introduced into an oil separator 60 provided in the discharge chamber 21. The oil separator 60 is installed integrally with the rear side block 20, and a space C having a predetermined width is provided between the main body portion 64 having a substantially cylindrical outer surface whose lower end portion is closed and the inner wall surface thereof. In this way, a substantially cylindrical tubular body 65 disposed substantially coaxially is provided. The upper side surface of the cylindrical body 65 whose both end surfaces are open is fixed to the upper inner peripheral surface of the main body portion 64. The length of the cylindrical body 65 is substantially half of the main body portion 64.

  As shown in FIG. 3, a refrigerant gas introduction path 66 communicating with each chamber hole 44 (see FIG. 2) is formed on the upper back side of the oil separator 60. Further, the discharge chamber 21 is provided with a pressure regulating valve body 90 for assisting the quick protrusion of the vane 58 when the compressor 100 is started up (details of the pressure regulating valve body 90 will be described later). . 3 is a view showing the inside of the discharge chamber 21 as viewed from the direction of arrow B in FIG. In FIG. 3, the pressure regulating valve body 90 is shown in cross section to show the internal structure.

  The refrigerant gas introduction path 66 communicates with the space C between the main body portion 64 and the cylinder 65 of the oil separator 60, and the refrigerant gas introduced into the refrigerant gas introduction path 66 through each chamber hole 44 is slightly in the space C. It is provided so as to be ejected obliquely downward (see FIG. 1).

  Therefore, when the high-temperature and high-pressure refrigerant gas discharged from each chamber hole 44 of the rear side block 20 is jetted into the space C of the oil separator 60 through the refrigerant gas introduction path 66, the inside of the space C spirally spirals. While moving down.

  By the way, the refrigerant gas discharged from the compression chambers 48a and 48b contains a part of the refrigerating machine oil leaked from the vane groove 59 to the compression chambers 48a and 48b, but the refrigerant gas swirls in the space C. When this occurs, a strong centrifugal force acts on the refrigerant gas including the mixed refrigeration oil. For this reason, the refrigerating machine oil R mixed in the refrigerant gas is separated from the refrigerant gas by the centrifugal force and dripped along the inner wall surface of the main body 64 (see FIG. 1). On the other hand, the high-pressure refrigerant gas from which the refrigerating machine oil has been separated enters the internal space from the lower opening portion of the cylinder 65, is jetted from the upper opening portion of the cylinder 65 to the upper portion of the discharge chamber 21, and is piped from a discharge port (not shown). And discharged to the condenser side.

  Further, the high-pressure refrigerating machine oil R (see FIG. 1) dripped along the inner wall surface of the main body 64 is discharged from a discharge hole 64 a provided in the bottom of the main body 64 and collected (stored) in the bottom of the discharge chamber 21. Is done.

  The high-pressure refrigerating machine oil R stored at the bottom of the discharge chamber 21 lubricates and cools the sliding portion and the like of the compressor 100, and causes the vane 58 to protrude toward the inner peripheral surface 49 of the cylinder 40, with the tip thereof It is used to apply a back pressure to the vane 58 so as to be biased to a state where it is brought into contact with the inner peripheral surface 49.

  A round hole (not shown) is formed on the rear side block 20 side of the oil separator 60 to be fitted with a boss formed around a through hole as a bearing of the rotating shaft 51 in the rear side block 20. When the oil separator 60 is installed on the rear side block 20, a vane back pressure space 69 (see FIGS. 1 and 3) described later is formed between the round hole and the end face of the boss of the rear side block 20. Has been.

  The rear side block 20 of the compressor body 70 is formed with an oil guide path 23 that guides the refrigerating machine oil R stored at the bottom of the discharge chamber 21 to the bearing of the rotation shaft 51 at the center.

  Part of the refrigerating machine oil guided to the bearing through the oil guide passage 23 passes through a sliding surface between the bearing and the outer peripheral surface of the rotary shaft 51, and is a groove for oil sump formed on the end surface of the rear side block 20. It is supplied to certain two saray grooves 25 (see FIGS. 1 and 2).

  Further, another part of the refrigerating machine oil guided to the bearing is guided to the vane back pressure space 69 formed on the oil separator 60 side through the sliding surface between the bearing and the outer peripheral surface of the rotating shaft 51. The vane back pressure space 69 is supplied to the saray groove 25 through the communication passage 24.

  The refrigerating machine oil supplied to the salai grooves 25 receives a pressure loss while passing through the sliding surface between the outer peripheral surface of the rotating shaft 51 and the bearing, so that it is more than the pressure in the discharge chamber 21. A little lower.

  The cylinder 40 and the front side block 30 are also formed with oil guide passages 23 a and 23 b communicating with the oil guide passage 23 in the rear side block 20.

  The oil guide passage 23 b extends to the bearing at the center of the front side block 30, and the refrigerating machine oil guided to the bearing of the front side block 30 through the oil guide passages 23, 23 a and 23 b is connected to the outer peripheral surface of the bearing and the rotary shaft 51. Is supplied to two Sarai grooves 35 formed on the end surface of the front side block 30 through the sliding surface between the two.

  Here, the vane grooves 59 also rotate with the rotation of the rotor 50, and the portions of the vane grooves 59 that open at both end faces of the rotor 50 are the salai grooves 25 of the rear side block 20 and the front side block 30. Refrigerating machine oil is supplied to the vane grooves 59 from the Sarai grooves 25 and 35 during the period facing the Sarai grooves 35. As a result, the high-pressure refrigerating machine oil supplied to each vane groove 59 acts as a vane back pressure that causes the vane 58 to protrude, and the tip of the vane 58 is brought into contact with the inner peripheral surface 49 of the cylinder 40.

  Thus, during normal operation in which the rotor 50 of the compressor 100 is rotationally driven, an appropriate back pressure acts on each vane 58, and as described above, the refrigerant gas suction process in each compression chamber 48a, 48b, The compression process is performed, and the refrigerant gas from which the refrigeration oil mixed in the oil separator 60 is separated is discharged to the condenser (not shown) side.

  Next, the configuration and operation of the pressure regulating valve body 90, which is a feature of the present invention, will be described.

(Configuration and operation of pressure regulating valve body 90)
As shown in FIGS. 3 and 4, the pressure regulating valve body 90 is provided in the vicinity of the refrigerant gas introduction path 66 in the discharge chamber 21, and communicates between the discharge chamber 21 and the vane back pressure space 69. Thus, the communication path 91 and the refrigerant introduction path 92 are formed inside. FIG. 4 is an enlarged cross-sectional view of the pressure regulating valve body 90.

  A large-diameter cylindrical valve body storage portion 91a is integrally formed on the upper side of the linear communication passage 91 (on the side opposite to the vane back pressure space 69) so that the tip side faces the discharge chamber 21. A cylindrical valve body 93 is slidably disposed in the valve body storage portion 91a. The depth (length) of the valve body storage portion 91 a is formed longer than the height of the valve body 93.

  The valve body 93 is urged toward the opening distal end side of the valve body storage portion 91a by a spring member 94 whose one end is held in the communication passage 91, and the valve body 93 is urged from inside the valve body storage portion 91a by this urging force. A locking member 95 is installed on the tip side of the pressure regulating valve body 90 so as not to jump out.

  The refrigerant introduction passage 92 includes a first passage 92a, a second passage 92b, and a third passage 92c. The third passage 92c communicating with the second passage 92b communicates with the vane back pressure space 69. Yes. The second passage 92b communicates with the third passage 92c at a right angle.

  Moreover, each one end side which the 1st channel | path 92a and the 2nd channel | path 92b oppose is exposed to the opposing position of the internal peripheral surface of the said valve body accommodating part 91a. The other end side (front end side) of the first passage 92a is exposed on the side surface of the pressure regulating valve body 90 on the refrigerant gas introduction path 66 side.

  As shown in FIGS. 5A and 5B, the cylindrical valve body 93 is formed with an annular refrigerant passage groove 93a by notching the entire peripheral surface of the central portion in a concave shape along the circumferential direction. The outer peripheral surface of the valve body 93 is slidably in contact with the inner peripheral surface of the valve body storage portion 91a.

  As will be described later, when the valve body 93 is located on the upper side of the valve body housing portion 91a, the valve passage state (valve) in which the first passage 92a and the second passage 92b are communicated with each other through the refrigerant passage groove 93a. When the valve body 93 is opened (see FIG. 6A), and the valve body 93 is positioned on the bottom side of the valve body storage portion 91a, the first passage 92a and the first passage 92a are formed on the upper outer peripheral surface of the valve body 93. The valve passage is closed between the two passages 92b (when the valve body 93 is closed: see FIG. 6B).

(When valve body 93 is opened)
When the compressor 100 is in a stopped state (non-operating state) for a long time, the refrigerant gas is in an uncompressed state, and therefore the pressure in the discharge chamber 21 and the vane back pressure space 69 is in a uniform state. Vane back pressure is not acting. In addition, when the compressor 100 has been in a stopped state (non-operating state) for a long time, the temperature of the refrigerant gas is reduced to the ambient environmental temperature, so that at least a part of the refrigerant gas in the discharge chamber 21 is liquid refrigerant. Has changed.

  Thus, when the pressure between the discharge chamber 21 and the vane back pressure space 69 is in a substantially equalized state, the valve body 93 is caused to be valving by the biasing force of the spring member 94 as shown in FIG. The storage portion 91 a is biased toward the opening tip side and is locked by a locking member 95. In this state, since the refrigerant passage groove 93a of the valve body 93 is located at the same position as the first passage 92a and the second passage 92b, the first passage 92a and the second passage 92b communicate with the refrigerant passage groove 93a interposed therebetween. . Therefore, the discharge chamber 21 and the vane back pressure space 69 communicate with each other through the refrigerant introduction passage 92 and the refrigerant passage groove 93 a of the valve body 93.

  When the compressor 100 is started (operated) in this state, the liquid refrigerant (arrow D in FIG. 6A) in the discharge chamber 21 at the initial start-up time becomes the refrigerant introduction passage 92 and the refrigerant passage of the valve body 93. It is introduced into the vane back pressure space 69 through the groove 93a. Since the valve body 93 is slidably in contact with the inner peripheral surface of the valve body storage portion 91 a and sealed, the liquid refrigerant in the discharge chamber 21 does not leak into the vane back pressure space 69 through the communication path 91.

  Since the pressure of the liquid refrigerant introduced into the vane back pressure space 69 through the refrigerant introduction passage 92 and the refrigerant passage groove 93a of the valve body 93 is increased at the initial stage of startup, the vane back pressure acting on the vane 58 gradually increases. I will do it. Therefore, the compression chambers 48a and 48b are formed by rapidly projecting the tip of the vane 58 by this vane back pressure and bringing it into contact with the inner peripheral surface 49 of the cylinder 40.

(When valve body 93 is closed)
Immediately after the compressor 100 is activated, the pressure of the liquid refrigerant acts on the upper surface of the valve body 93 (the surface exposed to the discharge chamber 21) (this pressure is small immediately after activation).

  Then, as the compressor 100 starts, the pressure of the liquid refrigerant in the discharge chamber 21 gradually increases, and as shown in FIG. 6B, the pressure of the liquid refrigerant (arrow F in FIG. 6B) becomes a spring. When the urging force of the member 94 becomes larger, the valve body 93 is pushed down to the bottom side of the valve body housing portion 91a against the urging force and closes the space between the first passage 92a and the second passage 92b. It becomes a state.

  As described above, when the valve body 93 is pushed down, the upper outer peripheral surface of the valve body 93 is sealed so as to close the space between the first passage 92a and the second passage 92b, thereby allowing the discharge chamber 21 to pass through the refrigerant introduction passage 92. The introduction of the liquid refrigerant into the vane back pressure space 69 is stopped.

  As shown in FIG. 6 (b), the high pressure refrigerating machine oil separated by the oil separator 60 (refrigerating machine oil recovered (stored) at the bottom of the discharge chamber 21) just before the valve body 93 is closed. ) Is introduced into the vane back pressure space 69, and a predetermined vane back pressure is generated. Then, with the generated predetermined vane back pressure, the tip end portion of the vane 58 is protruded and brought into contact with the inner peripheral surface 49 of the cylinder 40, whereby a stable normal operation state is achieved.

  Thus, when the valve element 93 is opened at the initial start of the compressor 100 that has been in a stopped state (non-operating state) for a long time, the refrigerant introduction passage 92 and the valve are formed between the discharge chamber 21 and the vane back pressure space 69. The liquid refrigerant in the discharge chamber 21 (arrow D in FIG. 6A) communicates with the refrigerant passage groove 93a of the body 93 and enters the vane back pressure space 69 through the refrigerant introduction passage 92 and the refrigerant passage groove 93a of the valve body 93. be introduced.

  Therefore, at the initial start of the compressor 100, the liquid refrigerant simply passes through the refrigerant passage groove 93a of the valve body 93, and the viscous resistance of the liquid refrigerant causes the valve body 93 to move to the bottom side of the valve body housing portion 91a (the spring member 94 side). ) Almost no action to push down. Therefore, unlike the above-described Patent Document 1, the valve element 93 is not closed earlier than usual due to the viscous resistance of the moving liquid refrigerant at the initial start of the compressor 100. As a result, a stable vane back pressure can be obtained by the liquid refrigerant even at the initial startup of the compressor 100, so that occurrence of vane chattering can be prevented.

The compressor 100 according to the embodiment has a configuration in which the suction process and the compression process are performed twice during one rotation of the rotor. However, the suction process and the compression process are performed once during the rotation of the rotor. The present invention can be similarly applied to a compressor having a process (vane rotary type gas compressor).

DESCRIPTION OF SYMBOLS 21 Discharge chamber 40 Cylinder 48a, 48b Compression chamber 50 Rotor 58 Vane 60 Oil separator 69 Vane back pressure space 70 Compressor main body 90 Pressure adjustment valve body part 91 Communication path 92 Refrigerant introduction path (fluid introduction path)
93 Valve body 93a Refrigerant passage groove (fluid introduction passage)
94 Spring member 95 Locking member 100 Compressor (gas compressor)

Claims (5)

A cylinder having a substantially elliptical inner wall surface, a rotor rotatably disposed in the cylinder, and a vane groove formed in the rotor are held so that the tip side can protrude freely from the rotor surface, and the tip in the protruding state is A plurality of vanes in contact with the inner wall surface of the cylinder, and a vane back pressure space for applying a vane back pressure that causes the vane to protrude from the rotor surface against the bottom of the vane groove,
By rotating the rotor, the volume of a compression chamber formed between the inner wall surface of the cylinder and the rotor is changed by sliding the tip of the vane protruding from the rotor surface against the inner wall surface of the cylinder. In the gas compressor that compresses the fluid introduced into the compression chamber to a high pressure and discharges the compressed high-pressure fluid to the discharge chamber.
A pressure regulating valve body is provided between the discharge chamber and the vane back pressure space,
The pressure regulating valve body portion is a communication passage communicating between the discharge chamber and the vane back pressure space;
A valve body in which an outer peripheral surface is slidably disposed with respect to an inner peripheral surface on the discharge chamber side of the communication passage, and a fluid passage groove is formed in a direction substantially orthogonal to the communication passage in an intermediate portion;
A fluid introduction passage formed to be able to communicate between the discharge chamber and the vane back pressure space through a fluid passage groove of the valve element disposed in the communication passage and a flow path different from the communication passage. Have
When the pressure between the discharge chamber and the vane back pressure space is substantially equal, the valve body is in a position where the fluid passage groove communicates with the fluid introduction passage, and the fluid from the discharge chamber A valve is opened to introduce fluid into the vane back pressure space through the introduction passage;
When the pressure on the discharge chamber side is increased and the differential force between the discharge chamber and the vane back pressure space is increased, the valve body is in a position where the outer peripheral surface closes the fluid introduction passage. The gas compressor is in a closed state in which the introduction of fluid from the discharge chamber to the vane back pressure space through the fluid introduction passage is stopped. The valve body has an outer peripheral surface that is slidable on an inner peripheral surface of the communication passage, and an annular fluid passage groove formed by notching a middle portion of the outer peripheral surface in a concave shape along the circumferential direction. And
The outer peripheral surface of the valve body is slidably in contact with the inner peripheral surface of the communication passage so that the fluid in the discharge chamber does not leak into the vane back pressure space through the communication passage. The gas compressor according to 1.   The valve body is biased toward the discharge chamber by a biasing force of a spring member, and the valve body is locked by a locking member so as not to jump out of the communication path into the discharge chamber. The gas compressor according to claim 1 or 2. When the pressure between the discharge chamber and the vane back pressure space is substantially equal, the valve body is in a state of being locked to the locking member by an urging force of the spring member,
When the pressure on the discharge chamber side increases and the differential force between the discharge chamber and the vane back pressure space increases, the valve body resists the urging force of the spring member. The gas compressor according to claim 3, wherein the gas compressor slides toward the vane back pressure space side of the communication path. An oil separator for separating oil mixed in the fluid from the high-pressure fluid discharged from the compression chamber;
5. The high-pressure refrigerating machine oil separated by the oil separator is introduced into the vane back pressure space from the discharge chamber when the valve is closed. 6. Gas compressor.