WO2017213006A1

WO2017213006A1 - Gas compressor

Info

Publication number: WO2017213006A1
Application number: PCT/JP2017/020332
Authority: WO
Inventors: 竜介山田; 英輝柳川; 圭佑中澤; 大騎竹差
Original assignee: カルソニックカンセイ株式会社
Priority date: 2016-06-08
Filing date: 2017-05-31
Publication date: 2017-12-14
Also published as: JP2017218995A

Abstract

Provided is a gas compressor that, when stopped, can immediately prevent a backflow of a refrigerant gas. The gas compressor (100) comprises: a housing (10) which separates an inner space from an outer space; a suction port (12a) which serves as a gas passage from an outer section to an inner section of the housing (10); a check valve (70) which allows the inflow of the gas through the suction port (12a) to the inner space of the housing (10) and prevents the backflow of the gas through the suction port (12a) to the outer space of the housing (10); and a compression mechanism unit (60) which suctions, compresses, and discharges the gas which has flowed in through the check valve (70). The check valve (70) comprises a valve body (71), which is movable to an open position allowing the inflow of the gas and to a closed position preventing the backflow of the gas, and a spring member (72) which pushes the valve body (71) toward the closed position. In the check valve (70), the fully open spring load (P) of the spring member when opening the suction port (12a) to the maximum open position is set to at least 0.4 (N).

Description

Gas compressor

The present invention relates to a gas compressor.

An air conditioning system (hereinafter also referred to as an air conditioning system) uses a gas compressor on the circulation path of the cooling medium. The gas compressor sucks low-pressure refrigerant gas (gas) through the suction port of the housing, and compresses the sucked refrigerant gas to high pressure by a compression mechanism portion housed inside the housing, and the resulting high-pressure refrigerant gas Is discharged outside through the discharge port.

The air conditioning system cools the refrigerant gas compressed by the gas compressor and liquefies it with a condenser, lowers the pressure with an expansion valve, sends it to the evaporator, and absorbs heat from the surrounding air to vaporize it with the evaporator. Cool the surrounding air by replacing it. In this air conditioning system, the vaporized low-pressure refrigerant gas is returned to the gas compressor and compressed again, and the air is cooled by repeating these steps. And an air-conditioning system repeats a drive and stop of a gas compressor suitably so that preset temperature may be maintained. Here, when the gas compressor is stopped, there is a possibility that the high-temperature and high-pressure refrigerant gas on the discharge port side flows back from the suction port to the evaporator side through the compression mechanism section. Then, in the air conditioning system, the evaporator and the like are warmed by the refrigerant gas that flows backward from the gas compressor, which causes an increase in the temperature of the refrigerant gas sucked into the gas compressor when it is driven again.

For this reason, some gas compressors are provided with a check valve in the suction port in order to prevent backflow of refrigerant gas to the evaporator side when stopped (see, for example, Patent Document 1). When the gas compressor is stopped, the check valve closes the suction port, and therefore the refrigerant gas can be prevented from flowing back to the evaporator through the suction port.

JP 2003-166486 A

By the way, in the air conditioning system, when the gas compressor is stopped, noise is generated immediately after that. This is because in the gas compressor, the pressure of the refrigerant gas on the suction side suddenly rises as it stops, and the high-pressure refrigerant gas flows backward from the suction port to the evaporator, thereby connecting to the evaporator in the air conditioning system It is considered that a sudden pressure fluctuation occurs and noise is generated accordingly. Here, in the gas compressor, a check valve is provided in the suction port. However, since the pressure increase on the suction side described above occurs abruptly, the refrigerant gas that causes pressure fluctuations before the check valve closes the suction port. It is thought that the reverse flow of has occurred.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a gas compressor capable of preventing the backflow of refrigerant gas as soon as it is stopped.

The gas compressor of the present invention includes a housing that partitions an internal space and an external space, a suction port that serves as a gas passage from the outside to the inside of the housing, and the gas that passes through the suction port and enters the internal space of the housing. And a check valve that prevents backflow of the gas to the external space of the housing through the suction port, and compression that sucks, compresses, and discharges the gas that has flowed in through the check valve And a check valve that is moved between an open position that allows the gas to flow in and a closed position that prevents the gas from flowing back, and the valve body is directed toward the closed position. A spring member that presses, and the check valve sets a spring load when the spring member is fully opened when the suction port is most opened to 0.4 (N) or more.

The gas compressor according to the present invention can prevent the backflow of the refrigerant gas as soon as it is stopped.

It is explanatory drawing which shows the structure of the compressor 100 of Example 1 which concerns on one Embodiment of the gas compressor which concerns on this invention with a longitudinal cross-section. It is explanatory drawing shown in the cross section obtained along the II line | wire of FIG. FIG. 3 is an explanatory diagram showing a surface of the front head 12 that faces the front side block 20. It is explanatory drawing which expands and shows the periphery of the non-return valve 70 shown in FIG. FIG. 5 is an explanatory view showing a cross section taken along line II-II in FIG. 4. It is a table | surface which shows the relationship of the audibility test result with respect to the spring load P (N) at the time of full opening, and spring load mass ratio Ra (N / kg).

Hereinafter, a vane rotary compressor 100 (hereinafter simply referred to as a compressor 100) as an example of a gas compressor according to the present invention will be described with reference to the drawings.

The compressor 100 according to the first embodiment is configured as a part of an air conditioning system (hereinafter simply referred to as an air conditioning system) for a vehicle that performs cooling using the heat of vaporization of a cooling medium, and is another component of the air conditioning system. Along with a condenser, an expansion valve, an evaporator, etc., it is provided on the circulation path of the cooling medium. The compressor 100 takes in a refrigerant gas G (gas) as a gaseous cooling medium from an evaporator of the air conditioning system, compresses the introduced refrigerant gas G, and supplies the compressed refrigerant gas G to the condenser of the air conditioning system. To do. The condenser radiates heat by exchanging heat between the compressed refrigerant gas and the surrounding air to liquefy the refrigerant gas, and sends the liquid refrigerant to the expansion valve at the high pressure. The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant is vaporized by absorbing heat from ambient air in the evaporator, and cools the air around the evaporator by heat exchange accompanying this vaporization. The vaporized low-pressure refrigerant gas G is again taken into the compressor 100 and compressed, and the above process is repeated thereafter.

As shown in FIG. 1, the compressor 100 includes a compression mechanism 60 that sucks low-pressure refrigerant gas G into the interior, compresses the refrigerant gas G to high pressure, and discharges it, and a housing 10 that houses the compression mechanism 60 therein. Prepare. The housing 10 includes a case 11 whose one end is closed, and a front head 12 which covers the open end 11b of the case 11. In the housing 10, a space for accommodating the compression mechanism portion 60 is formed inside the front head 12 so as to cover the end portion 11 b of the case 11. The compression mechanism section 60 includes a rotor 50 (rotating body), a rotating shaft 51, five vanes 58 (see FIG. 2), a cylinder 40, a front side block (FB) 20, and a rear side block (RB) 30.

The rotor 50 has a columnar shape, to which a rotating shaft 51 is attached, and is rotatable with the rotating shaft 51 around the axis C. Each vane 58 is provided so as to be able to advance and retreat in five grooves provided at equiangular intervals when viewed in the rotation direction around the axis C in the rotor 50, and can protrude from the outer peripheral surface of the rotor 50. The cylinder 40 has a cylindrical shape in which the cross-sectional contour shape of the inner peripheral surface 49 is formed in a substantially elliptical shape, and the outer peripheral surface of the rotor 50 is surrounded by the inner peripheral surface 49 from the outside (see FIG. 2). The front side block 20 and the rear side block 30 are provided so as to cover each end surface of the cylindrical cylinder 40 and each end surface of the columnar rotor 50.

In this way, the compression mechanism 60 is provided in each vane in a space partitioned by the cylinder 40 and the front side block 20 at the end corresponding to one end face and the rear side block 30 at the end corresponding to the other end face. The rotor 50 provided with 58 and a part of the rotating shaft 51 are accommodated. Thereby, in the compression mechanism part 60, two

cylinder chambers

53 and 54 having a substantially crescent-shaped cross-sectional outline are formed in a rotational symmetry with the axis C (rotating shaft 51) as the center (see FIG. 2). .

In the rotating shaft 51, a portion protruding from one end surface of the rotor 50 is rotatably supported by the bearing of the front side block 20 and is connected to the power transmission mechanism 80, and a portion protruding from the other end surface of the rotor 50 is The bearings of the rear side block 30 are rotatably supported. The power transmission mechanism 80 receives the driving force of the engine of the vehicle, for example, and rotates the rotating shaft 51 to rotate the rotor 50 provided with the vanes 58. Then, as shown in FIG. 2, each vane 58 protrudes from the outer peripheral surface of the rotor 50 and is pressed against the inner peripheral surface 49 of the cylinder 40. Thereby, each

cylinder chamber

53, 54 is partitioned into a plurality of compression chambers 48 by each vane 58 provided at equiangular intervals in the rotor 50. In the first embodiment, five (one of them) are defined by five vanes 58. One is partitioned into compression chambers 48 that straddle both

cylinder chambers

53, 54. Each compression chamber 48 performs a series of cycles of a suction stroke, a compression stroke, and a discharge stroke by increasing or decreasing the volume during one rotation of the rotor 50 (rotating shaft 51) in each

cylinder chamber

53, 54. The suction strokes, the compression strokes, and the discharge strokes in the two

cylinder chambers

53 and 54 are set within a range shifted by a rotation angle of 180 [degrees] with the axis C of the rotation shaft 51 interposed therebetween. Thus, in the compression mechanism section 60, each compression chamber 48 performs a series of cycles of the suction stroke, the compression stroke, and the discharge stroke twice (two cycles) during one rotation around the axis C of the rotation shaft 51.

In the housing 10, as shown in FIG. 1, a discharge port 11 a that discharges a compressed high-pressure refrigerant gas G to the condenser is provided in the case 11, and the low-pressure refrigerant gas G from the evaporator is sucked into the case 11. A suction port 12 a is provided in the front head 12. Inside the housing 10, a suction chamber 13 that is a space into which the low-pressure refrigerant gas G sucked through the suction port 12a is introduced, and a discharge that is a space through which the high-pressure refrigerant gas G discharged through the discharge port 11a passes. A chamber 14 is provided. The suction chamber 13 is formed by being partitioned by the front head 12 and the front side block 20 of the compression mechanism portion 60, and the discharge chamber 14 is formed by being partitioned by the case 11 and the rear side block 30 of the compression mechanism portion 60. The

As shown in FIG. 2, the suction chamber 13 and the

cylinder chambers

53, 54 lead to a stroke in which the volume of each compression chamber 48 increases through the

suction holes

22, 23 formed in the front side block 20. As a result, the refrigerant gas G in the suction chamber 13 is supplied to the compression chamber 48 in the suction stroke (stroke in which the volume increases). Further, the discharge chamber 14 and each compression chamber 48 lead to a stroke in which the volume of each compression chamber 48 decreases through the discharge hole 44 formed in the cylinder 40 and the communication hole formed in the rear side block 30. Accordingly, the high-pressure refrigerant gas G is discharged from the compression chambers 48 to the discharge chambers 14 in the discharge stroke corresponding to the final stage of the compression stroke. As shown in FIG. 1, an oil separator 65 for separating the refrigerating machine oil R mixed with the discharged refrigerant gas G is provided on the path of the refrigerant gas G between each compression chamber 48 and the discharge chamber 14. Provided. The separated refrigerating machine oil R is increased in pressure by the pressure of the refrigerant gas G in the discharge chamber 14, and is supplied to the back (bottom) side of each groove of the rotor 50 provided with each vane 58. 58 is used for pressing against the inner peripheral surface 49 of the cylinder 40 (so-called vane back pressure). In the housing 10 (compressor 100), as shown in FIG. 3, a check valve 70 for preventing the backflow of the refrigerant gas G from the suction chamber 13 is provided in the suction port 12a of the front head 12.

As shown in FIG. 5, the check valve 70 is provided on a cylindrical peripheral wall 17 formed in the suction port 12 a and includes a valve body 71, a coil spring 72 as a spring member, and a stopper member 73. The valve body 71 is provided in contact with the peripheral wall 17 of the suction port 12a, and is movable in the direction of the axis C1 of the suction port 12a while maintaining the inscribed state. The coil spring 72 extends most in an unloaded state and exerts an elastic force that resists the operation (compression) of bringing one end side (one end winding portion) and the other end side (the other end winding portion) closer to each other. Consists of springs. The coil spring 72 is provided in a front view of FIG. 5, with the lower end in contact with the bottom surface of the suction port 12 a and the upper end in contact with the valve body 71, and gives the valve body 71 a pressing force. The stopper member 73 is provided on the upper side of the suction port 12a when viewed from the front in FIG. 5, and defines the upper limit position of the valve body 71 in the suction port 12a by contacting the valve body 71.

As shown in FIG. 4, two

openings

18 and 19 communicating with the suction chamber 13 are formed in the peripheral wall 17 of the suction port 12 a with which the valve body 71 is inscribed. In the suction chamber 13, a first flow path 15 that communicates with the opening 18 and a second flow path 16 that communicates with the opening 19 are formed. The first flow path 15 is connected to the suction hole 22 (see FIG. 2) leading to one cylinder chamber 53 at the suction end 15a, and the second flow path 16 is connected to the suction hole 23 (leading to the other cylinder chamber 54). 2) and the suction end 16a. Therefore, the peripheral wall 17 of the suction port 12a has a path that leads from the opening 18 to the one cylinder chamber 53 through the first flow path 15 and the suction hole 22, and the other from the opening 19 through the second flow path 16 and the suction hole 23. And a path leading to the cylinder chamber 54.

As shown in FIG. 5, the valve body 71 of the check valve 70 is pressed against the stopper member 73 by the coil spring 72 when the compression mechanism 60 is not operating, and the portion (opening) of the peripheral wall 17 is branched. 18, 19). At this time, the valve body 71 closes the space above itself and the openings 18 and 19 (the opening degree is zero). This is hereinafter referred to as a closed position in the valve body 71. The valve body 71 of the check valve 70 has a negative pressure in the suction chamber 13 when the compression mechanism 60 is operated, and moves downward to the axis C1 of the suction port 12a against the pushing force of the coil spring 72. Moved along. Then, the valve body 71 communicates the space above itself with the first flow path 15 and the second flow path 16 through the

openings

18 and 19, and enters the

cylinder chambers

53 and 54 through the suction holes 22 and 23. Let them communicate. This is hereinafter referred to as an open position in the valve body 71. Here, in the suction chamber 13, the pressure decreases as the rotational speed of the rotary shaft 51 of the compression mechanism unit 60 increases, and therefore the amount of the valve element 71 moving downward against the pressing force of the coil spring 72 increases. . Then, the valve body 71 moves downward as the rotational speed of the rotary shaft 51 of the compression mechanism section 60 increases, and the area of the

openings

18 and 19 that is not substantially blocked (the opening degree of the valve body 71) is increased. Let

Thus, the valve body 71 (check valve 70) is in the closed position when the compression mechanism 60 is not operating, and prevents the refrigerant gas G from going back and forth between the evaporator and the suction chamber 13. Further, the valve body 71 (check valve 70) is in an open position when the compression mechanism 60 is operated, and the opening degree of the valve body 71 is changed while allowing the refrigerant gas G to flow into the suction chamber 13 from the evaporator. Let For this reason, the valve body 71 (check valve 70) has a function of preventing the reverse flow of the refrigerant gas G to the evaporator when the compression mechanism 60 is not operated (closed position), and the compression mechanism 60 is operated. And a function of adjusting the flow rate of the refrigerant gas G to the suction chamber 13 when it is open (open position).

Here, the technical problems of the conventional gas compressor (compressor) will be described. The problem of this technique is that even in the compressor 100 of the first embodiment, the fully open spring load P and the spring load mass ratio Ra (see FIG. 6) in the coil spring 72 of the check valve 70 must be set as described later. Since it has the same subject, it demonstrates using the compressor 100. FIG. The compressor 100 constitutes a part of the air conditioning system described above, and is appropriately driven and stopped according to the operation. In the air conditioning system, when the compressor 100 is stopped, noise is generated immediately after the stop. This is considered to be caused by the following.

In a circulation path for circulating a fluid such as the refrigerant gas G, it is known that when the circulation is interrupted in the middle of the circulation path, the pressure at the location interrupted by the kinetic energy of the fluid rapidly increases. When the compressor 100 used in the air conditioning system is stopped, the pressure of the refrigerant gas G in the suction chamber 13 suddenly increases, and between the suction chamber 13 and the outside of the suction port 12a (pipe connected to the evaporator). A pressure difference occurs. Then, in the compressor 100, the high-pressure refrigerant gas G flows backward from the suction port 12a to the evaporator, causing a pressure fluctuation in a pipe connected to the evaporator. Then, an impact sound is generated in the piping due to the generation of an excitation force that shakes the piping due to pressure fluctuation, and the impact sound is transmitted as noise. Here, in the compressor 100, the check valve 70 is provided in the suction port 12a to prevent the reverse flow of the refrigerant gas G. However, since the pressure in the suction chamber 13 is suddenly increased, the check valve 70 is sucked. It is considered that the reverse flow of the refrigerant gas G causing the pressure fluctuation occurs before closing the port 12a.

In order to prevent the generation of such noise, the compressor 100 of the present invention is configured such that the valve body 71 of the check valve 70 is immediately in the closed position in order to close the suction port 12a as soon as it is stopped. . Specifically, the configuration is as follows. In the compressor 100, the spring load P (N) when fully opened in the coil spring 72 of the check valve 70 is set to a predetermined value or more, which will be described later, from the viewpoint of immediately moving the valve body 71 to the closed position when stopped. The fully open spring load P (N) is a state in which the valve body 71 is most retracted in the check valve 70 and the two

openings

18 and 19, that is, the suction port 12a are most opened, in other words, the coil spring 72 is most bent. The coil spring 72 refers to a force that pushes the valve element 71 toward the closed position when the coil spring 72 is in a fully open (collapsed) state (full open state). Here, when the compressor 100 is stopped, the negative pressure in the suction chamber 13 is weakened (pressure is increased) compared with that during operation, and the pressure in the space above the valve body 71 of the check valve 70 is reduced. The difference becomes smaller. For this reason, in the compressor 100, when the fully open spring load P (N) in the coil spring 72 becomes larger than the pressure difference, the valve body 71 starts to move to the closed position, so the fully open spring load P (N) is increased. Thus, the valve body 71 can be quickly moved to the closed position.

The applicant conducted a test for occurrence of noise as follows in order to set a predetermined value of the fully open spring load P (N) in the coil spring 72 of the check valve 70. In the test, a compressor 100 is provided to configure a vehicle air conditioning system, and noise in the vehicle is confirmed by human hearing (hearing). In the compressor 100, 0.8 g of the valve element 71 is used in the check valve 70 having the above-described configuration, and the fully open spring load P (N) in the coil spring 72 in a state of being bent (shrinked) until fully opened. Change in steps. The test result (auditory test result) by this hearing (audibility) is shown in the table of FIG. The table of FIG. 6 shows the fully open spring load P (N) that is changed stepwise in the left column, the spring load mass ratio Ra (N / kg) in the middle column, and the audibility test results in the right column. Show. The spring load mass ratio Ra is a ratio of the fully open spring load P (N) in the coil spring 72 to the mass (kg) of the valve body 71, that is, a value obtained by dividing the fully open spring load P by the mass of the valve body 71. . In addition, the auditory test result is determined by the presence or absence of noise generated by human hearing in the car as described above. If noise is generated, the result is x. A triangle indicates that no noise can be confirmed. If you are not concerned about the noise (△), this hearing test is performed to confirm the noise, so it is sensitive to the noise, but it has been reduced to a level where it is difficult to understand. Say.

In this audibility test, as shown in FIG. 6, when the fully open spring load P is set to 0.4 (N), noise is not a concern (Δ), and the spring load mass ratio Ra at this time is 500 ( N / kg). Further, in this hearing test, when the fully open spring load P is set to 0.7 (N), noise cannot be confirmed (◯), and the spring load mass ratio Ra at this time is 875 (N / kg). . For this reason, the compressor 100 of the present invention basically sets the fully open spring load P to 0.4 (N) or more in order to prevent the occurrence of substantial noise, and more preferably the fully open spring load P is set to 0. Generation of noise is more reliably prevented by setting it to 7 (N) or more. The compressor 100 of the present invention basically has a spring load mass ratio Ra of 500 (N / kg) or more, more preferably a spring load mass ratio Ra of 875 (N / Kg) to prevent noise generation more reliably.

Here, the fully open spring load P is a value obtained by multiplying the spring constant (N / mm) of the coil spring 72 by the amount of deflection (shrinkage) (the amount of fully open deflection) (mm) of the coil spring 72 in the fully open state. Can show. For this reason, the setting of the fully open spring load P can be realized by appropriately combining increasing the spring constant and increasing the fully opened deflection amount. The compressor 100 (check valve 70) of the first embodiment increases the spring constant as compared with the conventional compressor (gas compressor), so that the fully open spring load P is the above-described predetermined value (0.4 (N)). , More preferably 0.7 (N)) or more. Moreover, the compressor 100 (check valve 70) of Example 1 raises a spring constant compared with the conventional compressor (gas compressor), The spring load mass ratio Ra is the predetermined value (500 (N / kg)) mentioned above. And more preferably 875 (N / kg)) or more. Here, in the compressor 100 (check valve 70) of the first embodiment, the fully open spring load P is set to 0.4 (N) and the spring load mass ratio Ra is set to 500 (N / kg). Both the fully open spring load P and the spring load mass ratio Ra are set together so that the spring load P is 0.7 (N) and the spring load mass ratio Ra is 875 (N / kg). May be. Setting that combines both can be realized by setting the spring constant and the fully open deflection amount in view of the mass (kg) of the valve element 71. As an example, the compressor 100 of the first embodiment sets the fully open spring load P to 0.4 (N) and the spring load mass ratio Ra to 500 (N / kg).

In the compressor 100 of the first embodiment, as described above, when stopped and the compression mechanism 60 is not operating, the valve body 71 is pressed against the stopper member 73 by the coil spring 72 in the check valve 70. Closed position. In the compressor 100, when the compression mechanism 60 is activated and activated, the suction chamber 13 becomes negative pressure, so that the valve element 71 moves downward against the pushing force of the coil spring 72 in the check valve 70. Open position. The compressor 100 causes the low-pressure refrigerant gas G to flow into the suction chamber 13 through the suction port 12a, compresses the refrigerant gas G by the compression mechanism unit 60, and discharges the refrigerant gas G to the discharge chamber 14. The high-pressure refrigerant gas G Is discharged through the discharge port 11a. Then, the air conditioning system cools the inside of the vehicle by repeating the above process using the refrigerant gas G compressed by the compressor 100.

The air conditioning system repeats driving the compressor 100 again when the interior of the vehicle reaches a set temperature to stop the compressor 100 to prevent excessive cooling and when the interior of the vehicle reaches a temperature somewhat higher than the set temperature. At this time, the compressor 100 sets the fully open spring load P (N) in the check valve 70 to be equal to or greater than the predetermined value described above. Therefore, as soon as the compressor 100 is stopped, the valve body 71 starts to move to the closed position. Immediately, the suction port 12a is shut off as a closed state. Thereby, in the air conditioning system using the compressor 100, it is possible to prevent noise from occurring when the compressor 100 is stopped.

In the compressor 100 according to the first embodiment of the present invention, the following effects can be obtained.

Since the compressor 100 sets the fully open spring load P in the check valve 70 to 0.4 (N) or more, when the compressor 100 is stopped, the valve body 71 can be immediately moved to the closed position. Is immediately closed to block the suction port 12a. For this reason, as soon as the compressor 100 is stopped, the backflow of the high-pressure refrigerant gas G from the suction port 12a to the evaporator can be prevented, and the generation of noise in the used air conditioning system can be prevented.

Since the compressor 100 sets the fully open spring load P in the check valve 70 to 0.7 (N) or more as a more preferable example, the valve body 71 can be moved more quickly to the closed position when stopped. The check valve 70 can be closed earlier, and the suction port 12a can be shut off. For this reason, the compressor 100 can more reliably prevent the reverse flow of the high-pressure refrigerant gas G from the suction port 12a immediately after being stopped to the evaporator, and can more reliably prevent the generation of noise in the used air conditioning system. .

Since the compressor 100 sets the spring load mass ratio Ra in the check valve 70 to 500 (N / kg) or more, the influence of the mass (kg) of the valve body 71 is also taken into consideration, so that the valve body when stopped The start of the movement of 71 to the closed position can be surely accelerated, and the check valve 70 can be immediately closed to shut off the suction port 12a. For this reason, as soon as the compressor 100 is stopped, the backflow of the high-pressure refrigerant gas G from the suction port 12a to the evaporator can be prevented, and the generation of noise in the used air conditioning system can be prevented. In addition, when the compressor 100 is stopped in the check valve 70 by setting the fully open spring load P to 0.4 (N) or more and the spring load mass ratio Ra to 500 (N / kg) or more. The start of movement of the valve body 71 to the closed position can be accelerated more reliably.

The compressor 100 is stopped because the influence of the mass (kg) of the valve body 71 is also taken into account in order to set the spring load mass ratio Ra in the check valve 70 to 875 (N / kg) or more as a more preferable example. In this case, the valve body 71 can be started to move to the closed position more reliably, and the check valve 70 can be closed earlier so that the suction port 12a can be shut off. For this reason, the compressor 100 can more reliably prevent the reverse flow of the high-pressure refrigerant gas G from the suction port 12a immediately after being stopped to the evaporator, and can more reliably prevent the generation of noise in the used air conditioning system. . In addition, when the compressor 100 is stopped in the check valve 70 by setting the fully open spring load P to 0.7 (N) or more and the spring load mass ratio Ra to 875 (N / kg) or more. The start of movement of the valve body 71 to the closed position can be accelerated more reliably.

The compressor 100 has a spring constant (N / mm) of the coil spring 72 higher than that of a conventional compressor (gas compressor) in order to set the fully open spring load P in the check valve 70. For this reason, the compressor 100 can be realized by using only the coil spring 72 having a different spring constant without causing a design change from the conventional compressor, and can be prevented from becoming larger than the conventional compressor. Further, the compressor 100 can increase the pressing force (spring load when fully closed) of the valve element 71 at the closed position in the check valve 70 at the closed position, compared with the conventional compressor. It is possible to improve the protrusion of each vane 58 from the rotor 50. This is due to the following. When the conventional compressor is stopped, the pressure in the suction chamber 13 becomes higher than the vane back pressure, so that the vanes 58 may not be properly ejected even when the rotor 50 rotates. On the other hand, the compressor 100 has a higher fully loaded spring load than the conventional compressor, so that the check valve 70 can be opened later than the conventional compressor when driven. Thereby, the compressor 100 can assist the suction chamber 13 to become negative pressure by the operation of the activated compression mechanism section 60, and the pressure in the suction chamber 13 can be made lower than the vane back pressure. Further, it is possible to improve the jump-out of each vane 58 from the rotor 50 at the time of startup.

The compressor 100 can set the fully open spring load P in the check valve 70 by increasing the fully open deflection amount (mm) of the coil spring 72 as compared with the conventional compressor (gas compressor). For this reason, the compressor 100 can be easily realized simply by adjusting the fully open deflection amount of the coil spring 72 in the check valve 70 from the conventional compressor.

The compressor 100 increases the fully open deflection (mm) while increasing the spring constant (N / mm) of the coil spring 72 as compared with the conventional compressor (gas compressor), so that the spring load when the check valve 70 is fully opened is increased. P can be set. Therefore, the compressor 100 can set the fully open spring load P by appropriately adjusting the spring constant and the fully open deflection amount in consideration of the fully closed spring load, the overall size, the strength of the stopper member 73, and the like. It is possible to search for the optimal combination while ensuring the degree of freedom.

As soon as the compressor 100 is stopped, the valve body 71 is brought into a closed position to prevent the reverse flow of the high-pressure refrigerant gas G from the suction port 12a to the evaporator, so that the efficiency of the air conditioning system used can be improved compared to the conventional compressor. Can be improved. This is due to the following. Since the high-pressure refrigerant gas G flowing backward from the suction port 12a is high in temperature, this refrigerant gas G causes an increase in the temperature of the evaporator and piping connected to the evaporator. Here, in the air conditioning system, the air is cooled by the evaporator, so there is a risk that the temperature in the vehicle will rise, and the timing for driving the compressor again is determined based on the temperature rise of the evaporator and the piping connected to it. There is a possibility that the timing is advanced. Further, in the air conditioning system, when the temperature of the evaporator or the piping connected to the evaporator rises, the temperature of the refrigerant gas G existing there increases, and the temperature of the refrigerant gas G sucked by the compressor when driving again is increased. As a result, the compression efficiency of the compressor may be reduced. For this reason, the compressor 100 can improve the efficiency of the air-conditioning system used compared with the conventional compressor.

Therefore, the compressor 100 can prevent the backflow of the refrigerant gas G as soon as it is stopped.

As mentioned above, although the gas compressor (compressor) of this invention has been demonstrated based on Example 1, it is not restricted to Example 1 about a concrete structure, The summary of invention which concerns on a claim and each claim As long as they do not deviate, design changes and additions are permitted.

In the first embodiment, the compressor 100 as an example of the gas compressor (compressor) according to the present invention has been described. However, a housing that partitions the internal space and the external space, a suction port that serves as a gas passage from the outside to the inside of the housing, and allowing the gas to flow into the internal space of the housing through the suction port, and A check valve that prevents backflow of the gas to the external space of the housing through the suction port; and a compression mechanism that sucks, compresses, and discharges the gas that has flowed in via the check valve. The check valve includes a valve body that is moved between an open position that allows the gas to flow in and a closed position that prevents the backflow of the gas, and a spring member that presses the valve body toward the closed position. In the check valve, any gas compressor may be used as long as the fully open spring load in the spring member when the suction port is most opened is 0.4 (N) or more. Limited to Not.

In the first embodiment, the check valve 70 is provided with the

openings

18 and 19 in the peripheral wall 17 forming the suction port 12a. For example, the check valve 70 has openings similar to the

openings

18 and 19 and moves the valve body 71. A cylindrical case that can be received may be provided in the suction port 12a, and may have other configurations, and is not limited to the configuration of the first embodiment. Further, the number of openings provided in the peripheral wall 17 (the same applies to the case) may be set as appropriate, and is not limited to the configuration of the first embodiment.

Furthermore, in Example 1, the spring load mass ratio Ra was set to 875 (N / kg) or more by making the fully open spring load P 0.7 (N) or more using 0.8 g of the valve body 71. As long as the spring load mass ratio Ra is 875 (N / kg) or more, the mass of the valve element 71 and the fully open spring load P may be set as appropriate, and are not limited to the configuration of the first embodiment. Similarly, in the check valve 70, as long as the spring load mass ratio Ra is 500 (N / kg) or more, the mass of the valve body 71 and the fully open spring load P may be appropriately set. The configuration is not limited to one.

In the first embodiment, the compressor 100 is a vane rotary type gas compressor, but the gas compressor according to the present invention is, for example, a vane rotary type such as a swash plate type gas compressor, a scroll type gas compressor, or the like. Other types of gas compressors may be used, and the configuration is not limited to that of the first embodiment.

Cross-reference to related applications

This application claims priority based on Japanese Patent Application No. 2016-114738 filed with the Japan Patent Office on June 8, 2016, the entire disclosure of which is fully incorporated herein by reference.

Claims

A housing that partitions the internal space from the external space;
A suction port serving as a gas passage from the outside to the inside of the housing;
A check valve that allows the gas to flow into the interior space of the housing through the suction port and prevents backflow of the gas into the outer space of the housing through the suction port;
A compression mechanism that sucks in, compresses, and discharges the gas flowing in through the check valve;
The check valve has a valve body that is moved between an open position that allows the gas to flow in and a closed position that prevents the backflow of the gas, and a spring member that presses the valve body toward the closed position. And
In the check valve, the fully open spring load in the spring member when the suction port is most opened is set to 0.4 (N) or more.
2. The gas compressor according to claim 1, wherein in the check valve, the fully open spring load of the spring member is set to 0.7 (N) or more.
2. The check valve according to claim 1, wherein a spring load mass ratio indicated by a ratio of the fully open spring load in the spring member to a mass of the valve body is set to 500 (N / kg) or more. Gas compressor.
A housing that partitions the internal space from the external space;
A suction port serving as a gas passage from the outside to the inside of the housing;
A check valve that allows the gas to flow into the interior space of the housing through the suction port and prevents backflow of the gas into the outer space of the housing through the suction port;
A compression mechanism that sucks in, compresses, and discharges the gas flowing in through the check valve;
The check valve has a valve body that is moved between an open position that allows the gas to flow in and a closed position that prevents the backflow of the gas, and a spring member that presses the valve body toward the closed position. And
In the check valve, a spring load mass ratio indicated by a ratio of a fully open spring load in the spring member when the suction port is most opened to a mass of the valve body is set to 875 (N / kg) or more. Characteristic gas compressor.
5. The gas compressor according to claim 4, wherein in the check valve, the fully open spring load in the spring member is set to 0.7 (N) or more.
The gas compressor according to any one of claims 1 to 5, wherein the check valve satisfies the setting of the fully open spring load by setting a spring constant of the spring member.