JPS62251482A - Check valve for delivery port of compressor - Google Patents

Abstract

PURPOSE:To improve the efficiency of a compressor by constructing a check valve for allowing flow-out through a delivery port to a delivery path with two check valves having different setting levels of differential pressure. CONSTITUTION:A check valve 21 for allowing flow-out through a delivery port 18 to a delivery path 20 is constructed with first and second check valves 22, 23. The spring force of a first spring member 71 is determined according to a primary setting pressure while the spring force of a second spring member 74 is determined according to a secondary setting pressure. Consequently, the first check valve 22 is suitable for small flow where the residual volume can be reduced by the small path of the check valve 22 thereby the efficiency of compressor can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION A9 Object of the Invention (1) Field of Industrial Application The present invention relates to a compressor, and more particularly to an improvement in a discharge port section in terms of capacity.

(2) Conventional technology In conventional compressors, a check valve such as a reed valve is arranged at the discharge port (generally there are several) that communicates the compression chamber and the discharge passage, and the compressed gas on the discharge passage side is This prevents backflow to the compression chamber side.

This check valve automatically opens and closes depending on the pressure difference between the compression chamber and the discharge passage, and has an appropriate opening degree depending on the flow rate passing through the check valve.

However, in such a conventional discharge port check valve structure, a non-ignorable volume of the discharge port passage, so-called residual volume, remains between the check valve and the compression mechanism.
This is a factor that reduces the efficiency of the compressor.

For this reason, measures are taken to reduce this residual volume by reducing the diameter of the discharge port passage, but simply reducing the diameter of the passage may be good at small flow rates, but at large flow rates, the passage resistance will increase and the compression work will increase. This increases the efficiency, and on the contrary becomes inefficient.

(3) Problems to be solved by the invention The present invention aims to solve the above problems.
Focusing on the presence of residual volume in the discharge port passage, which is a factor in reducing the efficiency of compressor compressors, the present invention aims to provide a check valve structure for the discharge port that can reduce this residual volume and improve the efficiency of the compressor. purpose.

B0 Structure and operation of the invention (+) Means for solving the problems According to the invention, the discharge port opening into the compression chamber is provided with a check valve that allows outflow from the discharge port to the discharge passage. In this compressor, the check valve prevents a small amount of flow from flowing out from the discharge port 6 to the discharge passage when the pressure difference before and after the check valve becomes larger than a predetermined primary setting pressure Pi. The first small flow check valve that allows and the pressure difference is 1
It includes a second large flow rate check valve that allows a large flow rate to flow out from the discharge port to the discharge passage when the secondary set pressure P2 is higher than the next set pressure Pl.

(2) Operation When the flow rate of gas compressed in the compression chamber is small, the pressure difference before and after the check valve is small, and the pressure difference is the predetermined pressure P
When the pressure difference exceeds i, the first small flow check valve commensurate with the pressure difference opens, and the compressed gas is thereby discharged into the discharge passage through the small passage for the first check valve. The first small flow rate check valve takes care of the pressure difference between the predetermined pressure P1 and the predetermined pressure P2, which is larger than the predetermined pressure P1.

When the flow rate of the gas being compressed in the compression chamber increases.

Due to the orifice mechanism, the pressure difference corresponding to this increase in flow rate also increases, and when this pressure difference exceeds a predetermined pressure P2, the second large flow rate check valve corresponding to the pressure difference opens. The compressed gas is discharged into the discharge passage through the large passage for the second check valve.

(3) Examples Hereinafter, the present invention will be explained in detail with reference to the drawings.

FIG. 1 shows a vehicular refrigerant compressor device to which the present invention is applied.

This compressor device includes a compression 111, a pair of compression ml, and a control device 4 for controlling the opening and closing of the on-off valve 2.3.
including.

The compressor 1 is a so-called vane type rotary compressor, and includes a rotor 6 having a plurality of bays 75 on the outer periphery, and the rotor 6.
and a housing 7 in which is housed.

The rotor 6 has a rotor body 9 rotatably supported by a rotating shaft 8, and a plurality of vane grooves 10 into which the vanes 5 are loosely fitted are formed on the outer periphery of the rotor body 9. Note that the rotating shaft 8 is connected to the output shaft of the vehicle engine via a TLN1 clutch (not shown).

The housing 7 includes a housing body 11, an upper housing 12 attached to the upper part of the housing body 11,
and a side housing 13 attached to the side of the housing body 11.

The side housing 13 is attached to the back side and the front side of the housing body 11 in the paper of FIG.

Inside the housing body 1, there is a side housing chamber 1.
In the inner peripheral wall surface 15 of the rotor 6, a suction port 17 is opened on the starting end side along the rotational direction 16 of the rotor 6, and a discharge port 18 is opened on the terminal end side. In addition, suction bow) 17 is the rotor 6
It is recessed so as to extend along the rotational direction 16 of. /\The housing body 11 and the upper housing 12 are respectively formed with a suction passage 19 and a discharge passage 20 that communicate with each port 17,18. Note that the discharge passage 20 is a passage portion (discharge port passage portion) formed in the housing body 11.
20a and a passage portion 2 formed in the upper housing 12.
0b, and a check valve 21 is interposed between these passage portions 20a and 20b.

This check valve 21 is formed in two series, includes a first check valve 22 and a second check valve 23, and is configured to allow refrigerant gas to flow from the passage portion 20a to the passage portion 20b. be done. In the upper housing 12, a valve chamber 24 for accommodating the check valve 21 is defined by the housing body 11.

Further, an unload port 25 is opened in the inner circumferential wall surface 15 of the cylinder chamber 14 near the discharge port 18 . This unload port 25 communicates with the suction passage 19 via an unload passage 26.

This unloading passage 26 is formed in the housing body 11 and the side housing 13, and the first on-off valve 2 is interposed in the middle of this unloading passage 26. By this first on-off valve 2, the unload passage 26 is connected to the suction passage 19.
The passage portion 26a is divided into a passage portion 26a that communicates with the unload port 25, and the passage portion 26b that communicates with the unload port 25.
A reverse ratio valve 27 is interposed in the middle of 6b. This check valve 27 is configured by a reed valve 27a and a regulating plate 27b, similarly to the check valve 21, so as to allow the flow of refrigerant gas from the unload port 25 to the first on-off valve z side. . Further, a valve chamber 28 for accommodating a check valve 27 is formed in the housing body 11.

On the inner side wall 30 of the cylinder chamber 14, that is, on the side surface of the side housing 13, there is a space located on the front side of the suction port 17 in the rotational direction 16 of the rotor 6, that is, at an intermediate position between the suction port 17 and the discharge port 18. Then, the bypass port 31 is opened. This bypass port 31 is
As shown in FIG. 2, the hole has a long hole shape extending in the longitudinal direction that matches the phase of the vane 5 so that it can be aligned with the side surface of the rotating vane 5 (indicated by the two-dot chain line). Furthermore, the dimension d2 in the width direction perpendicular to the longitudinal direction of the bypass port 31 is made smaller than the plate thickness d1 of the vane 5.

This bypass port 31 is communicated with the suction port 17 via a bypass passage 32. This bypass passage 32 is formed in the housing body 11 and the side housing 13,
The second on-off valve 3 is interposed in the middle of this bypass passage 32. By this on-off valve 3, the bypass passage 32 is divided into a passage part 32a communicating with the suction port 17 and a passage part 32b communicating with the bypass port 31,
A check valve 33 is interposed in the middle of this passage portion 32b. The check valve 33 is configured to allow the flow of refrigerant gas from the bypass port 31 to the second on-off valve 3 side.
1, a valve chamber 34 for accommodating the check valve 33 is formed in the reed valve 33a and the housing 13.

Similar to the bypass port 31, a plurality of sub-discharge ports 35 and 36 are opened in the inner side wall 30 of the cylinder chamber 14. These sub-discharge ports 35° 36 are located on the front side of the bypass port 31 in the rotational direction 16 of the rotor 6,
That is, they are opened at intervals along the rotational direction 16 so as to be located at an intermediate position between the bypass port 31 and the discharge port 1B. These sub-discharge ports 35, 3
The relationship between the vane 6 and the rotating vane 5 is similar to the relationship with the bypass port 31 described above. That is, the sub-discharge port 35
．． 36 has an elongated hole shape extending in the longitudinal direction of the vane 5 so as to be aligned with the side surface of the vane 75. Furthermore, the dimension d3 in the width direction perpendicular to the longitudinal direction of the sub-discharge bow) 35.36 is:
It is made smaller than the plate thickness d1 of the vane 5.

These sub-discharge ports (35, 36) are communicated with the valve chamber 24 via one discharge passage 37. This one discharge passage 37 is formed in the side housing 13, and a pair of check valves 38 and 39 are interposed in the middle of this one discharge passage 37 corresponding to each of the sub-discharge ports 35 and 36. These check valves 38.39
By one discharge passage 37, each sub-discharge port 35.36
It is divided into passage portions 37a and 37b communicating with the valve chamber 24, and passage portion 37c communicating with the valve chamber 24. These check valves 38, 39 are connected to the valve chamber 24 from each sub-discharge port 35, 36.
Like the check valve 21, it is configured by reed valves 38a, 39a and regulation plates 38b, 39b to allow the flow of refrigerant gas to the side. In addition, the side housing 13 includes
A valve chamber 40 is formed for accommodating a check valve 38,39.

The first on-off valve 2 is a so-called electromagnetic valve, and includes a solenoid 50 and a fixed core 5 which is activated by electric power of the solenoid 50.
a movable core 52 that is magnetically attracted to the movable core 52;
The on-off valve 2 includes a valve body 53 that operates integrally with the on-off valve 2, and a coil spring 54 that biases the valve body 53 to the closed state.
In order to prevent an undesired drag force from acting on the magnetic attraction force due to a pressure difference in the refrigerant gas between the passage portions 26a and 26b,
A bellows 55 for pressure compensation is installed to prevent this from occurring. Further, the communication hole 53a formed in the valve body 53 guides the pressure in the unload passage 26 into the bellows 55 to equalize the pressure, thereby making it easy to open and close the valve body 53. The biasing force of the coil spring 54 is adjusted by an adjustment screw M2S.

The first on-off valve 2 configured in this manner is controlled to be fully closed or fully opened on and off by power activation of the solenoid 50 by the control device 4.

The second on-off valve 3 is configured similarly to the first on-off valve 2,
Solenoid 60, fixed core 61. Movable core 62. Valve body 6
3. Communication hole 6 including coil spring 64 and bellows 65
3a and adjustment screw M6S are also the same.

This second on-off valve 3 is operated by a solenoid 6 controlled by a control device 4.
The opening degree is freely controlled from fully closed to fully open, that is, linear opening degree control is performed by applying zero electric power, more specifically, by changing the applied electric power.

The detailed structure of the check valve 21 will be explained with reference to FIG. 3. The wooden check valve 21 has a first check valve 22 and a second check valve 23.
As mentioned above, the first check valve 22 includes a first valve body 70 whose valve seat contact surface is a flat surface, and a second valve body 70 which has a flat valve seat contact surface.
and a first spring member 71 that biases and closes a valve hole 73 provided in a valve body 72. One end of the first spring member 71
The other end of the valve body 72 is engaged with the ceiling within the cylindrical portion 72a of the first valve body 72, and the other end thereof is engaged with the flange of the first valve body 70.

The second check valve includes a second valve body 72 and a second spring member 74 that urges and closes the valve body 72 to the discharge port passage portion 20a, and the second connecting body 72 has a valve seat contact surface. is made flat, one end of the second spring member 74 is locked to the ceiling surface of the valve seat 24, and the other end is locked to the flange of the second valve body 72.

The cylindrical portion 72a of the second valve body 72 has window portions 75 at appropriate intervals.
is drilled.

In this embodiment, the size and length of the valve hole 73, that is, the volume, are determined to be as small as possible in consideration of the volume of the discharge port passage section 20a and in accordance with the state where the flow rate of the compressed gas is small. Further, the spring force of the first spring member 81 is determined to be 1 in accordance with the primary setting pressure. The spring force of the second spring member 84 is determined in accordance with the secondary set pressure.

FIG. 4 shows another aspect of the check valve. The first check valve 22 has a first valve body 80 with a tapered valve seat abutting surface, and a second valve body that connects this valve body 80 with a tapered valve seat contact surface. 82. Therefore, the first valve body 80 is brought into contact with the tapered valve seat formed in the second valve body 82. ing.

The second check valve 23 has a valve seat contact surface that is tapered.
The valve body 82 and this valve body 82 are connected to the discharge port passage i'fB2.
0a and a second spring member 84 that is biased to close. Therefore, this second valve body 82 also comes into contact with a tapered valve seat formed in the discharge port passage section 20a.

The size of the valve hole 83 and the spring force kl of the first and second spring members 81.84 in this embodiment.

The size of k2 is determined according to the embodiment shown in FIG. 3, but in this embodiment, the discharge port passage 2 for large flow rate is
The first check valve 22 is a so-called reed valve, which shows another check valve configuration in Fig. 5. The first valve body 90 includes a first valve body 90 and a regulating plate 91 that regulates the opening degree of the valve body 90. The first valve body 90 closes a valve hole 93 provided in a second valve body 92. The second check valve 23 includes a second valve body 92 having a tapered valve seat contacting surface, and a second spring member 94 that biases and closes the valve body 92 to the discharge port passage 20a. Therefore, this second valve body 92 is in contact with a tapered valve seat formed in the discharge port passage section 20a.

In this embodiment, the size of the valve hole 93, the spring force kl of the first valve body 90, and the spring force 2 of the second spring member 94 are determined according to the previous embodiment. This is characterized in that the check valve 22 for small flow rates is made of reed pulp and has a simple structure, and that the discharge port passage 20a for large flow rates can be made as small as possible.

In the vehicle refrigerant compressor device configured as described above, the cylinder chamber 14 is divided into a plurality of volume chambers by each vane 5. That is, it is divided into a suction chamber 14a in which the suction port 17 is open, a high compression chamber 14c located near the discharge port 18, and a compression chamber 14b located between the suction chamber 14a and the high compression chamber 14c (second (see figure),
More specifically, the volume of each of the volume chambers 14a to 14c gradually changes from increasing to decreasing as the eccentric rotor 6 rotates, and the high compression chamber 14c has higher compression than the compression chamber 14b. As a result, the compressor 1 exerts a suction-compression pumping action on the refrigerant gas.

In such a pump action, when the first and second on-off valves 2.3 are closed, all of the compressed refrigerant gas is discharged from the discharge port 18 to the discharge passage 20, and the compression 411 is 100% compression capacity is achieved. Moreover, when the first on-off valve 2 is opened, most of the compressed refrigerant gas is returned from the unload port 25 to the suction passage 19 via the unload passage 26, and the compressed refrigerant gas is
is largely suppressed in its compression capacity. Furthermore, when the first on-off valve 2 is closed and the second on-off valve 3 is opened, a portion of the refrigerant gas compressed to a relatively low pressure flows into the bypass port).
31 and returns to the suction port 17 via the bypass passage 32, and a portion of the compression capacity of the compressed al is suppressed depending on the opening degree of the second on-off valve 2. Note that when the first on-off valve 2 is opened, the second on-off valve 3 is also fully opened, and as a result, as is clear from section E, the compression capacity of the compressor 1 is further reliably suppressed. be done.

In this way, by controlling the opening and closing of the first and second on-off valves 2.3, the compression volume of the compressor 1 is made variable with high accuracy and over a wide range.

In this stroke, the check valve 21 functions as follows.

When the compressor l is closed, the first on-off valve 2 is closed and the second on-off valve 3 is closed.
When operating with a large opening, the pressure of refrigerant gas in the compression chamber is reduced compared to the case of full compression capacity, and the front copper of the check valve 21 L! litigation t+ su
0: + 1
Spider 1) When the pressure τi becomes higher than P1, the first valve body 70 opens against the spring force kl of the first spring member 71, and the low compressed gas passes through the valve hole 73 and flows into the valve chamber 24. It will be discharged to the discharge passage 20 via. When the discharge is finished, the first valve body 70 immediately closes the valve hole 73 due to the biasing force of the first spring member 71 and functions as a check valve.

When the compression all is operated under high load by reducing the opening of the second on-off valve 3 or closing the first and second on-off valves 2.3, the refrigerant gas in the compression chamber is compressed to a high pressure. is,
The flow rate increases compared to the small flow rate. When the flow rate increases, the first check valve 22 can no longer handle the problem, passage resistance increases, and as a result, the pressure inside the compression chamber 14c increases, causing the valve chamber 2
4, and a pressure difference between the inside of the compression chamber 14c and the discharge port passage section 20a.

When the pressure difference becomes larger than the secondary set pressure P2, which is larger than the above-mentioned primary set pressure pt, the second valve body 72 opens against the spring force of the second spring member 74, Highly compressed gas is discharged from the discharge port passage section 20a through the valve chamber 24 to the discharge passage 20. When the discharge is finished, the second valve body 72 is immediately moved to the discharge port by the biasing force of the second spring member 74. The passage portion 20a is closed and the check valve operates.

The bypass port 31 and the sub-discharge ports 35 and 36 each have an elongated hole shape extending in the longitudinal direction of the vane 5 so as to be aligned with the side surface of the vane 5.

Since the dimensions d2 and d3 in the width direction perpendicular to the longitudinal direction are made smaller than the plate thickness dl of the vane 5, the compressed refrigerant gas flows through the ports 31, 35 and 36 to the vane 7.
There is no leakage to the volume chamber on the rear side in the rotational direction of No. 5.

Furthermore, since the sub-discharge ports 35 and 36 are provided, when the compression pressure of the refrigerant gas in the high compression chamber 14c becomes higher than a predetermined pressure, this compressed refrigerant gas flows through the 1-discharge passage 37. Since the refrigerant gas flows into the valve chamber 24 of the discharge port 18 through the refrigerant gas, the refrigerant gas is not excessively compressed, and therefore, the engine power for driving the compressor I can also be saved. Furthermore, since the sub-discharge ports (35, 36) are arranged at intervals from each other along the rotational direction of the rotor 6, compression pressures corresponding to their positions can be obtained.

In other words, the discharge pressure of the refrigerant gas can be arbitrarily set depending on the number and position of the sub-discharge ports.

Referring to FIG. 3, the control device 4 includes a plurality of memories Ml, M
2. A processing device 100 having M3...

The processing device 100 includes a drive circuit 71 for opening and closing the first and second on-off valves 2 and 3 in accordance with signals from the processing device ioo. In order to control the first and second on-off valves 2.3 according to the environment and the conditions set by the operator, signals as parameters representing these conditions are input.

For example, the opening Th of a throttle valve (not shown) provided in a means for supplying air-fuel mixture to the vehicle engine and the voltage vb of a battery mounted on the vehicle are selected as parameters representing the above-mentioned operating conditions. Further, as parameters representing the environmental conditions inside and outside the vehicle, for example, the vehicle interior temperature Tr, the amount of solar radiation Sr, and the outside air temperature To are selected.

Furthermore, one parameter representing the operator's setting conditions, for example, the set temperature Ts in the vehicle interior is selected.

The processing device 100 processes these parameters Th, Vb, Tr.
, Sr, To, Tsry) Follow the input signal.

The opening and closing of the first and second on-off valves 2.3 is controlled via the drive circuit 101.

The function of the processing unit gioo will be explained according to the following operational modes.

(A) When the battery voltage vb is lower than the reference value In this mode (A), the first and second on-off valves 2゜3 are opened, thereby reducing the load on the vehicle engine related to the driving force of the compressed Al. be done.

This mode (A) assumes a case where the voltage consumption of the battery is high or the electromotive force of the battery is low, and in such a case, the load on the vehicle engine is reduced as much as possible. Let me reduce it.

In other words, the cooling capacity is suppressed and the power generating capacity of the generator connected to the output shaft of the engine is increased so that the battery can be sufficiently charged.

(B) When the vehicle is accelerating, +rrs t#, lt/mouth) 慴 l斗 Song: k M fil' it /m) b rii
l 1? +w 21 and the second on-off valves 2 and 3 are opened, thereby reducing the load on the vehicle engine related to the driving force of the compressor l. This provides sufficient vehicle engine power for acceleration.

(C) When the acceleration state ends In this mode (C), the first on-off valve 2 is closed and the second on-off valve 3 is opened for a certain period of time at a certain opening, for example, the opening of the station. It is said that As a result, when the acceleration state ends, the compression capacity of the pressure wall is partially restored and the cooling action is started.

The reason why the second on-off valve 3 is set to the glazed opening state is because various conditions for controlling the compressor l change when the acceleration state ends, and so-called prospective control is performed. This is for the purpose of

CD) When controlling in relation to the vehicle interior temperature, this aspect (I
)), the set temperature Ts in the vehicle interior and the actual temperature T in the vehicle interior.
The first and second on-off valves 2,
3, thereby obtaining the compression capacity of the compressor l in accordance with the required cooling capacity. Note that since the actual sensible temperature inside the vehicle is affected by environmental conditions inside and outside the vehicle interior, such as the amount of solar radiation Sr, the set temperature Ts is corrected based on these conditions.

The above temperature difference is the set temperature Ts inside the vehicle and the outside temperature To.
, solar radiation isr, and vehicle interior temperature Tr are respectively measured, and the data is read into the memory of the processing device 70. Then,
The set temperature Ts in the vehicle interior is corrected by the outside air temperature To and the amount of solar radiation Sr, and the corrected set temperature Ts is calculated and obtained. This temperature difference is controlled by dividing it into three values based on experimental or empirical values. That is, A very large value is set as a, the next value is set as b, and a value with little difference is set as C, and the capacity of the compression I!l is changed according to each temperature difference.In addition, the correction set temperature Ts' A case where the vehicle interior temperature Tr falls below is also defined as -d, and the capacity of the compressor 1 is also controlled by this value.

In this way, mode (D) is controlled further divided into the following states.

(D-1) In this case (D-1) when the corrected set temperature Ts' and the vehicle interior temperature are almost the same, -d≦T r -Ts'<
b (7) In this case, the opening degree of the second on-off valve 3 is subjected to so-called map control to perform relatively minute temperature control.

(D-2) When starting the compressor l, when the vehicle interior temperature Tr is higher than the corrected set temperature Ts by more than a predetermined temperature difference and lower than the temperature difference a for cooling down (b≦T
r −Ts'< a) In this mode (D-2), there is a relatively large temperature difference between the vehicle interior temperature Tr and the corrected set temperature Ts'', and it is necessary to lower the temperature in the vehicle interior in a short time. Therefore, at the beginning of startup, the compressor 1 exerts 100% compression capacity, and when the temperature drops, the opening of the second on-off valve 3 is slightly opened to relieve the rapid cooling state and prevent excessive cooling. Thereafter, if the temperature falls within the predetermined temperature range, the operation is performed in the same manner as in the above embodiment (D-1).

In this mode (D-2), since the temperature is optimally controlled according to the stage of the temperature difference, there is no excessive cooling compared to the conventional method, and the driving force of the compressor 1 is wasted. Not at all.

(D-3) At the start of compression #ll, when the vehicle interior temperature Tr is higher than the corrected set temperature Ts'' by a predetermined temperature difference a (a≦Tr −Ts') This mode (D-3) This is a case where the temperature difference between the vehicle interior temperature Tr and the corrected set temperature Ts' is very large, and the temperature is intentionally controlled to a rapid cooling state below the set temperature Ts. , the vehicle interior temperature Tr is high and the heat capacity is large, and by rapidly cooling it to below the set temperature Ts, that is, cooling it down, the temperature felt on the skin of the human body will feel comfortable and cool.

In this embodiment (D-3), when the temperature inside the vehicle is extremely high, such as on a midsummer day, the supercooling state is first set lower than the set temperature Ts, taking into consideration the skin sensation of the human body, and then the compressor is turned on. almost 100% capacity control. After that, the temperature rises and the system returns to normal cooling mode without putting any load on the engine.

(D-4) At the time of starting compression AL, when the vehicle interior temperature Tr is lower than the corrected set temperature Ts' by a predetermined temperature difference -d (Tr-Ts'<-d) This aspect (D-4) Now, let's start with the predetermined temperature difference -
Since it is lower than d, there is no need to operate compressor 1 and
0% capacity control. When the temperature rises, the second on-off valve 2 is operated to control the temperature by map control.

In this mode (D-0), when there is no need to perform air conditioning from the beginning, the compression 411 is almost 100% capacity controlled to prevent engine output from being wasted.

As described above, the first and second on-off valves 2.3 are appropriately controlled depending on the operating conditions of the vehicle engine, the environment inside and outside the vehicle, and the conditions set by the operator, thereby reducing the load on the engine as much as possible. Effective cooling effect can be achieved.

The above embodiment illustrates one embodiment of the present invention, and
Various design modifications can be made based on the basic technical idea of the present invention. The following embodiments are included within the technical scope of the present invention.

■ In each of the above embodiments, the first check valve 22 and the second check valve
Although a mode has been shown in which the check valves 23 and the check valves 23 are arranged in series, they may be arranged in parallel.

The compressor is not limited to the two-vane rotary compressor, but also includes other positive displacement 4m compressors (Rempro type, axial type, and radial type). is not limited to an on/off type or proportional control type solenoid valve, but may also be a frequency type solenoid valve.

(2) The first and second on-off valves 2 and 3 do not need to be electromagnetic valves, and diaphragm valves controlled by pressure can be used.

(2) Further, the number of vanes 5 in the compressor 1 does not have to be three as shown in the embodiment.

C1 Effects of the Invention As described above, according to the present invention, in a compressor in which a discharge port opening into a compression chamber is provided with a check valve that allows outflow from the discharge port to a discharge passage, the check valve is , a first check valve that allows a small flow rate to flow from the discharge port to the discharge passage when the pressure difference before and after the check valve becomes larger than a predetermined primary set pressure P1; a second check valve that allows a large flow rate to flow from the discharge port to the discharge passage when the difference is greater than the secondary set pressure P2, which is greater than the primary set pressure P1; Therefore, the residual volume can be reduced by the small passage of the first check valve, which is suitable for small flow rates, and for this reason, compressed gas is discharged to the discharge passage side when the compressor is operating at a small flow rate. This increases the amount of fuel that can be used, improving the efficiency of the compressor.

In addition, when the flow rate is large, the pressure difference between the discharge passage side and the compression chamber becomes large, and the large passage of the second check valve that reduces the residual volume as much as possible opens, so the discharge resistance can be reduced.
As a result, the efficiency of the compressor is improved even in this case without increasing the compression work.

[Brief explanation of drawings]

The drawings show an embodiment of the compressor of the present invention; Fig. 1 is a partially expanded vertical sectional view of one embodiment, Fig. 2 is a partially enlarged sectional view, and Fig. 3 is a discharge diagram of the main part. FIG. 4 is an enlarged sectional view of the main part of another embodiment, FIG. 5 is an enlarged sectional view of the main part of another embodiment, and FIG.
The figure is a control system diagram for water pressure mm.

Claims (1)

[Scope of Claims] 1) A compressor in which a discharge port opening into a compression chamber is provided with a check valve that allows outflow from the discharge port to a discharge passage, the check valve comprising: a first check valve that allows a small flow rate to flow from the discharge port to the discharge passage when the pressure difference before and after becomes larger than a predetermined primary set pressure P1; and a second check valve that allows a large flow rate to flow from the discharge port to the discharge passage when the secondary set pressure P2 is higher than the primary set pressure P1. Compressor features. 2) The second check valve includes a second spring member having a spring force k2 corresponding to the secondary set pressure P2, and a second valve body that elastically closes the discharge port with the second spring member. The first check valve is formed of a first spring member having a spring force k1 corresponding to the primary set pressure P1, and the second valve body so as to communicate with the discharge port. The compressor according to claim 1, further comprising a first valve body that elastically closes a valve hole by the first spring member. 3) The second check valve includes a second spring member having a spring force k2 corresponding to the secondary set pressure P2, and a second valve body that elastically closes the discharge port with the second spring member. The first check valve has a spring force k1 corresponding to the primary set pressure P1, and the valve hole formed in the second valve body so as to communicate with the discharge port has the spring force. k
1. The compressor according to claim 1, comprising a first valve body which is elastically closed by a first valve body.