JP2002371980A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce over-compressing work by using reflected waves of pressure waves generated by compressed fluid discharged from a discharging port for opening a discharging valve at its own discharging port, in a compressor. SOLUTION: Discharging path length Lr from a discharging port 22 to pressure-released a discharging path outlet end 50a is decided on the basis of pressure wave-form measured under a compressor operating condition. By reflected waves of discharging compressed waves at the outlet end 50a, opening valve pressure at discharging compressed fluid is lowered. A part of the discharging path 50 is structured by a pipe 47, the discharging path length Lrfit decided on the basis of the pressure wave-form measured under the compressor operating condition is embodied by adjusting the length of the pipe.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant compressor used as a part of a car air conditioner system, an engine heat pump system, and the like, and more particularly to a compressor for reducing overcompression loss of a fluid to be compressed used as a refrigerant. The present invention relates to a vane compressor with improved efficiency.

[0002]

2. Description of the Related Art Conventionally, a vane compressor has been known as a refrigerant compressor used in a car air conditioner system, an engine heat pump system and the like. In this vane compressor, a multi-cylinder, reed valve mechanism is provided at a discharge port of a compression portion. The reed valve (discharge valve) is configured to open only when the pressure in the compression chamber inside the valve becomes higher than the pressure in the high pressure chamber outside the valve. And, the backflow from the high pressure chamber side to the compression chamber side is prevented,
This prevents recompression of the fluid to be compressed and keeps the compression chamber airtight.

[0003]

However, in the conventional vane type compressor, the pressure in the compression chamber must be higher than the pressure in the high pressure chamber in order for the fluid to be compressed compressed in the compression chamber to be discharged by opening the reed valve. Need to be For this reason, the opening of the reed valve is delayed or the opening degree decreases with respect to the end of the compression process in the compression chamber, and the excessive compression work of the fluid to be compressed increases, thereby reducing the efficiency of the compressor. . The present invention reduces the excessive compression work by using a reflected wave of a pressure wave generated by a compressed fluid discharged from a discharge port in a compressor to open a discharge valve at its own discharge port. Make it possible.

[0004]

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described. That is, in claim 1, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on the rear end surface of the cylinder, a rotor is rotatably provided on the inner periphery of the cylinder, and a vane groove is formed in the rotor. In a compressor in which a vane is slidably mounted in a groove, a discharge port is provided in a cylinder, and a discharge valve is provided to open and close the discharge port, the discharge path length from the discharge port to the discharge path outlet end where pressure is released Based on the pressure waveform measured under the compressor operating conditions,
An appropriate discharge path length is determined, and the valve opening pressure at the time of discharging the compressed fluid is reduced by the reflected wave of the discharge compression wave at the outlet end.

According to a second aspect of the present invention, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on the rear end surface of the cylinder, a rotor is rotatably provided on the inner periphery of the cylinder, and a vane groove is formed in the rotor. In a compressor in which a vane is slidably mounted in a vane groove, a discharge port is provided in a cylinder, and a discharge valve for opening and closing the discharge port is provided, an outlet in which a discharge path of a fluid to be compressed is formed from the discharge port to a side block. Composed of a unique path to the outlet end of the hole and an additional path having a pressure-released outlet end, measuring a pressure waveform under compressor operating conditions of the compressor using only the unique path, and calculating the pressure waveform from the pressure waveform. Calculate the time for the discharge pressure wave to reciprocate on the specific path to determine the specific path length, and derive the optimal timing position at which the reflected wave of the discharge pressure wave propagates to the discharge valve at the opening timing of the discharge valve. An appropriate discharge path length is determined based on the propagation speed of the pressure wave determined by the imaging position and the compressor operating conditions, and an appropriate additional path length is determined from an appropriate discharge path length and an appropriate proper path length. .

In a third aspect, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on the rear end surface of the cylinder, a rotor is rotatably provided on the inner periphery of the cylinder, and a vane groove is formed in the rotor. In a compressor in which a vane is slidably mounted in a vane groove, a discharge port is provided in a cylinder, and a discharge valve that opens and closes the discharge port is provided, the discharge path from the discharge port to the discharge path outlet end where the pressure is released is It consists of a tubular part and a volume part, measures the pressure waveform under the compressor operating conditions, and derives the optimal timing position where the reflected wave of the discharge pressure wave propagates to the discharge valve at the opening timing of the discharge valve from the pressure waveform. Then, an appropriate discharge path length is determined from the propagation speed of the pressure wave determined by the optimal timing position and the compressor operating conditions, and an appropriate pipe path length of the tubular portion is determined using a relational expression of an equivalent required length. Decide Those were.

According to a fourth aspect of the present invention, in the pressure waveform,
The pressure waveform of the discharge port pressure is a theoretical waveform of adiabatic change instead of the measured pressure waveform.

According to a fifth aspect of the present invention, a part of the discharge path is constituted by a pipe, and the appropriate discharge path length is adjusted by adjusting a pipe length.

According to a sixth aspect of the present invention, a lubricating oil removing section for removing the compressor lubricating oil from the fluid to be compressed is provided in the discharge path, and a path hole is formed in the lubricating oil removing section. This was performed by adjusting the length of the path hole.

According to a seventh aspect of the present invention, a discharge path is provided with a lubricating oil removing section for removing the compressor lubricating oil from the fluid to be compressed, and a path groove is formed in the lubricating oil removing section. This was carried out by adjusting the length of the path groove.

According to the present invention, a lubricating oil removing section and a spacer for removing the lubricating oil for the compressor from the fluid to be compressed are provided in the discharge path, and the discharge path is formed in the lubricating oil removing section and the spacer. The above-described appropriate discharge path length is obtained by adjusting the number of spacers.

In a ninth aspect, a plurality of discharge ports are provided,
A compressed fluid outlet hole is provided in the side block for each discharge port, a discharge path is provided from each discharge port through each outlet hole, and a pressure is released at each discharge path outlet end. In this configuration, a path connecting one discharge port and at least one other discharge port is cut off.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First, a vane type compressor 10 according to a first embodiment will be described with reference to FIGS. FIG.
1 is a side sectional view in the axial direction of the rotor showing the vane type compressor of the first embodiment, FIG. 2 is a plane sectional view in the axial direction of the rotor showing the vane type compressor of the first embodiment, and FIG. A-A
It is a line sectional view. Note that the left side of FIGS. 1 and 2 is the front side of the compressor. The vane compressor 10 houses the cylinder 1 inside a cylinder housing case 11, and the inner peripheral surface of the cylinder 1 is formed in a substantially elliptical shape. Side blocks 2 and 3 are provided on a front end face and a rear end face of the cylinder 1. A rotor 4 is rotatably provided inside the cylinder 1, and the rotor 4 is fixed to a rotor shaft 5. Bosses 6 and 7 are formed in the side blocks 2 and 3 along the direction in which the rotor shaft 5 extends, and the rotor shaft 5 is rotatably supported by the bosses 6 and 7. ing. A plurality of vane grooves 8.8 are formed from the outer peripheral side of the rotor 4 toward the vicinity of the rotor shaft 5, and the vanes 9.9 slide in the vane grooves 8.8, respectively. It is freely attached.

As shown in FIGS. 1 and 3, the inner peripheral side of the cylinder 1 has an inner wall of the cylinder 1, inner surfaces of side blocks 2, 3,
The outer peripheral surface of the rotor 4 and the vanes 9 are partitioned into a plurality of small chambers. The small chamber is called a compression chamber 15, and the rotor 4
The volume changes repeatedly due to the rotation of. As the rotor 4 rotates, a circulation process in which the three steps of suction, compression, and discharge constitute one cycle is repeatedly performed in each compression chamber 15. A front housing 16 is fixed to the side block 2 on the side opposite to the rotor 4. A suction chamber 13 is formed in the front housing 16. Further, a suction port 21 communicating with the suction chamber 13 is formed in the cylinder 1 and the side block 2. Compression chamber 1
In the suction process of No. 5, the suction port 21 formed in the cylinder 1
And the compression chamber 15 are communicated with each other, and a suction of a fluid to be compressed such as a refrigerant gas from the suction chamber 13 into the compression chamber 15 is performed. At the same time, in the compression step of the compression chamber 15, the fluid to be compressed is compressed in the compression chamber 15.

A position where the volume of the compression chamber 15 is near the minimum;
That is, the compression chamber 15 and the high pressure chamber (discharge chamber) 2 on the outer peripheral surface side of the cylinder 1
A discharge port 22 communicating with the fourth side is provided. As shown in FIG. 3, the discharge ports 22 are located on the circumference of the cylinder 1.
It is formed at a position substantially symmetrical with respect to the center axis of the cylinder 1. The discharge valve 23 is attached to an opening end of the discharge port 22 on the high-pressure chamber 24 side, and the discharge valve 23 prevents backflow of the fluid to be compressed from the high-pressure chamber 24 side to the compression chamber 15 side. The discharge valve 23 opens only when the pressure of the fluid to be compressed in the compression chamber 15 becomes higher than the pressure of the fluid to be compressed in the high-pressure chamber 24, and otherwise closes and closes from the high-pressure chamber 24 to the compression chamber 15 side. Backflow to prevent recompression of the fluid to be compressed. When the discharge valve 23 is closed as described above, the compression chamber 15 and the high-pressure chamber 24 are kept airtight by the surface around the discharge port 22 that contacts the discharge valve 23. In addition,
The opening of the discharge valve 23 is limited to a predetermined opening by the valve support 27.

In the side block 3 on the rear end side of the cylinder 1, an outlet hole 25 for the fluid to be compressed is provided for each discharge port 22. Further, in the vane type compressor 10 of the first embodiment, pipes 47
Is provided. The outlet hole 25 and the pipe 47 are connected so as to communicate with each other, and a discharge path 50 extending from the discharge port 22 to the outlet end of the pipe 47 (the end in the discharge direction) is formed. When the discharge valve 23 opens, the fluid to be compressed in the compression chamber 15 passes through the discharge port 22 and is discharged to the high-pressure chamber 24 side, and further passes through the outlet hole 25 and the pipe 47, and Is discharged. Exit end 50a of discharge path 50
At the outlet end of the pipe 47, the fluid to be compressed
4 is configured to be discharged into an open space. Therefore, the pressure of the fluid to be compressed is released at the outlet end of the discharge path 50.

The volume of the compression chamber 15 is reduced,
When the pressure in 5 becomes higher than the pressure in high-pressure chamber 24, discharge valve 23 opens. Here, when the compressed fluid is discharged from the discharge valve 23, a pressure wave is generated. The pressure wave is
The fluid to be compressed propagates before flowing out of the chamber 14 through the high-pressure chamber 24. The pressure wave is a high-pressure wave with respect to the pressure in the chamber 14, and exerts an action of compressing the compressed fluid as a medium to be compressed.
A pressure wave of a high pressure with respect to the pressure in the chamber 14 is
Hereinafter, a compression wave is used. On the other hand, a reflected wave of the pressure wave reflected at the open end where the pressure is released is defined as an expansion wave. The expansion wave is a low-pressure wave with respect to the pressure in the chamber 14, and exerts an action of expanding the compressed fluid as a medium to be compressed. In the vane compressor 10 of the first embodiment, since the outlet end of the pipe 47 is the open end where the pressure is released, the compression wave is reflected at the outlet end at the free end and changes to an expansion wave. FIG. 2 shows a compression wave 4 generated at one discharge port 22.
8 shows a state in which the free end 8 is reflected at the outlet end 50a and changes into an expansion wave 49, and the expansion wave 49 propagates to the discharge valve 23 of the discharge port 22.

In the present invention, the valve opening pressure at the time of discharging the fluid to be compressed (opening timing of the discharge valve 23) is reduced by utilizing the expansion wave generated by the discharge compression wave reflected at the outlet end. Like that. Here, the expansion wave to be used is an expansion wave generated by the free end reflection of the compression wave generated at the discharge port 22 at the outlet end 50a in the discharge step of the previous cycle. At this time, it takes time for these waves to reciprocate in the discharge path 50 before the compression wave generated inside the discharge valve 23 (discharge port 22) is changed to an expansion wave and propagates to the discharge valve 23. It is. The propagation speed of the compression wave and that of the expansion wave are the same. That is, the discharge is adjusted by adjusting the timing at the start of the discharge process of a certain cycle, that is, at the opening timing of the discharge valve 23 so that the compression wave generated in the cycle before the cycle turns into an expansion wave and just returns. That is, the valve opening pressure of the valve 23 is reduced.
Since the pressure of the fluid to be compressed filling the high-pressure chamber 24 is reduced by the expansion wave returned to the discharge valve 23, the valve opening pressure required to open the discharge valve 23 is reduced. When the valve opening pressure decreases at the time of opening the valve, excessive compression work for discharging the fluid to be compressed from the discharge valve 23 by the rotor 4 is reduced.
In the above description, a certain cycle is targeted at a cycle before the cycle, but this is the same as the compression chamber 15.
It does not refer to the cycle in. Compression chamber 15.1
Are formed by the vanes 9, 9,..., But as the rotor 4 rotates, the compression chambers 15, one after another in the discharge process, approach the discharge port 22. Therefore, here, at a certain discharge port 22, a certain compression chamber 15
The cycle of the compression chamber 15 that has reached the discharge port 22 immediately before this cycle is referred to as the previous cycle.

The propagation timing of the expansion wave is determined by the length of the discharge path 50. For this reason, in the first to third methods for determining the length of the discharge path described below, the outlet end 22 of the discharge path 50 whose pressure has been released from the discharge port 22.
The length of the discharge path up to 0a is determined based on the pressure waveform measured under the compressor operating conditions, and the expansion wave as the reflected wave reduces the valve opening pressure at the time of discharging the fluid to be compressed. That is, by setting the discharge path length of the discharge path 50 to an appropriate length, the propagation timing of the expansion wave coincides with the valve opening timing of the discharge valve 23, and the discharge valve 23
The valve opening pressure is reduced. The first to third methods for determining an appropriate discharge path length (additional path length) based on a pressure waveform measured under compressor operating conditions will be described later.

In the vane type compressor 10 of the first embodiment, a part of the discharge path 50 is constituted by a pipe 47. Therefore, just using pipes with different pipe lengths,
The length of the discharge path of the discharge path 50 can be changed. Therefore, the appropriate discharge path length, in which the propagation timing of the expansion wave coincides with the valve opening timing of the discharge valve 23,
It can be easily realized. Further, the shape of the discharge path is not limited to a straight path, but may be a configuration in which a bent portion or a curved portion is provided. The above-described effect of reducing the valve opening pressure of the discharge valve 23 depends on the length of the discharge path,
This is because there is almost no relation to the path shape of the above. In the vane compressor 10, the pipe 47 has a configuration in which an end is bent so that the pipe 47 can be accommodated in the cylinder storage case 11. That is, the length of the discharge path of the discharge path 50 can be freely adjusted by using the pipe regardless of the volume of the cylinder storage case 11.

The vane type compressor 10 has two discharge ports 2
2.22 are provided. Then, one discharge port 22
And the other discharge ports 22 are formed with communication paths 30. In the present invention, the communication paths 30 are configured to be shut off in order to prevent the pressure waves from the other discharge ports 22 from propagating and interfering with one discharge port 22. In the vane type compressor 10, the outer peripheral surface of the cylinder 1 and the inner peripheral surface of the casing 11 are not in close contact with each other, and communication paths 30 are formed therebetween. And, between the high pressure chambers 24, the communication path 30
30 via one of the outlets 22
22 are in communication. In order to cut off the communication path 30,
Seals 31 are provided in the communication paths 30. The seal 31 has a groove on the outer surface of the cylinder 1,
It is mounted in the groove. The seal 31 is inserted into the groove.
By mounting the seal, the positioning of the seal 31 can be easily performed, and the movement of the seal 31 during operation of the compressor can be prevented. As described above, the seal structure is configured by the seal 31, and the one discharge port 22 is replaced with the other discharge port 22.
The communication path 30 that communicates with the communication path is blocked.

The effect of reducing the valve opening pressure of the discharge valve 23 by using the expansion wave is to release the pressure at the outlet end so that the discharge timing is adjusted so that the valve opening timing matches the propagation timing of the expansion wave. This can be realized if a discharge path having a path length is provided, regardless of the number of discharge ports provided. For example, even in the case of a compressor in which the number of vanes provided is smaller than that of the vane-type compressor 10 and the cylinder is provided with only one discharge port, if the discharge path having the above-described configuration is provided, There is an action (decrease in valve opening pressure at the time of discharge). In this case, since there is only one discharge port, pressure wave interference does not occur between discharge ports in the first place.

Alternatively, even in a compressor having three or more discharge ports, the above-described operation (reduction of the valve opening pressure at the time of discharge) can be achieved if the following structure is adopted. The compressor includes a discharge path having the above-described configuration, and a plurality (for example, three) of the discharge paths.
Of these discharge ports, the path connecting one discharge port and at least one other discharge port is cut off. Here, since the purpose is to prevent pressure waves from propagating from other discharge ports and causing pressure wave interference at the time of discharge at one discharge port, communication paths between all discharge ports are necessarily cut off. There is no need to do it. The pressure wave interference that is a problem here is pressure wave interference that occurs when a compression wave propagates from one of the discharge ports to one of the discharge ports at the opening timing of one of the discharge ports. Therefore, at each discharge port, only the communication path with the discharge port that allows the compression wave to propagate just at the valve opening timing has to be blocked. The case where three or more discharge ports are formed in a cylinder refers to, for example, a case in which a plurality of cylinders are connected along a rotor shaft to form a vane-type compressor having another configuration. In this case, two discharge ports are provided on the circumference of each cylinder, and the number of discharge ports is twice the number of cylinders provided in the entire compressor. Also in this case, the communication path formed between the discharge ports is cut off to prevent the compression wave from propagating from another discharge port to one discharge port.

As described above, when two discharge ports 22 are provided as in the vane type compressor 10,
In the case of a compressor having two or more discharge ports, the valve opening pressure is increased at the time of discharge by blocking a path connecting one discharge port and at least one other discharge port among a plurality of discharge ports. This prevents pressure wave interference from occurring. Then, the valve opening pressure at the time of discharge increases due to the pressure wave from the other discharge port, thereby preventing the opening of the discharge valve from being obstructed and increasing the compression work. Further, if the discharge path is configured such that the outlet end is pressure-released and the discharge path length is such that the valve opening timing and the propagation timing of the expansion wave are matched, excessive discharge by the rotor 4 for opening the discharge valve. The reduction of the compression work is also performed at the same time.

As described above, in order to reduce the valve opening pressure when the discharge valve 23 is opened (valve opening timing), it is necessary to match the valve opening timing with the propagation timing of the expansion wave. The propagation timing of the expansion wave changes depending on the length of the ejection path of the ejection path 50. The longer the ejection path length, the more the propagation timing is delayed. In the present invention, the length of the discharge path is appropriately determined so that the two timings coincide with each other, and the discharge path 50 having the length of the discharge path is formed. It lowers. When the valve opening pressure at the time of discharge decreases, excessive compression work for opening the discharge valve 23 by the rotor 4 is reduced.

The discharge path 50 extends from the discharge port 22 to the outlet hole 2.
5, a path in the high-pressure chamber 24 to the inlet end (the end on the rotor 4 side), a path in the outlet hole 25, and a path in the pipe 47. In the vane-type compressor 10 of the first embodiment, the pipe 47 is a part of the discharge path (an additional path described later). A path formed by holes, grooves, or the like provided in the removing section may be used, and any configuration may be used as long as the configuration maintains air-tightness and liquid-tightness to the outlet end 50a of the discharge path 50.

The length of the discharge path 50 from the discharge port 22 to the inlet end of the outlet hole 25 is determined by the shapes and dimensions of the cylinder 1 and the cylinder housing case 11. The length of the path in the outlet hole 25 of the discharge path 50 is determined by the shape and size of the side block 3. The length of the discharge path 50 in the pipe 47 is determined by the length of the pipe 47. Therefore, in order to change the length of the discharge path, at least one of the three path lengths described above may be changed. Here, a path from the discharge port 22 to the entrance end of the exit hole 25,
The path combining the path inside the exit hole 25 is called a unique path. Further, a path obtained by removing the specific path from the discharge path is referred to as an additional path. In the first embodiment, the additional path is a pipe 47.
Corresponds to the path formed by In the first to fourth embodiments, the length of the discharge path is changed by adjusting the length of the additional path. Adjustment of the length of the additional path is one means of changing the length of the discharge path as described above, and the present invention is not limited to this means. For example, the length of the discharge path may be adjusted by changing the path length (length in the discharge direction) of the outlet hole formed inside the side block. Specifically, a plurality of side blocks having different exit hole path lengths are prepared, and the discharge path length is changed by replacing the side blocks.

Next, a method for determining the discharge path length of the discharge path 50 based on the pressure waveform measured under the compressor operating conditions will be described. The vane-type compressor is driven under predetermined operating conditions when constituting a part of an air conditioner or the like and actually using it. Compressor operating conditions include:
The number of rotations of the rotor shaft 5, the type of fluid to be compressed (refrigerant),
There are pressure and temperature of the fluid to be compressed at the time of suction and discharge.
In addition, as an element unique to each vane type compressor,
There are the shape and size of each member constituting the compressor, the number of vanes provided on the rotor, the number of discharge ports, and the like. The basic performance of the compressor is determined by these inherent elements. Therefore,
The basic performance of the compressor determined by the specific element,
The performance (working efficiency) exhibited when the compressor is driven varies depending on the compressor operating conditions.

In the first to third methods for determining the length of the discharge path, first, a target vane-type compressor is specified, and it is considered appropriate for each compressor operating condition when the compressor is actually driven. The length of the discharge path (or the length of the additional path) is determined, and the valve opening timing is matched with the propagation timing of the expansion wave, so that the valve opening pressure at the time of discharge is reduced. The ejection path length that is appropriate is more specifically,
Based on the pressure waveform measured under the compressor operating conditions, it is calculated (determined) according to first to third determination methods described later. Even in the vane type compressor having the same configuration (the above-described specific element), since the measured pressure waveform changes when the operating condition of the compressor is changed, the pressure waveform is measured for each operating condition of the compressor. , An appropriate ejection path length (an additional path length described later) is determined.

A first method of determining an appropriate discharge path length (additional path length) will be described with reference to FIGS. FIG. 4 is a schematic diagram showing the configuration of the ejection path, and is a flowchart showing a first method of determining an appropriate ejection path length. As shown in FIG. 4A, the discharge path length Lr of the discharge path is configured by combining the specific path length L0 of the specific path and the additional path length L of the additional path. Among the discharge paths, the discharge path having the appropriate discharge path length Lrfit is, for example, the discharge path 50 provided with the pipe 47.
The vane-type compressors of the second to fourth embodiments to be described later are provided with discharge paths having a configuration different from that of the pipe 47, and the discharge path lengths of these discharge paths are also the appropriate discharge path lengths described above. The first decision method is roughly divided into the following three steps. In the first stage, the eigenpath length L0 is determined. In the second stage, an appropriate ejection path length Lrfit is determined.
In the third stage, using the results of the first and second stages,
The additional path length Lfit is determined.

Incidentally, as will be described in detail when a second determination method described later is described, the path length of the compression chamber 15 is corrected based on the path length of the tubular portion including the pipe 47 and the outlet hole 25. It will include the quantity. That is, the unique path length L
0 and ejection path length Lr, appropriate ejection path length Lrf
It is the path length to which the correction amount is added.
Therefore, in FIG. 4 as well, the path length of the specific path length L0 does not coincide with the left and right width of the compression chamber 15 and the outlet hole 25 but is shifted.

First, as shown in FIG. 4 (b), a pressure waveform is measured in a state in which the compressor has no additional path, and the discharge path has only a proper path (step 101). The amount of rotation of the rotor 4 from the discharge compression wave maximum generation timing Tb to the compression wave propagation timing Tc is measured as a rotor angle change amount A. From the measured rotor angle change amount A (described later), an elapsed time from the discharge compression wave maximum generation timing Tb to the compression wave propagation timing Tc is calculated. (Step 102). Then, based on the difference between the two timings, the unique path length L0 is determined using Expression (3) described later (Step 103). As will be described in detail later, the characteristic path length L0 (in this case, also the discharge path length) is calculated by measuring the rotor angle change amount A.
An example of the pressure waveform measured in the state of only the unique path is the pressure waveform shown in FIG. Next, the position of the optimum timing Tfit when an appropriate discharge path is provided is derived (predicted) by referring to the pressure waveform in the case of only the unique path (step 104). Then, by deriving the position of the optimal timing Tfit, the optimal timing Tfit is derived from the maximum timing Tb of the discharge compression wave.
The amount of rotation of the rotor 4 by the time fit is measured as the rotor angle change amount B. As will be described in detail later, when the discharge is performed at the optimal timing Tfit, the valve opening pressure is reduced to the maximum, so that the compression work by the rotor 4 is reduced. Then, the elapsed time from the discharge compression wave maximum occurrence timing Tb to the optimum timing Tfit is calculated by substituting the measured rotor angle change amount B into the expression (8) described later (step 105). Further, an appropriate ejection path length Lrfit shown in FIG. 4C is calculated by using the following equation (7) (step 106). Then, by subtracting the inherent path length L0 from the appropriate discharge path length Lrfit, an appropriate additional path length Lfit is determined (step 107). Also, by the subtraction,
The influence of the correction amount of the inherent path length L0 described above is also eliminated.

The pressure waveform to be measured is a pressure waveform indicating the relationship between time (rotor 4 angle) and pressure in each of the pressure in the discharge port, the pressure after the discharge valve, and the pressure in the case. The pressure in the discharge port is the pressure in the discharge port 22. A pressure sensor (not shown) is provided in the cylinder 1 so that the detection unit of the sensor can come into contact with the fluid to be compressed in the discharge port 22, and the pressure in the discharge port is measured at a measurement position as shown in FIG. The post-discharge valve pressure refers to the pressure on the side opposite to the discharge port 22 of the discharge valve 23. Similarly, a pressure sensor (not shown) is provided on the cylinder 1 or the cylinder housing case 11 so that the detection unit of the sensor can come into contact with the fluid to be compressed in the high-pressure chamber 24, and discharges at a measurement position as shown in FIG. Measure post-valve pressure. The opening of the discharge valve 23 occurs when the pressure in the discharge port becomes higher than the pressure after the discharge valve. The pressure in the case is the same as the cylinder storage case 11.
Inside, that is, the pressure of the chamber 14. As described above, the pressure in the case is, as described above, whether the pressure wave generated inside the vane compressor is a compression wave or an expansion wave, that is, whether the pressure wave is on the pressurizing side of the valve opening pressure of the discharge valve 23 or on the pressure reducing side. It is used as a criterion for determining A pressure sensor (not shown) is provided in the cylinder housing case 11 so that the detection unit of the sensor can come into contact with the fluid to be compressed in the chamber 14, and the pressure in the case is measured at a measurement position as shown in FIG.

The pressure waveforms of the respective pressures in the compressor in which the discharge path is constituted only by the unique path will be described with reference to FIG. FIG. 6 is a view showing pressure waveforms of the respective pressures in the compressor in which the discharge path is constituted only by the unique path. In FIG. 6, the horizontal axis represents the angle of the rotor 4 and the vertical axis represents the magnitude of the pressure. The amount of change in the rotor angle corresponds to the amount of change in time. The elapsed time per one rotation of the rotor 4 can be calculated from the operating rotation speed (the number of rotations per minute) of the rotor shaft 5. Since one rotation of the rotor 4 is 360 °, the time required for the rotor 4 to change by 1 ° is also calculated. In the vane type compressor 10, five vanes 9 are provided, and every time the rotor 4 rotates by 72 ° (360/5), the fluid to be compressed is discharged from the compression chambers 15, 15,. The pressure waveforms of the discharge port pressure, the discharge valve pressure, and the case pressure shown in FIG. 6 are all periodically changed every 72 ° of the rotor rotation angle under a fixed compressor operating condition. I have.

When the rotor 4 rotates, the post-discharge valve pressure temporarily drops below the case internal pressure and reaches a minimum value as the rotor 4 rotates. Thereafter, it rises and reaches the maximum again, during which a peak having a maximum value is formed. The peak is lower than the peak having the maximum value. Here, the time when the pressure after the discharge valve becomes the maximum value is defined as the discharge compression wave maximum generation timing Tb (s).
The formation of the peak at which the pressure after the discharge valve reaches a maximum value (and a maximum value) indicates a state in which the discharge valve 23 is opened and a compression wave is generated. The pressure in the discharge port also has a maximum value near the angle at which the pressure after the discharge valve becomes a maximum value. That is, the vicinity of the angle at which the peak is formed is immediately after the discharge valve 23 is opened. Next, the formation of the valley at which the pressure after the discharge valve becomes the minimum value (and the minimum value) is that the compression wave is reflected at the outlet end of the discharge path via the discharge path, and propagates to the discharge valve 23 as the expansion wave. This shows a situation where the pressure after the discharge valve is reduced. That is, while the rotor 4 rotates from the maximum value to the minimum value of the pressure after the discharge valve, the pressure wave (compression wave and the expansion wave generated by reflection of the compression wave) reciprocates in the discharge path. . Here, the time when the pressure after the discharge valve becomes the minimum value is defined as the expansion wave maximum propagation timing Te (s). Next, the formation of the peak where the pressure after the discharge valve reaches a maximum value is that the expansion wave is reflected at the outlet end 50a via the discharge path 50, and then propagates as a compression wave to the discharge valve 23. This shows a situation where the rear pressure is increasing. As described above, at the outlet end where the pressure is released, the compression wave changes to an expansion wave, and the expansion wave changes to a compression wave. That is, the compression wave generated at the discharge port 22 is reflected twice at the outlet end of the discharge path, and finally becomes a compression wave and propagates to the discharge valve 23. Here, the time at which the pressure after the discharge valve reaches the maximum value is defined as the compression wave maximum propagation timing Tc (s). Thereafter, the discharge is performed by the next compression chamber 15 described above, and the pressure after the discharge valve becomes the maximum value again.

As described above, the discharge path length Lr of the discharge path
Is obtained as follows. The pressure wave reciprocates twice on the discharge path during the time period from the maximum discharge compression wave generation timing Tb to the maximum compression wave propagation timing Tc. That is, the pressure wave propagates the distance of the discharge path × 4. Assuming that the propagation speed of the pressure wave is vs and the length of the discharge path is Lr, Tb (s), Tc
(1) between (s), Lr (m) and vs (m / s)
The relationship of the formula is established.

[0037]

(Equation 1)

The pressure wave propagation velocity vs. is calculated by measuring the type of the compressed fluid determined under the compressor operating conditions and the temperature and pressure of the compressed fluid at the time of discharge. The speed of sound. The propagation speed of a pressure wave in a medium depends only on the type of the medium and the temperature and pressure of the medium. As described above, the compression wave and the expansion wave have the same sound speed.

The discharge path length Lr and the intrinsic path length L
0 and the additional path length L, as described above, (2)
The relationship shown in the equation holds. In the pressure waveform shown in FIG. 6, in order to calculate the eigenpath length L0 of the eigenpath, FIG.
As shown in (b), the configuration is such that no additional path is provided. Therefore, in this case, the additional path length L = 0.
When the equation (1) is modified using the equation (2) and L = 0, the relation of the equation (3) is established.

[0040]

(Equation 2)

In FIG. 6, the time that elapses from the discharge compression wave maximum generation timing Tb to the compression wave maximum propagation timing Tc corresponds to the time when the rotor 4 rotates and the angle change amount A becomes. Assuming that the operating rotation speed of the rotor shaft 5 is N (rpm), the rotor 4 rotates N / 60 times per second. One rotation of the rotor 4 is a 360-degree change in angle. That is, the angle change amount of the rotor 4 in one second is 36
0 × (N / 60). Therefore, A (deg),
Between Tb (s), Tc (s) and N / 60 (1 / s), the relations of equations (4) and (5) hold. (5)
The equation is obtained by modifying the equation (4). The elapsed time (left side) is obtained by calculating the angle change amount A of the rotor 4 and the rotor 4
Is equal to the product of the elapsed time per 1 ° of rotation (right side).

[0042]

(Equation 3)

As described above, the elapsed time between the two timings is calculated by measuring the amount of change in the rotor angle between the two timings.

Here, in calculating the eigenpath length L0, the calculation is performed using the maximum compression wave propagation timing Tc. As described above, while the time elapses from the maximum discharge compression wave generation timing Tb to the maximum expansion wave propagation timing Te, the pressure wave reciprocates once in the discharge path. Even using this relationship, it is possible to calculate the unique path length L0. In the pressure waveform shown in FIG. 6, the valley formed near the expansion wave maximum propagation timing Te has a gentler slope than the peak formed near the compression wave maximum propagation timing Tc. That is, it is more difficult to specify the minimum value of the valley (the minimum value of the pressure wave) than to specify the maximum value of the peak. Therefore, in this embodiment,
The eigenpath length L0 is calculated according to the equation (1) using the compression wave maximum propagation timing Tc. When the pressure waveform changes from that shown in FIG. 6 by changing the compressor operating conditions, the expansion wave maximum propagation timing Te becomes easier to specify than the compression wave maximum propagation timing Tc. Is the expansion wave maximum propagation timing Te
Is used to calculate the unique path length L0. In this case, the relationship of equation (6) is established. The number 2 appearing in the denominator in the equation (6) is a number meaning one round trip of the eigenpath (eigenpath × 2). When the expansion wave maximum propagation timing Te is used, the pressure wave only makes one round trip on the eigenpath.

[0045]

(Equation 4)

The opening of the discharge valve 23 occurs when the pressure in the discharge port coincides with the pressure after the discharge valve or rises above the pressure after the discharge valve, as described above. As shown in FIG. 6, the pressure in the discharge port is higher than the pressure after the discharge valve, and the valve is in the open state at the center in the left and right directions. On both sides of the drawing, the pressure in the discharge port is lower than the pressure after the discharge valve except for a part, and the valve is in a substantially closed state. Here, over time,
The timing at which the post-discharge valve pressure rises and the two pressures match is referred to as a valve opening timing TO, and the timing at which the post-discharge valve pressure drops and the two pressures match is a valve closing timing TS. As described above, the pressure waveform shown in FIG. 6 is a waveform when no additional path is provided, and the expansion wave propagation timing does not usually coincide with the valve opening timing. FIG.
Thus, at the valve opening timing, the compression wave is propagating to the discharge valve 23, the valve opening pressure of the discharge valve 23 is increased, and the working efficiency of the compressor is reduced. Therefore, in the present invention, the length of the discharge path is adjusted by providing an additional path,
A discharge path having an appropriate discharge path length is formed so that both timings coincide, and the valve opening pressure of the discharge valve 23 is reduced.

When a discharge path having an appropriate discharge path length is formed, the pressure in the discharge port coincides with the post-discharge valve pressure at the maximum expansion wave propagation timing at which the post-discharge valve pressure is minimized. When the additional path is provided, the cycle of the pressure change of the post-discharge valve pressure is smaller than the case where only the specific path shown in FIG. 6 is used.
become longer. As the cycle becomes longer, the position of the minimum value of the post-discharge valve pressure (rotor angle) also shifts toward the valve opening timing TO. When the additional path having an appropriate discharge path length is provided, the pressure after the discharge valve, which is the minimum value, and the pressure in the discharge port can be matched. The timing at which the expansion wave maximum propagation timing matches the valve opening timing as described above is determined as the optimum timing Tfi.
Let it be t. As shown in FIG. 6, the optimum timing Tfit is obtained by drawing a horizontal line (a constant pressure graph) at a pressure at which the pressure after the discharge valve becomes a minimum value and specifying a timing at which the horizontal line and the pressure in the discharge port match. Derived. In the present embodiment, for example, the formation of the appropriate discharge path described above
This is performed by adding an additional route such as Assuming that the appropriate additional path length is Lfit, Lfit (m), Tb
(S), Tfit (s) and vs (m / s)
Equation (7) holds. Expression (7) is obtained by changing the expansion wave maximum propagation timing from Te to Tfit in Expression (6), and substituting the ejection path length by adding the additional path length Lfit to the specific path length L0. is there.

[0048]

(Equation 5)

In FIG. 6, the time elapsed from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit corresponds to the time when the angle change amount of the rotor 4 becomes B. When Tfit, which is the optimal timing, is substituted for Tc in equation (5), and B ° is substituted for A °, the relationship of equation (8) is established. As described above, the elapsed time between both timings is calculated by measuring the rotor rotation angle B between the two timings.

[0050]

(Equation 6)

In the first determining method, the influence of the opening end correction on the ejection path length is processed as follows.
As described above, the appropriate additional ejection path length Lfit is
It is calculated by subtracting the unique path length L0 from the appropriate discharge path length Lrfit. Therefore, the influence of the opening end correction can be removed at the time of the subtraction. In order to perform such removal, the following premise is required. That is, it is assumed that the correction amount of the opening end correction when the additional path is provided and the correction amount of the opening end correction when only the unique path is excluded without the additional path are the same. The correction amount of the opening end correction changes depending on the shape and the sectional area of the outlet end of the discharge path. Therefore, the exit end of the specific path, that is, the exit hole 25 formed in the side block 3
If the shape and cross-sectional area of the outlet end are different between the outlet end of the discharge path and the outlet end of the discharge path provided with an additional path such as a pipe, the amount of correction of the open end correction differs between the two cases. For this reason, in the present embodiment, the shape and cross-sectional area of the outlet end of the unique path (the outlet end of the outlet hole 25) and the outlet end of the additional path (in the first embodiment, the outlet end of the pipe 47) are different. By making them coincide, the correction amount of the opening end correction is the same in both cases.

As described above, from the equations (6) and (7),
An appropriate additional path length Lfit is determined. Then, an additional path having an appropriate additional path length Lfit is connected to the pipe 47.
Is the vane type compressor 10 of the first embodiment.
It is. Also, in the above, by measuring the pressure waveform using a compressor having only a unique path and calculating the unique path length,
Although an appropriate additional path length is determined, the present invention is not limited to this method. The pressure waveform of a compressor having an additional path having a fixed length in the specific path is measured, and an appropriate additional path is determined based on the discharge path length of the compressor (specific path length + constant additional path length). The length may be determined.

Next, the reduction of the compression work in the vane compressor 10 of the first embodiment, in which the length of the discharge path is determined by the first determination method and a part of the discharge path is constituted by the pipe 47, will be described. This will be described with reference to FIGS. FIG. 7 is a diagram illustrating a relationship between a rotor angle, a pressure, and a lift ratio in a compressor in which a discharge path is configured only with a unique path and in a compressor in which an appropriate additional path is provided in the specific path to configure a discharge path. FIG. 8 shows the relationship between the volume of the compression chamber and the pressure in the discharge port in the compressor in which the discharge path is configured only with the unique path and the compressor in which the discharge path is configured by providing an appropriate additional path in the specific path. FIG. In FIG. 7A, each pressure waveform of the compressor in which the discharge path is constituted only by the unique path is shown by a thin line, and the vane of the first embodiment in which the discharge path is constituted by adding an appropriate additional path to the unique path. The pressure waveform of the compressor 10 is shown by a bold line. The pressure waveform when only the eigenpath is
This is the same as the pressure waveform shown in FIG. When the discharge path is constituted only by the unique path, at the valve opening timing TO, the pressure after the discharge valve is higher than the pressure in the case, and the discharge valve 2
The valve opening pressure of No. 3 has been increased. On the other hand, in the first embodiment in which the discharge path is configured by adding an appropriate additional path, the portion where the pressure after the discharge valve becomes minimum is shifted to the right side in the figure. That is, the expansion wave propagates to the maximum during discharge, and the above-described valve opening timing and the expansion wave propagation timing match. Then, at the optimum timing Tfit where the two timings coincide, the pressure after the discharge valve becomes lower than the pressure in the case, and the valve opening pressure decreases. By setting the length of the discharge path to an appropriate length so that the valve opening timing and the propagation timing of the expansion wave coincide, the valve opening pressure at the time of discharge decreases, and the load on the rotor 4 is reduced. Reduction of excessive compression work has been realized.

In FIG. 7B, the lift ratio of the discharge valve in the compressor in which the discharge path is constituted only by the unique path is shown by a thin line, and the discharge path is constituted by adding an appropriate additional path to the unique path. The lift ratio of the vane type compressor 10 according to one embodiment is indicated by a thick line. Here, the lift ratio indicates the degree of opening of the discharge valve 23, and the state of the lift ratio 1 indicates that the discharge valve 23 is fully opened while being regulated by the valve support 27 shown in FIG. It shows the state that it is doing.
Further, a state where the lift ratio is 0 indicates a state where the discharge valve 23 is completely closed. When an appropriate additional path is provided, the time to start opening and the time to reach the peak value are earlier than in the case of only the specific path. This also proves that the provision of the appropriate additional path reduces the valve opening pressure of the discharge valve 23 when the valve is opened. That is, it is understood that the excessive compression work by the rotor 4 is reduced.

FIG. 8 shows the case of the compressor in which the discharge path is constituted only by the unique path, and the vane compressor 10 of the first embodiment in which the discharge path is constituted by adding an appropriate additional path to the unique path.
3A and 3B show changes in the volume and pressure of the fluid to be compressed in the suction, compression, and discharge steps in the compression chamber 15. The graph in FIG. 8 is drawn in a loop shape, and shows one cycle of the suction, compression, and discharge processes. The lower part of the graph shows the suction step of the fluid to be compressed, the upper part shows the compression step until the pressure in the discharge port reaches the pressure after the discharge valve, and the range exceeding the pressure after the discharge valve shows the discharge step. I have. That is, referring to FIG. 8 corresponding to the rotation of the rotor 4, the state of the fluid to be compressed changes counterclockwise. Note that the valve opening timing at which the pressure in the discharge port coincides with the pressure after the discharge valve is different in the above two cases. In FIG. 8, the discharge step and the compression step are separated based on the valve opening timing in the case of the first embodiment in which an appropriate additional path is provided. In other cases, the separation between the ejection step and the compression step does not always match that in FIG.

Vane type compressor 1 provided with an appropriate additional path
In the case of 0, the peak value of the pressure in the discharge port is lower in the discharge step than in the case of only the specific path, and
The peak value is located on the lower volume side (left side in the figure). The above means that the discharge valve 23 is opened and the fluid to be compressed is discharged at a stage where the pressure on the compression chamber 15 side is lower than in the related art. In FIG. 8, in both cases, the area of the portion surrounded by the loop indicates the size of the compression work of the compression chamber 15 by the rotor 4. When an appropriate additional path is provided, the work corresponding to the area of the hatched portion (in the ejection step) is reduced as compared with the case where only the unique path is used. Accordingly, FIG. 8 also shows that in the case of the vane compressor 10 having an appropriate additional path, the overcompression loss of the fluid to be compressed is small, and the excessive compression work by the rotor 4 is reduced. I have.

As described above, according to the first method of determining the length of the discharge path, an appropriate discharge path length is determined, and a vane compressor having an appropriate discharge path length is configured.
The propagation timing of the expansion wave and the valve opening timing of the discharge valve 23 can be matched. The expansion wave has a lower pressure than the internal pressure of the case, and lowers the valve opening pressure of the discharge valve 23. Reduced.

Next, a second method of determining an appropriate ejection path length (additional path length) will be described with reference to FIGS. FIG. 9 is a schematic diagram showing the configuration of the ejection path, and FIG. 10 is a flowchart showing a second method of determining an appropriate ejection path length. In the discharge path where the pressure wave propagates,
If the cross-sectional area or cross-sectional shape of the path changes depending on the position of the path, the propagation speed of the compressor also changes depending on the position of the path. Also in the vane compressor 10 of the first embodiment, the high-pressure chamber 24 differs from the outlet hole 25 and the pipe 47 in cross-sectional area and cross-sectional shape. When passing through a tubular path such as the outlet hole 25 or the pipe 47,
In the case of passing through a path wider than the tubular path as in No. 4, since the equivalent required length changes as described later, a change occurs in the propagation time of the pressure wave. here,
As shown in FIG. 9A, the high-pressure chamber 24 is a volume part,
An additional path portion such as the outlet hole 25 and the pipe is defined as a tubular portion. The tubular portion, even if it is a pipe, the groove described below,
It may be a hole or an outlet hole 25,
This is a portion where the cross-sectional area and the cross-sectional shape are formed identically at any position on the path. In this embodiment, the sectional area is F, the sectional shape is circular, and the diameter is d. The volume of the high-pressure chamber 24, which is a volume portion, is set to Vc. In the relation of the equivalent required length described later, the tubular portion is affected by the cross-sectional area and the diameter (when the cross-sectional shape is circular), whereas the volume is affected only by the size of the volume. And
The path length of the tubular portion of the tubular portion is Lp, and the path length of the exit hole of the exit hole 25 is Ls. The sum of the additional path length L and the exit hole path length Ls is equal to the pipe path length Lp (formula (11) described later).

Considering the path length of the pressure wave based on the pipe path length Lp of the tubular part, the substantial path length of the volume part needs to be treated as a path length taking into account the correction amount. . The intrinsic path length L0 and the appropriate discharge path length Lrfit, which are determined by the above-described first determination method, are path lengths in consideration of the correction amount. This is the path length assuming. Here, as shown in FIG. 9 (c), the path length of the high-pressure chamber 24 taking into account the correction amount is set to the volume part path length Lv, and the path length of the exit hole 25 is set to the exit hole path length Ls. .
In the first determination method, first, the eigenpath length L0 is obtained,
Next, an appropriate additional path length Lfit is determined by obtaining the ejection path length Lrfit provided with an appropriate additional path, and obtaining the difference between these. In this case, since the high-pressure chamber 24 is included in the specific path and the specific path is removed in the step of obtaining the difference, the additional path length Lrfit is determined without measuring the path length of the volume path length Lv. can do.

The second determining method is roughly divided into the following three steps. In the first stage, an appropriate ejection path length Lrfit is determined using the same procedure as the first determination method. In the second stage, the appropriate discharge path length Lrfit is substituted into the relational expression of the equivalent required length, and the appropriate pipe section path length Lpf
It is determined (calculated). In the third stage, an appropriate additional path length Lfit is determined.

First, an appropriate ejection path length Lrfit is determined in the same procedure as the above-described first determination method. FIG.
Steps 201 to 2 of the second determination method shown in
Procedures up to step 04 are the same as steps 101 and steps 104 to 106 of the first determination method shown in FIG. That is, first, the pressure waveform is measured in a state in which the compressor has no additional path and the discharge path has only the unique path (step 201). Next, by referring to the pressure waveform (FIG. 6) in the case of only the eigenpath,
Optimal timing Tfit when an appropriate ejection path is provided
Is derived (predicted) (step 202). Then, by deriving the position of the optimum timing Tfit, the amount of rotation of the rotor 4 from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit is measured as the rotor angle change B. As previously mentioned,
When the discharge is performed at the optimal timing Tfit, the valve opening pressure is reduced to the maximum, so that the compression work by the rotor 4 is reduced. Then, when the measured rotor angle variation B is substituted into the equation (8), the elapsed time from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit is calculated (step 203). 9 (b) and 9
The appropriate ejection path length Lrfit shown in (c) is calculated by using the following equation (7) (step 204).

Next, the appropriate discharge path length Lrfit determined in step 204 is substituted into the relational expression of the equivalent required length (formulas (9) and (10) described later), and an appropriate pipe section is obtained. The path length Lpfit is determined (calculated). Specifically, this is performed as follows. The discharge path including the tubular part and the volume part as shown in FIG. 9B corresponds to the discharge path as shown in FIG. Will do. Then, the determined appropriate discharge path length Lrfit is
Actually, this is the length of the discharge path when the discharge path including the high-pressure chamber 24 having the volume Vc is a tubular path having the same cross-sectional area and diameter. Appropriate discharge path length Lrfit
Measures the rotor angle change B as described above,
The elapsed time from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit is calculated, and is determined by using the equation (7). Appropriate pipe path length Lpfi
t, appropriate ejection path length Lrfit, open end correction Lc,
Equation (9) between the cross-sectional area F and the diameter d, (1)
The relationship of equation (0) holds. In equation (9), tangen
The inverse function of the t function is used.

[0063]

(Equation 7)

Expression (9) is a relational expression of the equivalent required length, and expression (10) is an expression for correcting the opening end. The opening end correction Lc is deleted by using the relationship of the expression (9) and the expression (10),
Further, by substituting the appropriate discharge path length Lrfit determined as described above, the appropriate pipe section path length Lpfi
t is determined (step 205). 9 (b) and 9 (c), the relationship of the equation (11) is established between the pipe path length Lpfit, the exit hole path length Ls, and the appropriate additional path length Lfit. .

[0065]

(Equation 8)

From equation (11), the pipe path length Lpfit
By subtracting the exit hole path length Ls obtained by measuring the size of the exit hole 25, an appropriate additional path length Lfit is determined (step 206). As described above, an appropriate additional path length Lfit is determined. The compressor in which the additional path having the appropriate additional path length Lfit is configured by the pipe 47 is the vane compressor 10 of the first embodiment.

In the second determining method, the use of the relational expression of the equivalent required length in the equation (9) eliminates the need for determining the eigenpath length L0 required in the first determining method. As described above, the specific path length L0 is obtained by measuring the rotor angle change amount A, calculating the elapsed time from the discharge compression wave maximum generation timing Tb to the compression wave propagation timing Tc, and using the above equation (3). Has been determined. Therefore, even when it is difficult to specify the compression wave propagation timing Tc (or the expansion wave maximum propagation timing Te) from the pressure waveform (FIG. 6), the appropriate additional path length can be obtained by using the second determination method. Lfit (appropriate ejection path length Lrfit) can be determined.

Next, a third method of determining an appropriate ejection path length (additional path length) will be described with reference to FIGS. FIG. 11 is a flowchart showing a third method of determining an appropriate discharge path length. FIG. 12 is a pressure waveform of each pressure in a compressor having a discharge path formed only by a unique path, and a theoretical waveform of a discharge port pressure. FIG. As described above, the measurement of the pressure in the discharge port is performed at the measurement position shown in FIG. For this measurement, it is necessary to provide a pressure sensor in the cylinder 1 so that the detection unit of the sensor can come into contact with the fluid to be compressed in the discharge port 22. That is, a hole is formed in the side wall inside the discharge port 22, and the pressure sensor is disposed in the hole. Since the opening area of the discharge port 22 is small to perform a proper operation by inserting a tool or the like, it is difficult to provide a hole for disposing a pressure sensor in the cylinder 1 already manufactured. In addition, it is difficult to provide a special manufacturing process (for example, forming a hole for disposing a pressure sensor by casting) only for a test machine for determining a discharge path length. Thus, in the third determination method, an appropriate discharge path length (additional path length) is determined without the need for actual measurement of the discharge port internal pressure.

The third determining method is roughly divided into the following four steps. In the first stage, a theoretical formula for the pressure in the discharge port is derived. In the second stage, an appropriate ejection path length Lrfit is determined using the theoretical formula obtained in the first stage. In the third stage, an appropriate tube path length Lpfit is determined (calculated) using the relationship between the equivalent required lengths, as in the second stage of the second determination method. In the fourth step, an appropriate additional path length Lfit is determined as in the third step of the second determination method.

Since the fluid to be compressed in the compression chamber 15 is compressed in an adiabatic state, a state equation of adiabatic change can be applied. Assuming that the pressure in the compression chamber 15 is P and the volume is V,
Equation (12) holds. The multiplier k of the volume V is the specific heat ratio of the adiabatic change (molar specific heat / constant molar specific heat). Further, the product of the pressure P on the left side and the k-th power of the volume V is constant.

[0071]

(Equation 9)

From the compressor operating conditions described above, the suction pressure P1 in the compression chamber 15 in the suction process and the suction volume V1 immediately after the end of the suction process are specified. By substituting the suction pressure P1 and the suction volume V1 into the equation (12), (13)
An expression is derived. Equation (13) is a theoretical equation for the pressure in the discharge port (step 301). In FIG. 12, a theoretical waveform using the theoretical formula is used as a substitute for the measured value of the pressure in the discharge port. Then, an appropriate discharge path length can be determined without actually measuring the discharge port pressure which is difficult in the above. Also, the measurement results of the post-discharge valve pressure and the case internal pressure other than the discharge port internal pressure are shown in FIG. 12 (step 302).

[0073]

(Equation 10)

In the third determination method, the calculation of the optimum timing is performed as follows. Optimal timing T
As described above, “fit” is a timing at which the expansion wave maximum propagation timing coincides with the valve opening timing when an appropriate discharge path is provided, and the discharge valve 23 is opened at this timing. Thus, the discharge pressure is reduced to the maximum. The optimum timing Tfit is also the expansion wave maximum propagation timing, and at this time, the post-discharge valve pressure is the pressure P2 at which the minimum value is reached. Also, the optimal timing T
Since the “fit” is also the valve opening timing, the pressure in the discharge port at the optimum timing Tfit is the same as the minimum pressure P2.
Becomes When the pressure P2 and the volume V2 at the optimum timing Tfit are substituted into (13), the relationship of the expression (14) is established.

[0075]

[Equation 11]

From equation (14), the optimum timing Tfit
, The volume V2 of the compression chamber 15 can be calculated. The volume of the compression chamber 15 is uniquely determined by the rotation angle of the rotor 4. The reverse is also true, and the rotor angle is uniquely determined by the volume of the compression chamber 15. Referring to FIG. 12, the rotor angle when the volume is V2 can be specified, and the position of the optimum timing Tfit is derived (step 3).
03). Then, the optimal timing Tfit (volume V2)
Is determined using the discharge compression wave maximum generation timing Tb as a reference position.

The method of specifying the rotor angle change amount B is as follows.
As in the first and second determination methods, a horizontal line (constant pressure graph) is drawn at a pressure at which the post-discharge valve pressure is a minimum value, and the timing at which the horizontal line matches the discharge port pressure is specified. Then, it may be derived. Further, in order to obtain the rotor angle change amount B, instead of using the minimum pressure P2 at the optimum timing, the calculation may be performed using the discharge pressure P0 at the time of valve opening. The discharge pressure P0 is equal to the case pressure. By substituting the discharge pressure P0 into the above equation (13), the volume V0 of the compression chamber 15 at that time can be calculated. As described above, since the relationship between the volume of the compression chamber 15 and the rotor angle is uniquely determined, the amount of change in the rotor angle when the volume becomes V0 is the amount of change in the rotor angle when the volume becomes V2. B is different. As described above, since the pressure after the discharge valve has a gentle slope near the expansion wave maximum propagation timing, even if the valve opening timing slightly deviates from the expansion wave maximum propagation timing (by about ± 10 ° in rotor angle), it does not open. The effect of reducing the valve pressure is not lost. Therefore,
The discharge pressure P0 may be substituted for the minimum pressure P2, and a value deviated from the rotor angle change B may be used as the rotor angle change at the optimal timing.

When the rotor angle change amount B is calculated, the following operations in the third determining method are the same as those in the second determining method. By substituting the calculated rotor angle variation B into the equation (8), the elapsed time from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit is calculated (step 304). Further, FIGS. An appropriate ejection path length Lrfit shown in FIG. 9 (c) is calculated using the expression (7) described later (step 305). Then, also in the third determination method, the additional path length Lfit is determined using the relation of the equivalent required length. Expression (9) which is a relational expression of the equivalent required length and expression (1)
The opening end correction Lc is deleted from the equation (0). Further, the appropriate ejection path length Lrfi determined as described above.
t is substituted into the equation (9) to obtain an appropriate pipe path length Lpf.
It is determined (step 306). When the outlet hole path length Ls is subtracted from the pipe section path length Lpfit from the equation (11), an appropriate additional path length Lfit is obtained.
Is determined (step 307). As described above,
An appropriate additional path length Lfit is determined. Then, an additional path having an appropriate additional path length Lfit is connected to the pipe 47.
Is the vane type compressor 10 of the first embodiment.
It is.

In the third determination method, as described above, the theoretical formula of the discharge port pressure is used as a substitute for the measured value of the discharge port pressure. The discharge path length Lrfit (additional path length L
fit) can be determined. For this reason, it is possible to reduce the manufacturing cost of the testing machine required for determining the discharge path length Lrfit.

Next, a method of theoretically determining an appropriate discharge path length (additional path length) will be described with reference to FIG. FIG. 13 is a flowchart showing a method for theoretically determining an appropriate discharge path length. According to the first to third determination methods, a compressor having a discharge path only as a unique path is configured as a test machine, and a pressure waveform measured by the test machine (see FIGS. 6 and 1).
Based on 2), an appropriate ejection path length Lrfit (appropriate additional path length Lfit) is determined. On the other hand, in the method for theoretically determining the length of the discharge path shown in FIG. hand,
I'm trying to decide.

In the following, an appropriate discharge path length Lrfit
The theoretical determination method for determining (appropriate additional path length Lfit) is determined according to the order of equations used in the method.
I will explain. The equations used in the theoretical determination method are the following equations (15), (8), (7), (9),
Expressions (10) and (11). By substituting the results of the preceding equation into the following equation in accordance with the above-listed equations in this order, and calculating sequentially, an appropriate additional path length Lfit is finally determined from equation (11). You. In the following, each calculation formula will be described according to this order, but at the same time, the procedure of the theoretical determination method will be described.

The expression (15) described later is, as described above,
This is a relational expression derived in advance, and is a relational expression relating to compressor operating conditions, the above-described specific elements of the compressor, and the expansion wave maximum propagation timing. As described above, the compressor operating conditions include the operating speed of the rotor shaft 5, the type of the fluid to be compressed (refrigerant), the pressure and the temperature of the fluid to be compressed at the time of suction, and the like. Specific elements of the vane-type compressor include the shape and dimensions of each member constituting the compressor, the number of vanes provided on the rotor, the number of discharge ports, and the like. Is to be determined. Also,
As described above, when the expansion wave propagates to the discharge valve 23, the expansion wave has an effect of reducing the valve opening pressure. For this reason, the effect of the valve opening pressure drop greatly changes depending on the position of the timing at which the expansion wave propagates to the maximum. Therefore, by deriving the relational expression and specifying variables relating to the compressor operating conditions and the unique elements of the compressor, it is possible to calculate at which timing the expansion wave maximum propagation timing comes.

The above relational expression is derived as follows. First, the timing at which the reflected wave of the discharge compression wave propagates to the discharge valve is measured for each compressor operating condition and each unique element of the compressor. Then, the measurement result is accumulated, and the causal relationship between the compressor operating condition, the unique element of the compressor, and the propagation timing is derived from the accumulation result. In other words, the above relational expression is a relational expression related to the timing at which the reflected wave of the discharge compression wave propagates to the discharge valve, which is determined by the compressor operating conditions and the unique elements of the compressor. From the above-described derivation work, it has been clarified that the propagation timing largely depends on the number of vanes provided. Therefore, in the theoretical determination method, the relational expression is determined as a function depending only on the number of vanes provided, and the shape and dimensions of each member constituting the compressor, elements unique to the compressor such as the number of discharge ports, and the like. , And did not depend on compressor operating conditions. Therefore, when the vane arrangement number is substituted into the relational expression of the causal relationship, the rotor angle change amount B is calculated (step 401). As described above, the rotor angle change amount B indicates the amount of angle of rotation of the rotor from the maximum timing of the discharge compression wave to the optimum timing. The relational expression assumes that the following relationship is satisfied, where n is the number of vanes provided.

[0084]

(Equation 12)

The numeral 6 is written in the denominator in the equation (15). The number was determined from the causal relationship,
It is a correction value. In the present embodiment, the correction value is not a variable but a constant, since it does not depend on the compressor operating conditions or the unique elements of the compressor except for the number of vanes. Then, depending on the magnitude of the correction value, for example, FIG.
It is determined how much the expansion wave maximum propagation timing Te shown in FIG. 12 is delayed or advanced. As described above, since the pressure after the discharge valve has a gentle slope near the expansion wave maximum propagation timing, the valve opening timing is slightly larger than the expansion wave maximum propagation timing (± 1 in rotor angle).
Even if it deviates, the effect of reducing the valve opening pressure is not lost. In other words, the effect of reducing the valve opening pressure can be obtained regardless of whether the compressor has a different characteristic element excluding the number of vanes provided by the correction value in the equation (15) or a different compressor operating condition. It is done. The correction value when such an effect is obtained is 6. Therefore, the correction value is set to 5 to 7
It may be a value in the vicinity of 6, such as Substituting the number of vanes 9 provided in the vane compressor 10 into the number of vanes n, the rotor angle change amount B is 60 from the equation (15).
°. 6 and 12, the rotor angle variation B
Is approximately 60 °, and the optimal timing Tfit substantially coincides between the case of measurement and the case of the theoretical determination method. And such an optimal timing T
The fit or approach of the fit is not limited to the compressor operating conditions shown in FIGS. 6 and 12. If the compressor operating conditions are different, the unique elements other than the vane arrangement number n may be different. It is realized even in different cases.

By substituting the rotor angle variation B calculated from the equation (15) into the equation (8), the elapsed time from the discharge compression wave maximum generation timing Tb to the optimum timing Tfit is calculated (step 402). Further, FIG.
(B), an appropriate ejection path length Lr shown in FIG.
fit is calculated using the equation (7) (step 40).
3). Equation (9) is a relational equation of the equivalent required length, and (1)
Equation (0) is an equation for aperture end correction. (10)
The opening end correction Lc is deleted using the relationship of the expression, and the appropriate ejection path length Lrf determined as described above is further determined.
By substituting “it”, an appropriate pipe path length Lpfit is determined (step 404). In addition, the pipe path length Lpf
it, exit hole path length Ls, appropriate additional path length Lfi
As shown in FIGS. 9B and 9C, t is (11)
The relationship of the formula is established. From equation (11), the pipe path length L
When the exit hole path length Ls is subtracted from pfit, an appropriate additional path length Lfit is determined (step 40).
5). As described above, the appropriate additional path length Lfit
Is determined. The compressor in which the additional path having the appropriate additional path length Lfit is configured by the pipe 47 is the vane compressor 10 of the first embodiment.

As described above, the appropriate discharge path length is determined according to the theoretical method for determining the discharge path length, and the vane compressor having the appropriate discharge path length is configured. And the opening timing of the discharge valve 23 can be matched. The expansion wave has a lower pressure than the pressure in the case, and reduces the valve opening pressure of the discharge valve 23. Therefore, the excessive compression work of the compression chamber 15 performed by the rotor to open the discharge valve 23 is reduced. Is done.

Next, a lubricating oil removing section 51 is provided in the compressor,
The vane-type compressor 120 according to the second embodiment uses the passage hole 52 formed in the lubricating oil removing portion 51 as the appropriate additional passage.
Will be described with reference to FIGS. 14 to 16. FIG.
16 is a partial sectional view in the rotor axial direction showing the vane type compressor of the second embodiment, and FIG. 15 is a partial sectional view in the rotor axial direction showing the vane type compressor of the second embodiment. FIG. 5 is a five-view drawing showing a lubricating oil removing unit of the second embodiment. FIG.
4. As shown in FIG. 15, in the vane compressor 120 of the second embodiment, a lubricating oil removing unit 51 is provided on the side block 3 on the side opposite to the cylinder 1. Lubricating oil removal unit 51
Are configured in a shape as shown in FIG. FIG.
16A is a front view of the lubricant removing unit 51, FIG. 16C is a rear view of the lubricant removing unit 51, FIG. 16D is a side view of the lubricant removing unit 51, and FIG. It is a plane sectional view of oil removal part 51. The lubricating oil removing section 51 has the outlet hole 25
• Route holes 52 are formed to communicate with 25.
A discharge path is formed from the discharge port 22 to the outlet end 52a (end of the discharge direction) of the path hole 52. At the outlet end 52a of the passage hole 52, the fluid to be compressed
The fluid to be compressed is released at the outlet end 52 a of the passage hole 52.

Here, the path hole 52 corresponds to the additional path, and the pipe 47 provided in the vane type compressor 10 of the first embodiment.
This has the same effect as described above. That is, the vane type compressor 120 is provided with the lubricating oil removing unit 51 in which a path hole having an appropriate additional path length is formed, so that the discharge path length becomes an appropriate discharge path length. By providing an appropriate discharge path in the vane compressor 120, as described above, the maximum propagation timing of the expansion wave can be made to coincide with the valve opening timing of the discharge valve 23, and the valve opening pressure can be reduced. In addition, excessive compression work by the rotor 4 can be reduced.

The cross-sectional area and cross-sectional shape of the inlet end 52b of the passage hole 52 (the end of the passage hole 52 on the cylinder 1 side) are the cross-sectional area and cross-sectional shape of the outlet end 25a of the outlet hole 25 formed in the side block 3. It is formed so as to match. The outlet hole 25 and the passage hole 52 can be treated as an integral tubular part in the relationship between the equivalent required lengths used in the second and third determination methods and the theoretical determination method.

A lubricating oil removing plate 53 is provided in the lubricating oil removing unit 51 in front of the passage hole 52 in the discharge direction (rearward of the compressor body). An open space is formed between the outlet end 52a of the passage hole 52 and the lubricating oil removing plate 53, and the outlet end 52a is released in pressure in the open space.
The lubricating oil removing plate 53 is formed in a V-shape in a plan view, and is provided such that the forked end side of the lubricating oil removing plate 53 is located forward (in the rear of the compressor body) in the discharge direction. The compressed fluid discharged from the passage hole 52 is
The lubricating oil removing portion 53 is in contact with the lubricating oil removing plate 53 that is inclined with respect to the discharge direction, and flows out to the left and right outside of the lubricating oil removing portion 51. Here, the lubricating oil mixed in the fluid to be compressed is separated at the time of contact with the lubricating oil removing plate 53. That is, the lubricating oil removing plate 53 functions as a filter for separating lubricating oil.

In the vane compressor 120 according to the second embodiment having the lubricating oil removing section 51 having the above-described configuration, the discharge can be performed simply by using the lubricating oil removing sections 51 having different path hole lengths of the path holes 52. The discharge path length of the path can be changed. Therefore, the propagation timing of the expansion wave and the discharge valve 2
An appropriate discharge path length that matches the valve opening timing of No. 3 can be easily realized. Further, by providing the lubricating oil removing unit 51 in the vane compressor 120, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

Next, a lubricating oil removing section 61 is provided in the compressor,
The channel groove 62 formed in the lubricating oil removing portion 61 is used as the appropriate additional channel, and the vane type compressor 130 of the third embodiment is used.
Will be described with reference to FIGS. FIG.
FIG. 19 is a partial sectional view in the rotor axial direction showing the vane type compressor of the third embodiment. FIG. 18 is a partial sectional view in the rotor axial direction showing the vane type compressor of the third embodiment. FIG. 20 is a rear view in the rotor axial direction showing the vane type compressor of the third embodiment, and FIG. 20 is a five-view drawing showing a lubricating oil removing unit of the third embodiment. As shown in FIGS. 17 and 18, in the vane compressor 130 of the third embodiment, a lubricating oil removing unit 61 is provided on the side block 3 on the side opposite to the cylinder 1. The lubricating oil removing unit 61 is configured in a shape as shown in FIG. It is configured in a shape as shown in FIG. FIG.
0 (a) is a front view of the lubricating oil removing unit 51, FIG. 20 (c) is a rear view of the lubricating oil removing unit 51, FIG. 20 (d) is a side view of the lubricating oil removing unit 51, and FIG. FIG. 3 is a plan sectional view of a lubricating oil removing unit 51. On the front surface (the side of the side block 3) of the lubricating oil removing portion 61, path grooves 62, 62 communicating with the outlet holes 25, 25 are formed. In addition, a lubricating oil removing portion 61 is provided at an end of the channel groove 62 on a side not connected to the outlet end 25a.
A path hole 64 is formed to pass through the front and rear surfaces of the hole. When the lubricating oil removing portion 61 is abutted on the side block 3 and fixed, the channel grooves 62 have a closed configuration except for the openings at both ends, and can be used as a channel for discharging the compressed fluid. Then, an ejection path is formed from the ejection port 22 to the exit end 64a (the end in the ejection direction) of the path hole 64 via the path groove 62. At the exit end 64a of the passage hole 64,
The compressed fluid is discharged into the open space in the chamber 14, and the compressed fluid is released at the outlet end 64 a of the passage hole 64.

The path formed by combining the path groove 62 and the path hole 64 corresponds to the additional path, and has the same effect as the pipe 47 provided in the vane compressor 10 of the first embodiment. Things. That is, the vane type compressor 130 is provided with the lubricating oil removing unit 61 such that the path length of the path groove 62 and the path hole 64 becomes an appropriate additional path length. Length. By providing an appropriate discharge path in the vane compressor 130, as described above, the maximum propagation timing of the expansion wave can be made to coincide with the valve opening timing of the discharge valve 23, and the valve opening pressure is reduced. In addition, excessive compression work by the rotor 4 can be reduced.

A lubricating oil removing plate 63 is provided in the lubricating oil removing section 61 in front of the passage hole 64 in the discharge direction (rearward of the compressor body). The lubricating oil removing plate 63 has the same configuration as the lubricating oil removing plate 53 provided in the lubricating oil removing unit 51 of the second embodiment, and has the same function. The shape of the path formed by the path groove 62 is not a straight path but a curved path. As described above, the above-described action of lowering the valve opening pressure of the discharge valve 23 depends on the length of the discharge path, but hardly relates to the path shape of the discharge path 50. There is no problem. By providing a bend in the path, it is possible to make the path length longer in a limited space of the lubricating oil removing unit 61 than in the case of a straight line.

In the vane compressor 130 of the third embodiment provided with the lubricating oil removing section 61 having the above-described configuration, the discharge can be performed only by using the lubricating oil removing sections 61 having different path groove lengths of the path grooves 62. The discharge path length of the path can be changed. Therefore, the propagation timing of the expansion wave and the discharge valve 2
An appropriate discharge path length that matches the valve opening timing of No. 3 can be easily realized. Further, by providing the lubricating oil removing unit 61 in the vane compressor 130, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

Next, the vane type compressor 14 of the fourth embodiment in which the compressor is provided with the lubricating oil removing portion 51 and the spacers 54 and 55 is provided.
0 will be described with reference to FIGS. 21 to 24. FIG.
FIG. 1 is a partial sectional view in the rotor axial direction showing a vane type compressor of a fourth embodiment, and FIG. 22 is a partial sectional view in the rotor axial direction showing the vane type compressor of the fourth embodiment. 23
FIG. 24 is a two-sided (front and plan) view showing the spacer of the fourth embodiment, and FIG. 24 is a two-sided (front and plan) view showing the path partitioning spacer of the fourth embodiment. As shown in FIGS. 21 and 22, in the vane type compressor 140 of the fourth embodiment, the lubricating oil removing unit 51 is provided on the side block 3 opposite to the cylinder 1 side.
Is provided. One or a plurality of spacers 54 and 55 are provided between the side block 3 and the lubricating oil removing portion 51, respectively. Lubricating oil removal unit 51, spacer 54
A path hole and a path groove are formed in 55, respectively.
By arranging the spacers 54 and 55 between the side block 3 and the lubricating oil removing section 51 in a manner described later, the path holes and the path grooves of these members are appropriately communicated. I have. Here, “appropriate” means the following. The communication path formed by the path holes and the path grooves of these members has the same cross-sectional area and substantially the same cross-sectional shape regardless of the position on the path, and the communication path can be regarded as the tubular portion. It is. If it can be regarded as a tubular portion, it is possible to apply the relationship of the equivalent required length, and determine the path length of the communication path using the second, third determination method and the theoretical determination method Becomes possible.

As shown in FIG. 23, the spacer 54 has long grooves 54a formed on the front and rear surfaces when it is disposed in the compressor.
-54a is formed, and four long grooves 54a are formed in total. In each of the front and rear surfaces, a long groove 54
a · 54a is formed to be symmetrical in plan view. In addition, the outlet hole 25 formed in the side block 3 and the passage hole 52 formed in the lubricating oil removing portion 51 are formed so as to overlap in a front view (rear view) at the time of the arrangement. The long grooves 54a formed on the front and rear surfaces
The set of 54a has a long groove 54 in each of the left and right sets.
A hole 54b is formed on the inside of the long groove 5a.
4a and 54a communicate with each other. According to the above configuration, when the spacer 54 is provided at the rear portion of the side block 3, the long groove 54a on the side block 3 side is closed except for openings at both ends, and can be used as a path for discharging the compressed fluid. When the spacer 54 is provided in front of the lubricating oil removing unit 51, the long groove 54a on the lubricating oil removing unit 51 side can be used as a path for discharging the compressed fluid.

However, when the spacers 54 are arranged side by side, the communicating portion between the spacers 54 becomes wider than the cross section of the outlet hole 25 or the passage hole 52. Then, the discharge path from the outlet hole 25 to the path hole 52 cannot be handled as a tubular portion having the same cross-sectional area. As described above, if there are path portions having different cross-sectional areas, the relationship between the equivalent required lengths described above cannot be used. Alternatively, a more complicated equivalent required length relationship in which three or more sections having different cross-sectional areas are used may be used. Would.

Therefore, the spacer 55 is provided between the spacers 54 so that the discharge path from the outlet hole 25 to the passage hole 52 can be handled as a tubular portion having an equal cross-sectional area. As shown in FIG. 24, the spacer 55 has a front view (rear view)
Path hole 56.5 overlapping with exit hole 25 and path hole 52
6 are formed. When the spacer 55 is provided at one of the front and rear portions of the spacer 54, the long groove 54a on the spacer 55 side becomes a sealed configuration except for the openings at both ends, and can be used as a path for discharging the compressed fluid. In addition, the cross-sectional area of the path can be made substantially equal on the path. Then, the relationship of the equivalent required length can be used.

With the above arrangement, the spacers 54 and the spacers 55 are arranged side by side, so that one or a plurality of spacers 54.
5 and the length of the communication path formed by the lubricating oil removing portion 51 can be freely adjusted. Then, it is possible to easily realize an appropriate discharge path length in which the propagation timing of the expansion wave and the valve opening timing of the discharge valve 23 match. Further, by providing the lubricating oil removing unit 51 in the vane compressor 140, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

In the configuration of the fourth embodiment, the length of the discharge path may be adjusted using only one or a plurality of spacers 55. In the case of the spacer 55, even if a plurality of spacers are connected in parallel, the outlet hole 25, the spacers 55, 55,.
In the communication path formed by the path hole 52, the cross-sectional area does not change depending on the position on the path. Therefore, the relation of the equivalent required length can be applied.
Further, in the configuration of the fourth embodiment, a configuration may be used in which the lubricating oil removing unit 61 in which the channel groove 62 is formed is used instead of the lubricating oil removing unit 51. In this case,
It is necessary to arrange the lubricating oil removing portion 61 and the spacer 54 in which the long groove 54a is formed so as not to be adjacent to each other so that the sectional area does not change depending on the position on the path.

[0103]

According to the present invention, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on a rear end surface of the cylinder, and a rotor is rotatably provided on the inner peripheral surface of the cylinder.
A compressor in which a vane groove is formed in a rotor, a vane is slidably mounted in the vane groove, a discharge port is provided in a cylinder, and a discharge valve is provided with a discharge valve for opening and closing the discharge port. The discharge path length to the path outlet end is determined to be an appropriate discharge path length based on the pressure waveform measured under the compressor operating conditions, and the compression wave is compressed by the reflected wave of the discharge compression wave at the outlet end. Since the valve opening pressure at the time of fluid discharge is reduced, the propagation timing of the expansion wave and the valve opening timing of the discharge valve can be matched. The expansion wave is
Since the pressure is lower than the pressure in the case and lowers the valve opening pressure of the discharge valve, excessive compression work of the compression chamber performed by the rotor to open the discharge valve is reduced.

As described in claim 2, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on the rear end surface of the cylinder, and a rotor is rotatably provided on the inner periphery of the cylinder.
In a compressor in which a vane groove is formed in a rotor, a vane is slidably mounted in a vane groove, a discharge port is provided in a cylinder, and a discharge valve for opening and closing the discharge port is provided, a discharge path of a fluid to be compressed is discharged. Composed of a unique path from the outlet to the outlet end of the outlet hole formed in the side block, and an additional path having a pressure-released outlet end. Measured and calculated the time for the discharge pressure wave to reciprocate on the specific path from the pressure waveform to determine the specific path length, and the reflected wave of the discharge pressure wave propagates to the discharge valve at the opening timing of the discharge valve. Deriving a timing position, determining an appropriate discharge path length from the optimum timing position and the propagation speed of the pressure wave determined by the compressor operating conditions, and selecting an appropriate additional path from the appropriate discharge path length and the appropriate proper path length. length Since determined, it is possible to eliminate the influence of the discharge passage length by an open end correction can be performed to determine the exact discharge passage length. Then, the propagation timing of the expansion wave can be matched with the valve opening timing of the discharge valve. Furthermore, since an appropriate additional path length is determined, the discharge path length can be adjusted only by adjusting the additional path length of the additional path added to the compressor, and the discharge path having an appropriate discharge path length can be easily obtained. Can be realized.

According to a third aspect of the present invention, a cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on the rear end surface of the cylinder, and a rotor is rotatably provided on the inner periphery of the cylinder.
In a compressor in which a vane groove is formed in a rotor, a vane is slidably mounted in a vane groove, a discharge port is provided in a cylinder, and a discharge valve is provided with a discharge valve for opening and closing the discharge port. The discharge path up to the path outlet end is composed of a tubular part and a volume part, and measures a pressure waveform under compressor operating conditions, and a reflected wave of the discharge pressure wave is generated from the pressure waveform at the opening timing of the discharge valve. Deriving the optimal timing position to propagate to, determine the appropriate discharge path length from the optimal timing position and the propagation velocity of the pressure wave determined by the compressor operating conditions, using the relational expression of the equivalent required length, the tubular part Since the appropriate pipe path length is determined, even when it is difficult to specify the maximum propagation timing of the compression wave or the maximum propagation timing of the expansion wave from the pressure waveform, it is necessary to determine the appropriate discharge path length. What to do Can. Then, the propagation timing of the expansion wave can be matched with the valve opening timing of the discharge valve.

According to a fourth aspect of the present invention, among the pressure waveforms, the pressure waveform of the pressure in the discharge port is replaced with the theoretical waveform of the adiabatic change instead of the measured pressure waveform. It is possible to determine an appropriate ejection path length (additional path length) while eliminating the need for measuring the length of the ejection path. Then, the propagation timing of the expansion wave can be matched with the valve opening timing of the discharge valve.

According to a fifth aspect of the present invention, a part of the discharge path is constituted by a pipe, and the appropriate discharge path length is adjusted by adjusting the pipe length. Can be easily realized. Further, even when the pipe is stored in the cylinder storage case, an appropriate discharge path length can be realized irrespective of the volume of the case by applying a bending process to the pipe.

According to a sixth aspect of the present invention, the discharge path is provided with a lubricating oil removing section for removing the compressor lubricating oil from the fluid to be compressed, and a path hole is formed in the lubricating oil removing section. Since the length is adjusted by adjusting the length of the path hole, the length of the discharge path can be changed only by using the lubricating oil removing units having different path hole lengths. Therefore, it is possible to easily realize an appropriate discharge path length in which the propagation timing of the expansion wave coincides with the valve opening timing of the discharge valve 23. Further, by providing the lubricating oil removing section, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

According to a seventh aspect of the present invention, the discharge path is provided with a lubricating oil removing section for removing the compressor lubricating oil from the fluid to be compressed, and a path groove is formed in the lubricating oil removing section to form the appropriate discharge path. Since the length is adjusted by adjusting the length of the path groove, the length of the discharge path can be changed only by using lubricating oil removing units having different path groove lengths. Therefore, it is possible to easily realize an appropriate discharge path length in which the propagation timing of the expansion wave coincides with the valve opening timing of the discharge valve 23. Further, by providing the lubricating oil removing section, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

According to an eighth aspect of the present invention, the discharge path is provided with a lubricating oil removing section and a spacer for removing the compressor lubricating oil from the fluid to be compressed, and the discharge path is provided in the lubricating oil removing section and the spacer. Since the formation and the appropriate discharge path length are performed by adjusting the number of spacers, the path length of the communication path formed by one or more spacers and the lubricating oil removing unit can be freely set. Adjustable. Then, it is possible to easily realize an appropriate discharge path length in which the propagation timing of the expansion wave coincides with the valve opening timing of the discharge valve. Further, by providing the lubricating oil removing unit, it is possible to separate the lubricating oil for the compressor that is mixed with the fluid to be compressed in the compression process.

According to a ninth aspect of the present invention, a plurality of discharge ports are provided, a compressed fluid outlet hole is provided for each discharge port in the side block, and a discharge path is provided from each discharge port through each outlet hole. The path outlet end is configured to release the pressure, and among the plurality of discharge ports, the path connecting one discharge port and at least one other discharge port is cut off, so that the rotor for opening the discharge valve is used. Excessive compression work is reduced.
Further, the occurrence of pressure wave interference that increases the valve opening pressure during discharge is prevented. Then, the valve opening pressure at the time of discharge increases due to the pressure wave from the other discharge port, thereby preventing the opening of the discharge valve from being obstructed and increasing the compression work.

[Brief description of the drawings]

FIG. 1 is a side sectional view in the rotor axial direction showing a vane type compressor of a first embodiment.

FIG. 2 is a sectional view in a rotor axial direction showing a vane-type compressor of the first embodiment.

FIG. 3 is a sectional view taken along line AA of FIG. 1;

FIG. 4 is a schematic diagram illustrating a configuration of a discharge path.

FIG. 5 is a flowchart showing a first method of determining an appropriate ejection path length.

FIG. 6 is a diagram showing pressure waveforms of the respective pressures in a compressor in which a discharge path is constituted only by a unique path.

FIG. 7 shows a compressor in which a discharge path is constituted only by a unique path;
FIG. 9 is a diagram illustrating a relationship between a rotor angle, a pressure, and a lift ratio in a compressor in which a proper additional path is provided in a proper path to form a discharge path.

FIG. 8 shows a compressor in which a discharge path is constituted only by a unique path;
FIG. 9 is a diagram illustrating a relationship between a compression chamber volume and a discharge port pressure in a compressor in which a discharge path is configured by providing an appropriate additional path in a proper path.

FIG. 9 is a schematic diagram illustrating a configuration of a discharge path.

FIG. 10 is a flowchart showing a second method of determining an appropriate ejection path length.

FIG. 11 is a flowchart showing a third method of determining an appropriate ejection path length.

FIG. 12 is a diagram showing a pressure waveform of each pressure and a theoretical waveform of a pressure in a discharge port in a compressor in which a discharge path is constituted only by a unique path.

FIG. 13 is a flowchart showing a method for theoretically determining an appropriate ejection path length.

FIG. 14 is a partial sectional view in a rotor axial direction showing a vane-type compressor of a second embodiment.

FIG. 15 is a partial cross-sectional view in the rotor axial direction showing a vane-type compressor of a second embodiment.

FIG. 16 is a five-view drawing showing a lubricating oil removing unit of the second embodiment.

FIG. 17 is a partial cross-sectional view in the rotor axial direction showing a vane-type compressor of a third embodiment.

FIG. 18 is a partial sectional view in a rotor axial direction showing a vane-type compressor of a third embodiment.

FIG. 19 is a rear view in the rotor axial direction showing the vane-type compressor of the third embodiment.

FIG. 20 is a five-view drawing showing a lubricating oil removing unit of the third embodiment.

FIG. 21 is a partial sectional view of a side surface in a rotor axial direction showing a vane-type compressor of a fourth embodiment.

FIG. 22 is a partial sectional view in the rotor axial direction showing a vane-type compressor of a fourth embodiment.

FIG. 23 is a two-sided (front and plan) view showing the spacer of the fourth embodiment.

FIG. 24 is a two-view (front and plan) view showing a spacer for a path partition of the fourth embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cylinder 3 Side block 4 Rotor 8 Vane groove 9 Vane 11 Cylinder storage case 22 Discharge port 23 Discharge valve 30 Communication path 47 Piping 51 ・ 61 Lubricating oil removing part 52 Path hole 54/55 Spacer 62 Path groove 64 Path hole Lfit Appropriate Addition path length Lrfit Appropriate discharge path length

Claims (9)

[Claims] 1. A cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on a rear end surface of the cylinder, a rotor is rotatably provided on the inner periphery of the cylinder, a vane groove is formed in the rotor, and a vane is formed in the vane groove. Slidably mounted, a discharge port is provided in the cylinder, and a discharge valve that opens and closes the discharge port is used to compress the discharge path length from the discharge port to the discharge path outlet end where pressure is released. Based on the pressure waveform measured under machine operating conditions, an appropriate discharge path length is determined, and the reflected wave at the outlet end of the discharge compression wave causes the valve opening pressure at the time of discharge of the compressed fluid to decrease. A vane compressor. 2. A cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on a rear end surface of the cylinder, a rotor is rotatably provided on an inner periphery of the cylinder, a vane groove is formed in the rotor, and a vane groove is formed in the vane groove. Slidably mounted, a discharge port is provided in the cylinder, and a discharge valve for opening and closing the discharge port is provided. And an additional path having a pressure-released outlet end, and measuring a pressure waveform under compressor operating conditions of the compressor using only the specific path, and a discharge pressure wave from the pressure waveform. The length of the specific path is determined by calculating the reciprocating time of the specific path, and the optimum timing position at which the reflected wave of the discharge pressure wave propagates to the discharge valve at the opening timing of the discharge valve is derived. Vane type characterized in that an appropriate discharge path length was determined from the pressure wave propagation velocity determined by the machine operating conditions, and an appropriate additional path length was determined from an appropriate discharge path length and an appropriate proper path length. Compressor. 3. A cylinder having a substantially elliptical inner peripheral surface is provided, a side block is provided on a rear end surface of the cylinder, a rotor is rotatably provided on the inner periphery of the cylinder, a vane groove is formed in the rotor, and a vane groove is formed in the vane groove. Slidably mounted, a discharge port is provided in the cylinder, and a discharge valve is provided to open and close the discharge port. And measuring the pressure waveform under the compressor operating conditions, deriving the optimal timing position at which the reflected pressure wave of the discharge pressure wave propagates to the discharge valve at the opening timing of the discharge valve from the pressure waveform. The appropriate discharge path length was determined from the pressure wave propagation velocity determined by the timing position and compressor operating conditions, and the appropriate pipe path length of the tubular portion was determined using the relational expression of the equivalent required length. Characterized by Vane type compressor. 4. The pressure waveform of the pressure in the discharge port among the pressure waveforms is a theoretical waveform of adiabatic change instead of the measured pressure waveform. A vane-type compressor as described. 5. A part of the discharge path is constituted by a pipe,
2. The vane compressor according to claim 1, wherein the appropriate discharge path length is adjusted by adjusting a pipe length. 6. A lubricating oil removing section for removing a compressor lubricating oil from a fluid to be compressed is provided in a discharge path, a path hole is formed in the lubricating oil removing section, and the appropriate discharge path length is determined by adjusting the length of the path. 2. The vane compressor according to claim 1, wherein the length of the hole is adjusted. 7. A lubricating oil removing section for removing a compressor lubricating oil from a fluid to be compressed is provided in a discharge path, a path groove is formed in the lubricating oil removing section, and the appropriate discharge path length is adjusted by a path. The vane compressor according to claim 1, wherein the groove length is adjusted. 8. A discharge path is provided with a lubricating oil removing section and a spacer for removing compressor lubricating oil from a compressed fluid, and a discharge path is formed in the lubricating oil removing section and the spacer, and 2. The vane compressor according to claim 1, wherein the length of the discharge path is adjusted by adjusting the number of spacers. 9. A plurality of discharge ports are provided, a compressed fluid outlet port is provided for each discharge port in the side block, a discharge path is provided from each discharge port through each outlet port, and the discharge path outlet end is pressure released. 9. The apparatus according to claim 1, wherein a path that connects one of the plurality of outlets and at least one other outlet is disconnected from the plurality of outlets. 10. Vane compressor.