Test method for compressor ring valve and test device for compressor ring valve

Abstract

To provide a compressor ring valve test method which can test a ring valve in an environment in which an operation condition of a compressor is reproduced, and a compressor ring valve test device.SOLUTION: A compressor ring valve test method for testing a compressor ring valve by using a ring valve test device comprises: an attachment step (S11) for attaching a ring valve to the ring valve test device including a simulated valve seat which is simulated with a valve seat of a compressor, a guide for guiding the ring valve, and a spring for energizing the ring valve toward the simulated valve seat; an impact force impartment step (S13) for imparting an impact force oriented in a separation direction separating from the simulated valve seat to the ring valve which is seated on the simulated valve seat by the execution of the attachment step; and a measurement step (S15) for measuring a parameter indicating a response of the ring valve which is imparted with the impact force.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present disclosure relates to a method for testing a compressor ring valve and a testing device for a compressor ring valve. [Background technology]

[0002] Compressors equipped with ring valves are known. For example, the compressor disclosed in Patent Document 1 includes a suction valve and a discharge valve. Both the suction valve and the discharge valve are configured to operate in response to pressure fluctuations in a compression chamber or the like provided in the compressor. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 5863135 Summary of the Invention [Problem to be solved by the invention]

[0004] According to the findings of the inventors, when a compressor is operating, the above-mentioned pressure fluctuations exert an impact force on a ring valve such as a suction valve or a discharge valve. If the phenomena related to the ring valve at this time can be clarified, it will be possible to design a ring valve that meets the specifications of the compressor. Therefore, it is desirable to test the ring valve in an environment that reproduces the operating conditions of the compressor.

[0005] An object of the present disclosure is to provide a method for testing a compressor ring valve and a testing device for a compressor ring valve that can perform testing in an environment that reproduces the operating conditions of the compressor. [Means for solving the problem]

[0006] A method for testing a compressor ring valve according to at least one embodiment of the present disclosure includes: A compressor ring valve testing method for testing a compressor ring valve using a ring valve testing device, comprising: an attachment step of attaching the ring valve to the ring valve testing device, the ring valve testing device including a simulated valve seat that simulates a valve seat of the compressor, a guide for guiding the ring valve, and a spring for biasing the ring valve toward the simulated valve seat; an impact force applying step of applying an impact force to the ring valve seated on the simulated valve seat by performing the mounting step in a direction in which the ring valve is separated from the simulated valve seat; a measuring step of measuring a parameter indicative of a response of the ring valve to which the impact force is applied; Equipped with.

[0007] A testing device for a compressor ring valve according to at least one embodiment of the present disclosure includes: a simulated valve seat that simulates a compressor valve seat; a guide for guiding a ring valve for a compressor; a spring for biasing the ring valve toward the simulated valve seat; an impact force applying unit configured to apply an impact force to the ring valve seated on the simulated valve seat in a direction away from the simulated valve seat; Equipped with. [Effects of the Invention]

[0008] According to the present disclosure, it is possible to provide a method for testing a compressor ring valve and a testing device for a compressor ring valve that can perform testing in an environment that reproduces the operating conditions of a compressor. [Brief explanation of the drawings]

[0009] [Figure 1] FIG. 1 is a conceptual cross-sectional view of a compressor according to an embodiment. [Figure 2] FIG. 1 is a conceptual explanatory diagram of a test device according to a first embodiment. [Figure 3] FIG. 1 is a conceptual diagram illustrating a test unit according to an embodiment. [Figure 4]1 is a flowchart of a method for testing a compressor ring valve according to an embodiment. [Figure 5] 10 is a conceptual graph of parameters illustrating the response of a discharge valve according to one embodiment. [Figure 6] FIG. 10 is a conceptual explanatory diagram of a test device according to a second embodiment. [Figure 7] FIG. 10 is a conceptual explanatory diagram of a partition operating portion according to another embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0010] Hereinafter, several embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of components described as embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the present disclosure. For example, expressions expressing relative or absolute arrangement such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial" not only express such an arrangement exactly, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained. For example, expressions such as "identical," "equal," and "homogeneous" that indicate that something is in an equal state not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained. For example, expressions representing shapes such as a square shape or a cylindrical shape not only represent shapes such as a square shape or a cylindrical shape in the strict geometric sense, but also represent shapes including uneven portions, chamfered portions, etc., to the extent that the same effect can be obtained. On the other hand, the expressions "comprise," "include," or "have" one element are not exclusive expressions that exclude the presence of other elements. Note that the same components will be denoted by the same reference numerals and the description thereof will be omitted.

[0011] <1. Overview of Reciprocating Compressor 10> FIG. 1 is a conceptual cross-sectional view of a reciprocating compressor 10 (hereinafter, sometimes referred to as "compressor 10") according to one embodiment of the present disclosure. The compressor 10 is incorporated into a refrigeration cycle including a plurality of heat exchangers, such as a condenser and an evaporator. Examples of the refrigeration cycle include a two-stage refrigeration cycle, a two-stage compression refrigeration cycle, and a reverse Brayton refrigeration cycle. In this case, the gas compressed by the compressor 10 is a refrigerant gas. In other embodiments, the compressor 10 may be incorporated into an internal combustion engine or the like, and the gas compressed by the compressor 10 may be combustion gas or the like.

[0012] A compressor 10 according to one embodiment of the present disclosure includes a crankcase 16 and a plurality of cylinders 40 housed in the crankcase 16. Each cylinder 40 defines a cylinder chamber Sc therein, in which a piston 42 is housed. Each piston 42 is connected to a crankshaft 48, which is supported by a bearing 50 provided in the crankcase 16, via a connecting rod 52 or the like. One end of the crankshaft 48 is connected to a motor 54, and each piston 42 can reciprocate within each cylinder 40 when driven by the motor 54. 1, a portion of the multiple cylinders 40, which may be, for example, four or eight, is omitted and only two cylinders 40 are shown as representatives. To reduce torque fluctuations of the crankshaft, the crank directions of the multiple cylinders 40 are changed. The pistons 42 in the cylinders 40 are connected to a crankshaft 48 so as to reciprocate in different phases.

[0013] A valve plate 44 is provided at one end of the cylinder 40 (the upper end of the cylinder 40 in FIG. 1 ) to support the discharge valve 12. A discharge valve seat 70, an example of a valve seat, is disposed inside an opening formed in the valve plate 44. The discharge valve seat 70 is connected to a valve cage 66 with bolts 68, and the discharge valve 12, which serves as a ring valve, is held between the discharge valve seat 70 and the valve cage 66. The valve cage 66, an example of a back seat, is biased toward the cylinder 40 by a head spring 64. The discharge valve 12 is also biased toward the discharge valve seat 70 by a valve spring 67 housed in a spring hole 69 provided in the valve cage 66. Furthermore, the valve cage 66 is provided with a discharge valve guide 56 to guide the reciprocating movement of the discharge valve 12. The discharge valve guide 56 is a wall surface extending circumferentially around the valve cage 66 and faces one radial side of the valve cage 66 (the radially inward side in the example of FIG. 1 ).

[0014] The compressor 10 according to an embodiment of the present disclosure further includes an intake valve 63 serving as a ring valve disposed around the cylinder 40, and an intake valve seat 61 configured to seat the intake valve 63. The intake valve seat 61 is an example of a valve seat. An intake back seat 71, an example of a back seat, is provided on the opposite side of the intake valve 63 from the intake valve seat 61. An intake valve guide 57 is provided on the intake back seat 71 to guide the reciprocating movement of the intake valve 63. In this embodiment, the intake valve guide 57 is a wall surface extending circumferentially around the intake back seat 71 and faces one radial side of the intake back seat 71 (the radially outer side in the example of FIG. 1). The compressor 10 may also include an intake valve spring (not shown) that presses the intake valve 63 against the intake valve seat 61. The intake valve spring has, for example, a plate shape that faces and contacts the intake valve 63 and is disposed between the intake valve 63 and the intake back seat 71.

[0015] The operation of the compressor 10 shown in FIG. 1 is outlined as follows. When the motor 54 is driven, the piston 42 descends, reducing the pressure in the sealed space within the cylinder chamber Sc. This causes the pressure in the suction space Si, formed outside the cylinder 40, to exceed the pressure in the sealed space by a certain amount. The suction valve 63, which was seated on the suction valve seat 61, is pushed up and collides with the suction back seat 71. At this time, gas in the suction space Si passes through the suction valve seat 61 and is drawn into the cylinder chamber Sc. The piston 42 then stops descending and begins to rise. The piston 42 compresses the gas, pressurizing the sealed space. As a result, the suction valve 63 is pushed down and seats on the suction valve seat 61. When the piston 42 continues to rise and the pressure in the sealed space exceeds the pressure in the discharge space Sd by a certain amount, the discharge valve 12 is pushed up from the discharge valve seat 70 and collides with the valve cage 66. At this time, the compressed gas in the cylinder chamber Sc is discharged into the discharge space Sd. When the piston 42 then starts to descend, the pressure in the sealed space of the cylinder chamber Sc is reduced, and the discharge valve 12 is biased by the valve spring 67 and seats on the discharge valve seat 70 .

[0016] When the compressor 10 of this embodiment operates as described above, the discharge valve 12 repeatedly collides with the discharge valve seat 70 and the valve cage 66, and the suction valve 63 repeatedly collides with the suction valve seat 61 and the suction back seat 71. The cycle of these collisions is the same as the cycle of the reciprocating motion of the piston 42. In other words, the discharge valve 12 and the suction valve 63 repeatedly collide with each other numerous times in a short period of time. If the stress generated in the valves during these collisions is excessive, the valves may be damaged. Therefore, in order for the compressor 10 to perform to its specified specifications, it is necessary to accurately grasp the stress generated in these valves due to collisions. It is also preferable to accurately grasp the velocity or inclination (attitude) of these valves when a collision occurs, and to utilize this information in designing valves that can withstand collisions. Therefore, in this disclosure, a testing apparatus 1 for compressor ring valves (hereinafter sometimes simply referred to as the "testing apparatus 1") is prepared. In the following description, a testing apparatus 1A(1) according to a first embodiment and a testing apparatus 1B(1) according to a second embodiment are prepared. Details of these apparatuses are described below.

[0017] 2. Testing Apparatus 1A According to First Embodiment 2-5, a testing apparatus 1A(1) according to a first embodiment configured to test a discharge valve 12 is illustrated. FIG. 2 is a conceptual diagram of the testing apparatus 1A(1) according to the first embodiment. FIG. 3 is a conceptual diagram of a unit under test 101A(101) according to an embodiment of the present disclosure. FIG. 4 is a flowchart of a method for testing a compressor ring valve according to an embodiment of the present disclosure. FIG. 5 is a conceptual graph of parameters showing the response of a discharge valve 12 according to an embodiment of the present disclosure.

[0018] As shown in Fig. 2, the testing apparatus 1A of this embodiment includes a supply source 20, an impact force application unit 80, and a test unit 101A (101). The supply source 20 stores a gas, which may be air, under high pressure. The supply source 20 may store a liquid instead of a gas. The liquid is converted into a gas as it is discharged from the supply source 20.

[0019] The impact force application unit 80 according to one embodiment of the present disclosure is a shock tube unit. The impact force application unit 80 includes a gas supply line 81 connected to the supply source 20 and a pipe 85 to which gas is supplied from the gas supply line 81. The gas supply line 81 illustrated in FIG. 2 is provided with, in order from upstream to downstream, a pressure regulating valve 89 and a shutoff valve 88. The pipe 85 includes a high-pressure pipe 85H configured to store gas supplied from the supply source 20 in a high-pressure state, and a low-pressure pipe 85L disposed downstream (on the right side in the example of FIG. 2) of the high-pressure pipe 85H. A high-pressure space Sh, which is the internal space of the high-pressure pipe 85H, and a low-pressure space Sl, which is the internal space of the low-pressure pipe 85L, are separated by a partition operating unit 87A (87). When the partition operating unit 87A is activated, the high-pressure space Sh and the low-pressure space Sl are connected to each other. For example, the partition operating unit 87A is an elastic sheet material configured to rupture upon activation. As a more specific example, the partition operating portion 87A is a membrane.

[0020] As illustrated in Fig. 3, a test unit 101A according to one embodiment of the present disclosure includes a simulated valve seat 105A (105) that simulates the discharge valve seat 70 (see Fig. 1) of the compressor 10, and a simulated valve back seat 109A (109) that simulates the valve cage 66. The simulated valve seat 105A and the simulated valve back seat 109A are arranged side by side with their respective axes parallel to each other, and the discharge valve 12 is disposed between these seats. The simulated valve seat 105A is connected to the downstream end (the right end in the example of Fig. 2) of the low-pressure pipe 85L and is configured to guide gas discharged from the low-pressure space Sl to the discharge valve 12.

[0021] The simulated valve seat 105A of this example is obtained by additionally machining the discharge valve seat 70 for the purpose of testing. As a specific example, the simulated valve seat 105A differs from the discharge valve seat 70 in that the simulated valve seat 105A has a seat hole 195 that opens toward the opposite side of the simulated valve back seat 109A. In this example, the shaft of the fastening member 115 that connects the simulated valve seat 105A and the simulated valve back seat 109A to each other is exposed through the seat hole 195. The fastening member 115 has a hole 115A that opens in the axial direction. The simulated valve back seat 109A of this example is also obtained by additionally machining the valve cage 66 for the purpose of testing. As a specific example, the simulated valve back seat 109A differs from the valve cage 66 in that the simulated valve back seat 109A has a back seat hole 199 that opens toward the opposite side of the simulated valve seat 105A.

[0022] The back seat hole 199 also opens toward the simulated valve seat 105A, and a non-contact sensor 160 is attached to the inside of the hole. The non-contact sensor 160 is configured to output a signal corresponding to the distance to the discharge valve 12, and is connected to an arithmetic unit 170 including a processor and a memory. One example of the non-contact sensor 160 is an eddy current displacement sensor. The non-contact sensor 160 may also be an ultrasonic sensor, a laser distance sensor, or the like.

[0023] The non-contact sensor 160 is configured to continuously output a signal. Therefore, the arithmetic device 170 can also obtain the speed of the reciprocating discharge valve 12 based on changes over time in the output result of the non-contact sensor 160. Furthermore, in this embodiment, although detailed illustration is omitted, a plurality of back seat holes 199 (more specifically, three) are provided along the circumferential direction of the simulated valve back seat 109A, and a non-contact sensor 160 is provided inside each back seat hole 199. Therefore, the arithmetic device 170 obtains the position of each of the plurality of parts that make up the discharge valve 12. In other words, the arithmetic device 170 can also obtain the inclination (attitude) of the reciprocating discharge valve 12.

[0024] The test unit 101A according to one embodiment of the present disclosure further includes a guide 106A (106) for guiding the discharge valve 12, and a spring 108A for biasing the discharge valve 12 toward the simulated valve seat 105A. The guide 106A has substantially the same shape as the previously described discharge valve guide 56 (see FIG. 1), and the spring 108A has substantially the same shape as the previously described valve spring 67 (see FIG. 1). With the above configuration, the test unit 101A can reproduce the environment in which the discharge valve 12 operates when the compressor 10 is in operation.

[0025] In this embodiment, at least one strain gauge 130 is provided on a seat surface 39A of the discharge valve 12, which is the surface facing the simulated valve seat 105A and opposite the spring 108A. More specifically, multiple strain gauges 130 are arranged at equal intervals around the circumferential direction of the discharge valve 12. For example, the number of strain gauges 130 is 10 or more. Each strain gauge 130 is connected to a computing device 170 via a wiring 136. The strain of the discharge valve 12 correlates with the stress generated in the discharge valve 12. Therefore, the computing device 170 can calculate the stress generated in the discharge valve 12 by measuring the strain generated in the discharge valve 12 based on the output result of at least one strain gauge 130. Note that a portion of the wiring 136 is arranged inside a hole 115A formed in the fastening member 115 described above, and the wiring 136 drawn out from the hole 115A is connected to the computing device 170.

[0026] Referring to FIG. 4, a method for testing a compressor ring valve using a testing apparatus 1A(1) to test a discharge valve 12 is illustrated. In the following description, steps may be abbreviated as "S." First, an installation step is performed to install the discharge valve 12 in the testing apparatus 1A (S11). Specifically, as shown in FIG. 3, the discharge valve 12 is disposed between a simulated valve seat 105A and a simulated valve back seat 109A, and is biased by a spring 108A. As a result, the discharge valve 12 is seated on the simulated valve seat 105A, completing the installation of the discharge valve 12. At this time, a plurality of strain gauges 130 are attached to the seat surface 39A of the discharge valve 12.

[0027] Next, as shown in FIG. 4, an impact force applying step is performed in which an impact force in a direction away from the simulated valve seat 105A is applied to the discharge valve 12 seated on the simulated valve seat 105A by performing the mounting step (S13).

[0028] For example, the partition actuation unit 87A illustrated in FIG. 2 is actuated, and the high-pressure space Sh and the low-pressure space Sl are connected to each other. In a more detailed example, in an embodiment in which the partition actuation unit 87A is a membrane, the membrane ruptures when the pressure difference between the high-pressure space Sh and the low-pressure space Sl exceeds a predetermined value. Gas flows instantaneously from the high-pressure pipe 85H to the low-pressure pipe 85L, and pressure is applied to the low-pressure space Sl (at this time, the pressure control valve 89 functions to adjust the rate of change in pressure in the high-pressure space Sh). A shock wave generated by the applied pressure is transmitted to the discharge valve 12 via the simulated valve seat 105. An impact force is applied to the seat surface 39A of the discharge valve 12 in the separation direction (arrow S), which moves the discharge valve 12 away from the simulated valve seat 105A. The discharge valve 12 moves in the separation direction while being guided by the guide 106A. The above-mentioned specified value, which is the pressure difference at which the membrane bursts, is determined according to, for example, the membrane thickness, hardness, or rigidity, etc. In other words, the pressure applied to the low-pressure space S1 is determined based on the characteristic values ​​of the membrane. In other embodiments, after the pressure in the high-pressure space Sh reaches a specified pressure by operating the pressure regulating valve 89, the partition operating unit 87A may be activated (for example, by rupturing the membrane with a heating wire or needle) to apply pressure to the low-pressure space Sl.

[0029] Immediately after the impact force is applied, the shutoff valve 88 switches from the open state to the closed state, and the application of the impact force to the discharge valve 12 ends. More specifically, the shutoff valve 88 switches to the closed state on the condition that a specified time has elapsed since the pressure gauge provided in the high-pressure pipe 85H began to drop. Therefore, it is preferable that the shutoff valve 88 be controlled by a controller (not shown).

[0030] 4, a measurement step is executed to measure parameters indicating the response of the discharge valve 12 to which an impact force is applied (S15). In this example, the strain of the discharge valve 12 and the position of the discharge valve 12 are measured as parameters indicating the response. The calculation device 170 acquires the strain of the discharge valve 12 based on the output result of the strain gauge 130, and acquires the position of the discharge valve 12 based on the output result of the non-contact sensor 160. This identifies the stress generated in the discharge valve 12 and the inclination (posture) and speed of the discharge valve 12 as it reciprocates.

[0031] Referring to FIG. 3, the operation of the discharge valve 12 during the measurement process will be described. The discharge valve 12, which has been separated from the simulated valve seat 105A by the application of an impact force, moves while being guided by the guide 106A against the biasing force of the spring 108A and collides with the simulated valve back seat 109A (in this example, the shutoff valve 88 has already switched to the closed state before this collision). The biasing force of the spring 108A then causes the direction of movement of the discharge valve 12 to change, and the discharge valve 12 begins to move in the opposite direction. As the discharge valve 12 moves in the opposite direction while being guided by the guide 106A, it collides with the simulated valve seat 105A. The discharge valve 12 then bounces back toward the simulated valve back seat 109A. In this way, the above parameters are measured as the discharge valve 12 successively collides with the simulated valve back seat 109A and the simulated valve seat 105A.

[0032] The measurement results of the parameters are conceptually shown in Figure 5. In this figure, the change over time in the impact force applied to the discharge valve 12 is shown in the upper graph. The change over time in the output result of the non-contact sensor 160 is shown in the middle graph, and the change over time in the output result of the strain gauge 130 is shown in the lower graph. In this embodiment, three non-contact sensors 160 and ten or more strain gauges 130 are provided, but in the conceptual diagram of Figure 5, only one representative measurement result of each is shown.

[0033] In the figure, tf indicates the activation timing of the shutoff valve 88, i.e., the timing at which application of the impact force to the discharge valve 12 ends. As described above, tf occurs before the timing (t1) at which the discharge valve 12, to which the impact force has been applied, switches its movement direction from the separating direction to the opposite direction. The controller (not shown) closes the shutoff valve 88 a specified time after detecting a pressure drop in the high-pressure space Sh based on the output of the pressure gauge. For example, this specified time is set to be greater than or equal to ¼ and less than or equal to ½ of the natural period of the test unit 101A, so that tf occurs before t1. The natural period can be calculated in advance based on the mass of the discharge valve 12, the impact force acting on the discharge valve 12, the spring constant of the spring 108A, and the like. In other embodiments, the specified time may be set to be greater than or equal to ¼ and less than or equal to ½ of the period of the piston 42 of the compressor 10. The shutoff valve 88 remains closed until the discharge valve 12 has completed its reciprocating movement and stopped. In other words, the application of the impact force is not resumed until the discharge valve 12 has finished reciprocating and stopped.

[0034] At t1, which indicates a timing later than tf, the discharge valve 12 collides with the simulated valve back seat 109A, and at the timing indicated by t2, the discharge valve 12 collides with the simulated valve seat 105A. The strain of the discharge valve 12 instantaneously peaks in response to each collision. Based on the output results of the strain gauge 130 and the non-contact sensor 160, the computing device 170 can acquire the stress generated in the discharge valve 12 when a collision occurs, the time from the application of the impact force to the collision of the discharge valve 12, and the tilt (posture) of the discharge valve 12 when the collision occurs. In other words, the events related to the discharge valve 12 when a collision occurs can be clarified.

[0035] According to the above configuration, when an impact force is applied to the discharge valve 12 attached to the testing apparatus 1A, the discharge valve 12 moves away from the simulated valve seat 105A and then collides with the simulated valve seat 105A due to the biasing force of the spring 108A. In the measurement step (S15), the strain of the discharge valve 12 and the position (velocity and inclination) of the discharge valve 12 are acquired as parameters indicating the response until the discharge valve 12 collides with the simulated valve seat 105A. This realizes a testing method for a compressor ring valve that can test the discharge valve 12 in an environment that reproduces the operating conditions of the compressor 10. The strain (stress) of the discharge valve 12 and the position (velocity and inclination) of the discharge valve 12, which are parameters acquired in the measurement step, are reflected in the design of the discharge valve 12, contributing to the development of a discharge valve 12 that can perform the desired function.

[0036] Furthermore, in the impact force applying step (S13), an impact force generated by application of pressure in the low-pressure space S1 is applied to the seat surface 39A of the discharge valve 12. According to the above configuration, the impact force generated by pressure fluctuations in the cylinder 40 when the actual compressor 10 is operating can be reproduced in the impact force applying step. Therefore, the operating conditions of the compressor 10 can be reproduced more faithfully. Furthermore, the inventors have confirmed that the discharge valve 12 can reciprocate in an inclined position when the compressor 10 is operating, and the operation of such a discharge valve 12 can be reproduced in the impact force applying step.

[0037] Furthermore, in the impact force application step (S13), application of the impact force ends before the discharge valve 12, which is moving in the separation direction, starts moving in the opposite direction. According to the inventors' findings, when the compressor 10 is actually operating, the discharge valve 12, which continues to move back and forth due to repeated pressure fluctuations inside the cylinder 40, tends to rotate circumferentially. With the above configuration, the time for applying the impact force to the discharge valve 12 is shortened, thereby suppressing circumferential rotation of the discharge valve 12, which may occur when an impact force is applied for a relatively long time. This allows for stable measurement of the discharge valve 12. For example, suppressing circumferential rotation of the discharge valve 12 can prevent tangling or breakage of the wiring 136 connected to the strain gauge 130. Therefore, stable strain measurement can be performed.

[0038] Furthermore, in the measurement step (S15), the strain occurring in the discharge valve 12 is measured as a parameter based on the output result of at least one strain gauge 130 attached to the discharge valve 12. According to the above configuration, the impact stress occurring in the discharge valve 12 can be acquired and can be used in the development of the discharge valve 12.

[0039] Furthermore, in the measurement step (S15), at least one strain gauge 130 is attached to the seat surface 39A of the discharge valve 12. With the above configuration, even if the discharge valve 12 rotates in the circumferential direction as the impact force application step is performed, interference between the wiring 136 attached to the strain gauge 130 and the spring 108A can be suppressed. Therefore, stable measurement can be performed.

[0040] In the measurement step (S15), the non-contact sensor 160 is used to measure at least one of the inclination and the speed of the discharge valve 12. According to the above configuration, it is possible to grasp the detailed behavior of the discharge valve 12 to which an impact force is applied, and this can be used in the development of the discharge valve 12.

[0041] <3. Testing Apparatus 1B According to Second Embodiment> Referring to Fig. 6, a test apparatus 1B(1) according to a second embodiment configured to test an intake valve 63 is illustrated. Fig. 6 is a schematic explanatory diagram of the test apparatus 1B according to the second embodiment. In the following, explanations of the configuration common to the test apparatus 1A will be omitted or simplified.

[0042] The test apparatus 1B includes a test unit 101B (101) instead of the test unit 101A (see FIG. 3). The test unit 101B includes a simulated valve seat 105B (105) that simulates the suction valve seat 61 of the compressor 10, a simulated valve back seat 109B (109) that simulates the suction back seat 71, and a guide 106B for guiding the reciprocating movement of the suction valve 63. The guide 106B has substantially the same shape as the suction valve guide 57 (see FIG. 1), and the simulated valve seat 105B has substantially the same shape as the suction valve seat 61. The simulated valve back seat 109B is obtained by additionally machining the suction back seat 71 for the test. Specifically, the simulated valve back seat 109B has a plurality of back seat holes 197 arranged circumferentially. A non-contact sensor 160 is provided in one of the plurality of back sheet holes 197, and a wire 136 connected to a strain gauge 130 is drawn out of another back sheet hole 197.

[0043] In this embodiment, at least one strain gauge 130 is provided on the back seat surface 38B, which is the surface of the intake valve 63 located between the simulated valve seat 105B and the simulated valve back seat 109B, opposite the simulated valve seat 105B. Wiring 136 connected to the strain gauge 130 is drawn out from inside the back seat hole 197 to the outside. When the intake valve 63 moves back and forth between the simulated valve seat 105B and the simulated valve back seat 109B, the strain gauge 130 enters the inside of the back seat hole 197, thereby avoiding collision between the strain gauge 130 and the simulated valve back seat 109B.

[0044] Furthermore, a spring (not shown) having the same shape as the intake valve spring (not shown) of compressor 10 may be provided between back seat surface 38B and simulated valve back seat 109B, away from strain gauge 130. This spring comes into contact with back seat surface 38B.

[0045] The test apparatus 1B can also apply an impact force to the intake valve 63 using the method described above. It is also possible to obtain strain, which is a parameter indicating the response of the intake valve 63 to which an impact force is applied, and the position (velocity and inclination) of the intake valve 63. To avoid duplication, detailed explanations thereof will be omitted.

[0046] At least one strain gauge 130 is attached to the back seat surface 38B. This configuration makes it possible to accurately measure the stress generated in the intake valve 63 that collides with at least one of the simulated valve back seat 109B and the simulated valve seat 105B during the impact force application step (S13). This can be used in the development of the intake valve 63.

[0047] 4. Examples of partition operating portion 87 according to other embodiments FIG. 7 is a conceptual explanatory diagram of a partition actuation unit 87B (87) according to another embodiment. The partition actuation unit 87B is a valve that separates the high-pressure space Sh from the low-pressure space Sl. More specifically, the partition actuation unit 87B (87) is a reciprocating spool valve that includes a sleeve 92, a spool 95 configured to reciprocate within the sleeve 92, and a spring 91 that connects the spool 95 within the sleeve 92. The sleeve 92 is connected to a branch line 99 that branches off from the gas supply line 81, and the internal pressure of the sleeve 92 can be adjusted by a pressure adjustment valve 98 provided in the branch line 99. When the actuation unit 97 of the partition actuation unit 87B is pressed and the spool 95 moves so as to increase the elastic deformation of the spring 91, the high-pressure space Sh and the low-pressure space Sl are connected to each other, and an impact force is applied to the discharge valve 12 or the suction valve 63. Immediately thereafter, the restoring force of the spring 91 causes the spool 95 to move in the opposite direction together with the operating part 97, and the high pressure space Sh and the low pressure space Sl become disconnected from each other. Note that the partition operating part 87B may be a rotary spool valve in which the spool 95 rotates around the axial direction of the sleeve 92, instead of being a reciprocating sleeve valve.

[0048] In the impact force application step (S13), an impact force is applied to the discharge valve 12 or the suction valve 63 by operating the partition operating unit 87B, which is a valve that separates the high-pressure space Sh and the low-pressure space Sl. According to the above configuration, impact forces can be applied to the discharge valve 12 or the suction valve 63 multiple times at desired timing. Therefore, there is no need to replace the membrane, and the response parameters of the discharge valve 12 can be obtained efficiently. This makes the test more efficient.

[0049] The present disclosure is not limited to the above-described embodiments. In the testing apparatus 1A according to the first embodiment, the strain gauge 130 may be attached to the surface of the discharge valve 12 opposite the seat surface 39A. Alternatively, in the testing apparatus 1B according to the second embodiment, the strain gauge 130 may be attached to the surface of the intake valve 63 opposite the back seat surface 38B. In this case, a seat valve hole (not shown) for arranging the wiring 136 of the strain gauge 130 may be provided by additionally machining the simulated valve seat 105B for the test. Furthermore, instead of applying pressure in the low-pressure space S1, an impulse hammer or a vibrator may be used to apply an impact force.

[0050] <5. Summary> The contents of the above-described embodiments can be understood, for example, as follows.

[0051] 1) A method for testing a compressor ring valve according to at least one embodiment of the present disclosure, comprising: A compressor ring valve testing method for testing compressor ring valves (discharge valve 12, suction valve 63) using a ring valve testing device (1), comprising: an attachment step (S11) of attaching the ring valve to the ring valve testing device (1) including a simulated valve seat (105) simulating a valve seat (discharge valve seat 70, suction valve seat 61) of a compressor (10), guides (106A, 106B) for guiding the ring valve, and a spring (108A) for biasing the ring valve toward the simulated valve seat; an impact force application step (S13) of applying an impact force to the ring valve seated on the simulated valve seat by performing the mounting step in a direction away from the simulated valve seat; a measuring step (S15) of measuring a parameter indicating a response of the ring valve to which the impact force is applied; Equipped with.

[0052] According to the configuration of 1) above, when an impact force is applied to a ring valve attached to a ring valve testing device, the ring valve separates from the simulated valve seat and then collides with the simulated valve seat due to the biasing force of the spring. In the measurement process, parameters indicating the response of the ring valve up to the point where it collides with the simulated valve seat are obtained. This realizes a testing method for compressor ring valves that can be tested in an environment that reproduces the operating conditions of a compressor. The parameters obtained in the measurement process are reflected in the design of the ring valve, contributing to the development of ring valves that can perform the desired functions.

[0053] 2) In some embodiments, the method for testing the compressor ring valve described in 1) above comprises the steps of: In the impact force applying step, the impact force generated by applying pressure is applied to a seat surface (39A) of the ring valve, which is the surface facing the simulated valve seat.

[0054] According to the configuration 2) above, the impact force generated by pressure fluctuations when an actual compressor is operating can be reproduced in the impact force applying step. Therefore, the operating conditions of the compressor can be reproduced more faithfully. For example, the inventors have confirmed that the ring valve reciprocates in an inclined position when the compressor is operating, and the impact force applying step can reproduce this type of ring valve movement.

[0055] 3) In some embodiments, the method for testing a compressor ring valve according to 1) or 2) above comprises: In the impact force applying step, the application of the impact force is completed before the ring valve moving in the separating direction starts to move in the opposite direction.

[0056] According to the findings of the inventors, when an actual compressor is operating, the ring valve tends to rotate in the circumferential direction due to intermittent pressure fluctuations. The configuration of 3) above shortens the time during which an impact force is applied to the ring valve. Therefore, it is possible to suppress the circumferential rotation of the ring valve, which can occur when an impact force is applied over a relatively long period of time. This facilitates testing of the ring valve.

[0057] 4) In some embodiments, the method for testing a compressor ring valve according to any one of 1) to 3) above, In the impact force applying step, the impact force is applied by operating a valve (partition operating portion 87B) that separates the high pressure space (Sh) and the low pressure space (Sl).

[0058] According to the above configuration 4), impact force can be applied to the ring valve multiple times at desired timing, thereby improving the efficiency of the test.

[0059] 5) In some embodiments, the method for testing a compressor ring valve according to any one of 1) to 4) above, In the measuring step, the strain occurring in the ring valve is measured as the parameter based on the output result of at least one strain gauge (130) attached to the ring valve.

[0060] According to the above configuration 5), the impact stress generated in the ring valve when a collision occurs can be obtained, and this can be used for the development of ring valves.

[0061] 6) In some embodiments, the method for testing the compressor ring valve described in 5) above comprises: In the measuring step, the at least one strain gauge is attached to a back seat surface (38B) of the ring valve, which is a surface facing the simulated valve seat and located on the opposite side to the spring.

[0062] According to the above configuration 6), even when the ring valve rotates in the circumferential direction as the impact force application process is performed, interference between the wiring (136) attached to the strain gauge and the spring can be suppressed.

[0063] 7) In some embodiments, the method for testing the compressor ring valve described in 5) above, comprising: In the mounting step, the ring valve is mounted in the ring valve testing device including a simulated valve back seat (109) arranged in line with the simulated valve seat; In the measuring step, the at least one strain gauge is attached to a back seat surface (38B) of the ring valve, which is on the simulated valve back seat side and is in contact with the spring.

[0064] According to the above configuration 7), the stress generated in the ring valve that collides with the simulated valve back seat as the impact force application process is performed can be accurately measured. Therefore, it can be used for the development of ring valves.

[0065] 8) In some embodiments, the method for testing a compressor ring valve according to any one of 1) to 7) above, further comprising: In the measuring step, at least one of the inclination and the speed of the ring valve is measured using a non-contact sensor (160).

[0066] According to the above configuration 8), it is possible to grasp the detailed behavior of the ring valve when an impact force is applied, and this can be utilized in the development of ring valves.

[0067] 9) Testing device for compressor ring valves according to at least one embodiment of the present disclosure (1) a simulated valve seat (105) that simulates the valve seats (discharge valve seat 70, suction valve seat 61) of the compressor (10); Guides (106A, 106B) for guiding compressor ring valves (discharge valve 12, suction valve 63); a spring (108A) for biasing the valve seat toward the simulated valve seat; an impact force applying unit (80) configured to apply an impact force to the ring valve seated on the simulated valve seat in a direction away from the simulated valve seat; Equipped with.

[0068] According to the configuration of 9) above, when an impact force is applied to the ring valve seated on the simulated valve seat, the ring valve separates from the simulated valve seat and then collides with the simulated valve seat due to the biasing force of the spring. This realizes a ring valve testing device (1) that can perform testing under an environment that reproduces the operating conditions of a compressor. [Explanation of symbols]

[0069] 1: Compressor ring valve test equipment (test equipment) 10: Compressor 12: Discharge valve (ring valve) 38B: Back sheet surface 39A: Seat surface 80: Impact force applying part 105: Simulated valve seat 106A: Guide 106B: Guide 108: Spring 109: Simulated valve back seat 130: Strain gauge Sh: High pressure space Sl: Low pressure space

Claims

1. A compressor ring valve testing method for testing a compressor ring valve using a ring valve testing device, comprising: an attachment step of attaching the ring valve to the ring valve testing device, the ring valve testing device including a simulated valve seat that simulates a valve seat of a compressor, a guide for guiding the ring valve, and a spring for biasing the ring valve toward the simulated valve seat; an impact force applying step of applying an impact force to the ring valve seated on the simulated valve seat by performing the mounting step in a direction in which the ring valve is separated from the simulated valve seat; a measuring step of measuring a parameter indicative of a response of the ring valve to which the impact force is applied; Equipped with In the impact force application step, the ring valve is guided by the guide surface that extends in the circumferential direction and faces one radial direction, and the ring valve is moved in the separation direction by the impact force against the biasing force of the spring. Test methods for compressor ring valves.

2. In the impact force application step, the impact force generated by the application of pressure is applied to a seat surface of the ring valve, which is a surface facing the simulated valve seat. The method for testing a compressor ring valve according to claim 1.

3. In the impact force application step, application of the impact force is completed before the ring valve moving in the separating direction starts to move in the opposite direction.

3. A method for testing a compressor ring valve according to claim 1 or 2.

4. In the impact force application step, the impact force is applied by operating a valve that separates a high-pressure space from a low-pressure space. A method for testing a compressor ring valve according to any one of claims 1 to 3.

5. In the measuring step, a strain generated in the ring valve is measured as the parameter based on an output result of at least one strain gauge attached to the ring valve. A method for testing a compressor ring valve according to any one of claims 1 to 4.

6. In the measuring step, the at least one strain gauge is attached to a back seat surface of the ring valve, which is a surface facing the simulated valve seat and located on the opposite side from the spring. The method for testing a compressor ring valve according to claim 5.

7. In the mounting step, the ring valve is mounted in the ring valve testing device including a simulated valve back seat arranged in line with the simulated valve seat; In the measuring step, the at least one strain gauge is attached to a back seat surface of the ring valve, which is a surface on the simulated valve back seat side and is in contact with the spring. The method for testing a compressor ring valve according to claim 5.

8. In the measuring step, at least one of the inclination and the velocity of the ring valve is measured using a non-contact sensor. A method for testing a compressor ring valve according to any one of claims 1 to 7.

9. a simulated valve seat that simulates a compressor valve seat; a guide for guiding a ring valve for a compressor; a spring for biasing the ring valve toward the simulated valve seat; an impact force applying unit configured to apply an impact force to the ring valve seated on the simulated valve seat in a direction away from the simulated valve seat; Equipped with The guide has a surface that extends in a circumferential direction and faces one side in a radial direction, The impact force applying unit is configured to apply the impact force to the ring valve so that the ring valve moves in the separation direction by the impact force against the biasing force of the spring while being guided by the surface of the guide. Test equipment for compressor ring valves.

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