JP7708640B2 - Wear test method and wear test device for compressor ring valve - Google Patents

Description

This disclosure relates to a wear test method and a wear test device for compressor ring valves.

The wear testing device disclosed in Patent Document 1 makes it possible to evaluate the wear resistance of seal rings installed in automobile transmissions. The device is equipped with a seal ring as a test specimen, a disk against which the seal ring is pressed, and a rotating shaft connected to the disk. When the rotating shaft rotates, the disk rotates relative to the seal ring. The seal ring wears due to the sliding that occurs between the seal ring and the disk.

JP 2002-161981 A

Instead of a seal ring, a compressor ring valve may be used as a test specimen. To accurately evaluate the wear resistance of this ring valve, it is preferable for the wear test device to reproduce the behavior of the ring valve when the compressor is operating. However, such a configuration is not disclosed in the above patent document.

The objective of this disclosure is to provide a wear test method and a wear test device for compressor ring valves that can accurately evaluate the wear resistance of the ring valves.

A method for wear testing of a compressor ring valve according to at least one embodiment of the present disclosure includes:
a step of holding a compressor ring valve inclined relative to a simulated valve seat simulating a valve seat for a compressor such that a portion of a circumferential direction of one side of the ring valve is in partial contact with the simulated valve seat;
The method includes a step of moving the ring valve relative to the simulated valve sheet so that a portion of the one side that comes into contact with the simulated valve sheet slides against the simulated valve sheet and the portion of the one side that comes into contact with the simulated valve sheet changes in the circumferential direction.

According to at least one embodiment of the present disclosure, a compressor ring valve wear testing apparatus includes:
A first shaft;
A second shaft configured to rotate in conjunction with the first shaft while being inclined relative to the first shaft;
A simulated valve seat that is provided coaxially with the first shaft and simulates a valve seat for a compressor;
a ring valve holding portion for holding the compressor ring valve such that one side of the ring valve is in partial contact with the simulated valve seat;
a driving source for rotating the first shaft and the second shaft so that a portion of the one side that comes into contact with the simulated valve seat slides against the simulated valve seat and the portion of the one side that comes into contact with the simulated valve seat changes in the circumferential direction of the ring valve.

The present disclosure provides a wear test method and a wear test device for compressor ring valves that can accurately evaluate the wear resistance of the ring valves.

FIG. 1 is a conceptual cross-sectional view of a reciprocating compressor according to one embodiment. FIG. 2 is a schematic perspective view of an intake valve seat and an intake valve according to an embodiment. 1 is a schematic cross-sectional view of a wear testing device according to a first embodiment. FIG. 4 is an explanatory diagram illustrating the behavior of a ring valve in a wear test according to one embodiment. FIG. 5 is a schematic cross-sectional view of a wear testing device according to a second embodiment. 1 is a flowchart illustrating a wear test method according to an embodiment.

Hereinafter, some 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 the 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 configuration, such as "in a certain direction,""along a certain direction,""parallel,""orthogonal,""center,""concentric," or "coaxial," not only strictly express such a configuration, 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 indicating that things are in an equal state, such as "identical,""equal," and "homogeneous," 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 describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained.
On the other hand, the expressions "comprise", "include", or "have" a certain element are not exclusive expressions excluding the presence of other elements.
In addition, the same components are denoted by the same reference numerals and the description thereof may be omitted.

1. Overview of Compressor 10
1 is a conceptual cross-sectional view of a compressor 10 according to an 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 another embodiment, the compressor 10 may be incorporated into an internal combustion engine or the like, and the gas compressed by the compressor 10 may be a combustion gas.

The compressor 10 according to one embodiment of the present disclosure is a reciprocating compressor. The compressor 10 includes a crankcase 16 and a plurality of cylinder sleeves 40 housed in the crankcase 16. Each cylinder sleeve 40 defines a cylinder chamber Sc inside in which a piston 42 is housed. Each piston 42 is connected to a crankshaft 48 supported by a thrust bearing 50 provided in the crankcase 16 via a connecting rod 52 and a crank pin 53. In addition, one end of the crankshaft 48 is connected to a motor 54, and each piston 42 can reciprocate inside each cylinder sleeve 40 by driving the motor 54.

In the exemplary embodiment shown in FIG. 1, two cylinder sleeves 40 are provided in parallel, and the pistons 42 of the two cylinder sleeves 40 are connected to the crankshaft 48 so as to reciprocate in phases that are 180° apart in the rotation angle of the crankshaft 48.

A support plate 44 is provided at one end of the cylinder sleeve 40 (the upper end of the cylinder sleeve 40 in FIG. 1) to support the discharge valve 67. A truncated cone-shaped valve plate 70 is disposed inside an opening formed in the support plate 44. The valve plate 70 is connected to a valve cage 66 by bolts 68, and the discharge valve 67 is held between the valve plate 70 and the valve cage 66. The valve cage 66 is biased toward the cylinder sleeve 40 by a coil spring 64. The discharge valve 67 is also biased toward the valve plate 70 by a valve spring (not shown) housed in a spring hole 69 provided in the valve cage 66.

The compressor 10 according to one embodiment of the present disclosure further includes a suction valve 63 provided around the cylinder chamber Sc of the cylinder sleeve 40, and a suction valve seat 61 configured to seat the suction valve 63. The suction valve 63 is an O-ring shape that extends continuously in the circumferential direction based on the axis of the cylinder sleeve 40. The suction valve seat 61 of this embodiment includes an opposing surface that faces the suction valve 63, and a raised portion 61P that is an area that is raised toward the suction valve 63 is formed on the opposing surface. One side of the suction valve 63 partially contacts the raised portion 61P.

The operation of the compressor 10 shown in FIG. 1 to draw in and compress gas is as follows. When the motor 54 is driven and the piston 42 descends to reduce the pressure of the cylinder chamber Sc in the cylinder sleeve 40, the pressure of the suction space Si formed outside the cylinder sleeve 40 exceeds the pressure of the cylinder chamber Sc to a certain extent. The suction valve 63 seated on the suction valve seat 61 is pushed up, and the gas sucked in the suction space Si flows into the cylinder chamber Sc through the suction valve seat 61. The piston 42 then stops descending and starts to rise. The gas is compressed by the piston 42 and the cylinder chamber Sc is pressurized, so that the suction valve 63 is pushed down and seats on the suction valve seat 61. When the piston 42 further rises and the pressure of the cylinder chamber Sc exceeds the pressure of the discharge space Sd to a certain extent, the discharge valve 67 is pushed up and the compressed gas in the cylinder chamber Sc is discharged into the discharge space Sd.

<2. Behavior of the suction valve 63 before it is seated>
Referring to Fig. 2, a detailed example of the behavior of the suction valve 63 before it is seated according to an embodiment of the present disclosure is illustrated. Fig. 2 is a perspective view that shows a schematic view of the suction valve seat 61 and the suction valve 63. Note that Fig. 2 omits the above-mentioned raised portion 61P of the suction valve seat 61.

When the suction valve 63, which is raised from the suction valve seat 61, is pushed down, the pressure difference between the gas pressure in the cylinder chamber Sc and the gas pressure in the suction space Si is not strictly uniform in the circumferential direction of the suction valve 63. Therefore, the suction valve 63 is pushed down in an inclined position with respect to the axial direction of the cylinder sleeve 40. At this time, bending stress occurs in the suction valve 63 due to the pressure acting on the suction valve 63, and the suction valve 63 bends so that its inner part is positioned on the suction valve seat 61 side (arrow B). Therefore, when the suction valve 63 starts to contact the suction valve seat 61, one side 63A of the suction valve 63 (the lower surface of the suction valve 63 in FIG. 2) comes into contact with the suction valve seat 61. In other words, a part of the one side 63A of the suction valve 63 comes into contact with the suction valve seat 61. Part of the reaction force acting on the suction valve 63 due to the partial contact becomes a rotational force that rotates the suction valve 63 in the circumferential direction (arrow R). The contact portion 63P on the one side 63A changes as the suction valve 63 rotates. The suction valve 63 gradually falls as it rotates, and then comes into contact with the suction valve seat 61 in a position facing the suction valve seat 61. As a result, the suction valve 63 stops rotating and seats on the suction valve seat 61. Note that while the suction valve 63 slides against the suction valve seat 61, it may move in a radial direction based on the axis of the suction valve seat 61. In other words, the suction valve 63 may move relative to the suction valve seat 61 not only in the circumferential direction of the suction valve seat 61 but also in the radial direction.

While the compressor 10 is operating, the suction valve 63 repeats the above behavior each time it changes from a raised state to a seated state. Therefore, one side 63A of the suction valve 63 and the suction valve seat 61 repeatedly slide against each other, gradually wearing down the one side 63A. To accurately evaluate whether the suction valve 63 has a wear resistance equal to or higher than the required level, it is preferable to conduct a wear test that reproduces the above behavior of the suction valve 63 when the compressor 10 is operating.

Compressor oil may be mixed into the gas sucked into the compressor 10. In this case, compressor oil is interposed between one side 63A of the suction valve seat 61 and the raised portion 61P of the suction valve seat 61, reducing wear on the suction valve 63.

In addition, the compressor 10 according to another embodiment may include a stopper mechanism (not shown) for preventing (restricting) the rotation of the suction valve 63. As an example, the stopper mechanism may include a convex portion provided on the outer peripheral end of the suction valve 63 and a concave portion fixed to fit into the convex portion. Alternatively, the stopper mechanism may include a through hole provided in the suction valve 63 and a pin fixed to be inserted into the through hole. The through hole is opened in the axial direction of the suction valve 63. The provision of the stopper mechanism suppresses the above-mentioned rotational movement of the suction valve 63. However, even in this case, a clearance is inevitably formed between the two members that fit together, so the rotation of the suction valve 63 before it is seated is not completely eliminated.

Furthermore, the compressor 10 according to another embodiment may include a suction valve spring (not shown) that presses the suction valve 63 against the suction valve seat 61. The suction valve spring has a plate shape that faces and contacts the suction valve 63. Even in this case, the rotation of the suction valve 63 before it seats does not disappear completely. The biasing force applied from the suction valve spring to the suction valve 63 may act as a bending stress on the suction valve 63 (arrow B in FIG. 2). As the bending stress increases, the area of one side 63A of the suction valve 63 that corresponds to the partial contact portion 63P may increase.

<3. Wear test device 1 for compressor ring valve>
A wear test apparatus 1 for a compressor ring valve according to one embodiment of the present disclosure (hereinafter, may be simply referred to as "wear test apparatus 1") will be described. Below, a wear test apparatus 1A(1) according to a first embodiment and a wear test apparatus 1B(1) according to a second embodiment will be described in order.

<3-1. Wear test device 1A for compressor ring valve according to the first embodiment>
Fig. 3 is a schematic cross-sectional view of the wear test apparatus 1A. Fig. 4 is an explanatory diagram showing a schematic behavior of a compressor ring valve 15 evaluated by the wear test apparatus 1A. In this embodiment, as an example, the compressor ring valve 15 (hereinafter, may be simply referred to as "ring valve 15") is the suction valve 63 of the compressor 10 described above.

As illustrated in FIG. 3, the wear test device 1A (1) according to the first embodiment includes a horizontally extending support base 72, a first shaft 11A (11) connected to the support base 72 via a number of bearings 98, a simulated valve seat 21A (21) arranged coaxially with the first shaft 11A, and a second shaft 12A (12) configured to rotate in conjunction with the first shaft 11A while being inclined relative to the first shaft 11A.

The first shaft 11A is rotatable with respect to the support base 72 and extends parallel to the vertical direction. The simulated valve sheet 21A imitates the suction valve sheet 61 (see FIG. 1), which is an example of a valve sheet for a compressor. In this example, the suction valve sheet 61 that has been additionally machined for testing corresponds to the simulated valve sheet 21A. The simulated valve sheet 21A is fixed to the support base 72. The simulated valve sheet 21A also includes an opposing surface 21F that faces one side of the axial direction of the first shaft 11A (the upper side in the example of FIG. 3). The opposing surface 21F is formed with a raised portion 21P, which is a raised area. Both the opposing surface 21F and the raised portion 21P are O-ring-shaped with the first shaft 11 at the center. The second shaft 12A in this example extends at an angle with respect to the vertical direction. The second shaft 12A is also directly connected to one end of the first shaft 11A. As a more specific example, the second shaft 12A is fixed to the first shaft 11A by a fastening member (not shown). Note that the second shaft 12A may be formed integrally with the first shaft 11A.

The wear test device 1A of this embodiment further includes a ring valve holder 29A (29) configured to hold a compressor ring valve 15. The ring valve holder 29A is rotatably connected to the second shaft 12A. The ring valve 15 held by the ring valve holder 29A is located on one side of the axial direction of the first shaft 11A with respect to the simulated valve seat 21A, and faces the opposing surface 21F of the simulated valve seat 21A. The ring valve 15 is also coaxial with the second shaft 12A and inclined with respect to the axis L1 of the first shaft 11A. As a result, one side 15A of the ring valve 15 comes into contact with the above-mentioned raised portion 21P of the opposing surface 21F.

An example of a specific structure that allows the ring valve holder 29 to rotate relative to the second shaft 12A is as follows. The ring valve holder 29A includes a base 295 that is connected to the first shaft 11A via a bearing 97, a first holder 291 that is fixed to the base 295 by a plurality of first fastening members 91, and a second holder 292 that is fixed to the first holder 291 by a plurality of second fastening members 92. The first holder 291 and the second holder 292 face each other and contact each other. Since the bearing 97 is interposed between the base 295 and the second shaft 12A, the ring valve holder 29 is rotatable relative to the second shaft 12A.

An example of a specific structure in which the ring valve holding portion 29A holds the ring valve 15 is as follows.
A recess 289 is formed on the outer end of the first holder 291 in the radial direction based on the second shaft 12A. This recess 289 is recessed in the axial direction of the second shaft 12A in a direction away from the second holder 292. The shape of the recess 289 is an O-ring shape when viewed in the axial direction of the second shaft 12A. The recess 289 accommodates the inner part of the ring valve 15. The part of the ring valve 15 accommodated in the recess 289 is sandwiched between the first holder 291 and the second holder 292. The axial direction of the ring valve 15 held in this manner coincides with the axial direction of the first shaft 11A. One side 15A of the ring valve 15 is in one-sided contact with the raised portion 21P of the simulation valve sheet 21A.

To replace the ring valve 15 with another ring valve 15, the second fastening member 92 is removed and the second holder 292 is detached from the first holder 291. This allows the held ring valve 15 to be removed from the ring valve holding portion 29A. The new O-ring-shaped ring valve 15 is then positioned so that its inner end abuts the recess 289. After the ring valve 15 housed in the recess 289 is sandwiched between the second holder 292, the second holder 292 is fixed to the first holder 291 by the second fastening member 92. This completes the replacement of the ring valve 15, and the ring valve holding portion 29 can hold the new ring valve 15.

The wear test device 1A of this embodiment further includes a driving source 30. The driving source 30 is a motor configured to rotate the first shaft 11A and the second shaft 12A. In this example, the driving source 30 is connected to the first shaft 11A. When the driving source 30 applies a driving force to the first shaft 11A, the first shaft 11A rotates around the axis L1, and the second shaft 12A revolves around the axis L1 of the first shaft 11A. Therefore, the ring valve 15 held by the ring valve holding portion 29A revolves around the axis L1 in an inclined position relative to the first shaft 11A.

When the ring valve 15 rotates around the axis L1 together with the ring valve holding portion 29A, the contact portion 15P of the ring valve 15 slides against the raised portion 21P (see FIG. 4). Note that in FIG. 4, which is a schematic diagram of the first shaft 11 as viewed in the axial direction, the axis L2 of the second shaft 12 is indicated by a dot for the purpose of simplified illustration.

As illustrated in FIG. 4, as the ring valve 15 rotates about the axis L1, the contact portion 15P slides against the raised portion 21P of the simulated valve seat 21. The frictional force generated between the contact portion 15P and the raised portion 21P due to the sliding causes the ring valve 15 to rotate about the axis L2 (arrow R). Therefore, the portion of one side 15A of the ring valve 15 that corresponds to the contact portion 15P changes in the circumferential direction of the ring valve 15 as it rotates. This relative movement of the tilted ring valve 15 with respect to the simulated valve seat 21 is similar to the relative movement of the suction valve 63 with respect to the suction valve seat 61 described above.

According to the above configuration, since the second shaft 12A is inclined relative to the first shaft 11A, when the drive source 30 is driven, the ring valve 15 inclined relative to the simulated valve seat 21A rotates around the axis L1 of the first shaft 11A. This rotation allows the contact portion 15P of one side 15A of the ring valve 15 that contacts the simulated valve seat 21 to slide against the simulated valve seat 21, and the ring valve 15 can move relative to the simulated valve seat 21 so that the contact portion 15P on one side 15A of the ring valve 15 changes in the circumferential direction. As a result, the wear test device 1A can reproduce the behavior of the ring valve 15 while the compressor 10 is operating, and can slide one side 15A of the ring valve 15 against the simulated valve seat 21A. Therefore, the wear test device 1A that can accurately evaluate the wear resistance of the ring valve 15 is realized.

Returning to FIG. 3, in one embodiment of the present disclosure, a stopper 87 for preventing rotation of the ring valve holding portion 29A around the second shaft 12A may be selectively installed depending on, for example, the test conditions. The stopper 87 is swingably connected to the fixed plate 25 extending horizontally as an example. The fixed plate 25 is supported by the fixed base 24. In an embodiment in which the stopper 87 is provided, even if the second shaft 12A rotates, the rotation of the ring valve holding portion 29A and the ring valve 15 around the axis L2 is prevented. In other words, the stopper 87 applies a braking force to the ring valve 15 that prevents rotation around the axis of the ring valve 15. However, even in this case, the ring valve 15 can rotate around the axis L1 together with the second shaft 12A as the first shaft 11A rotates. Since the rotation of the ring valve 15 around the axis L2 of the second shaft 12 is prevented, the behavior of the suction valve 63 when the compressor 10 is provided with the above-mentioned stopper mechanism can be reproduced.

The wear test device 1A may further include a biasing means 35 for biasing the ring valve holding portion 29A toward the simulated valve seat 21. In this embodiment, the biasing means 35 is a stud bolt that presses the fixed plate 25 toward the fixed base 24. In other embodiments, the biasing means 35 may be a spring interposed between the fixed plate 25 and the stopper 87. The biasing means 35 may also directly bias the ring valve holding portion 29A.

With the above configuration, the contact portion 15P of the ring valve 15 presses against the simulated valve sheet 21A, increasing the frictional force generated by the contact portion 15P sliding against the simulated valve sheet 21A, and accelerating the progression of wear on the one side 15A. Therefore, the wear resistance of the ring valve 15 can be accurately evaluated in a short time.

In this embodiment, the second shaft 12A is eccentric with respect to the first shaft 11A. In the example of FIG. 3, the amount of eccentricity of the second shaft 12A with respect to the first shaft 11A corresponds to dimension E. In this case, as shown in FIG. 4, the ring valve 15 moves relative to the simulated valve seat 21 in the radial direction based on the axis of the simulated valve seat 21A (i.e., the axis L1 of the first shaft 11A). Therefore, the radial distance between the ring valve 15 and the axis L1 changes as the ring valve 15 rotates. This increases the amount of sliding of the contact portion 15P against the simulated valve seat 21A, so that the wear resistance of the ring valve 15 can be accurately evaluated in a short time. In addition, the behavior of the suction valve 63 moving radially relative to the suction valve seat 61 in the compressor 10 can be reproduced.

In addition, in this embodiment, the simulated valve sheet 21A is fixed in a specified position and does not rotate or pivot when driven by the drive source 30. In this example, the simulated valve sheet 21A is fixed to the support base 72 by multiple fastening members. With the above configuration, the drive mechanism for moving the simulated valve sheet 21A and the ring valve 15 is not required, so the wear test device 1A can be simplified.

In addition, in this embodiment, the second shaft 12B is directly connected to the first shaft 11B, and the ring valve holder 29A is connected to the second shaft 12B via a bearing 97. By simply adopting a configuration in which the ring valve holder 29A is connected via a bearing 97 to the second shaft 12A, which is directly connected to the first shaft 11A, the contact portion 15P of the ring valve 15 slides against the simulated valve seat 21A, and the contact portion 15P on one side 15A of the ring valve 15 moves in the circumferential direction. This simplifies the wear test device 1A.

<3-2. Abrasion testing device 1B according to the second embodiment>
An abrasion test apparatus 1B(1) according to a second embodiment is illustrated with reference to Fig. 5. Fig. 5 is a schematic cross-sectional view of the abrasion test apparatus 1B according to the second embodiment.

The wear test device 1B includes a first support stand 31 and a first shaft 11B (11) connected to the first support stand 31 via a plurality of bearings 39. A simulated valve sheet 21B (21) is fixed to one end of the first shaft 11B, for example, by a fastening member 59. The simulated valve sheet 21B, which is coaxial with the first shaft 11B, includes an opposing surface 21F that faces the ring valve 15 and a raised portion 21P that is a raised area of the opposing surface 21F. The raised portion 21P in the second embodiment is an O-ring shape centered on the axis M1 of the first shaft 11.

The wear test device 1B further includes a second support stand 32, a second shaft 12B connected to the second support stand 32 via a plurality of bearings 38, and a ring valve holder 29B (29) fixed to the second shaft 12B. The second shaft 12B is inclined and eccentric with respect to the first shaft 11B. The ring valve 15 held by the ring valve holder 29B is held so that one side 15A of the ring valve 15 abuts on the raised portion 21P of the simulated valve seat 21B. The ring valve 15 is fixed to the ring valve holder 29B by a fastening member not shown. Although not shown in detail, the second support stand 32 may be supported by another support stand so that it can rotate around the axis M1 of the first shaft 11B.

The wear test device 1B further includes a drive source 30 connected to the first shaft 11B. When the drive source 30 is driven, the simulated valve sheet 21B rotates together with the first shaft 11B. A rotational force centered on the axis M1 of the first shaft 11B is transmitted from the simulated valve sheet 21B to the ring valve 15. As a result, the ring valve 15 rotates together with the ring valve holder 29B and the second shaft 12B around the axis M1. In other words, the ring valve 15, the ring valve holder 29B, and the second shaft 12B are driven by the simulated valve sheet 21, which is driven to rotate. In addition, due to the frictional force generated between the raised portion 21P and one side 15A of the ring valve 15, the ring valve 15 rotates together with the ring valve holder 29B and the second shaft 12B around the axis M2 of the second shaft 12B. If no slippage occurs between the ring valve 15 and the simulated valve seat 21, the rotation speed of the second shaft 12B about its axis M2 is the same as the rotation speed of the first shaft 11B about its axis M1. If slippage occurs, the rotation speed of the second shaft 12B is slower than the rotation speed of the first shaft 11B.

Based on the above principle, the ring valve 15 behaves in the same manner as described with reference to FIG. 4. In other words, the contact portion 15P on one side 15A that contacts the simulated valve sheet 21B slides against the simulated valve sheet 21B, and the contact portion 15P on one side 15A changes in the circumferential direction of the ring valve 15. The speed at which the contact portion 15P on one side 15A changes in the circumferential direction is the same as the rotation speed of the second shaft 12B.

The wear test apparatus 1B according to the second embodiment described above can accurately evaluate the wear resistance of the ring valve 15, similar to the wear test apparatus 1B according to the first embodiment. The second shaft 12B shown in FIG. 5 may not be eccentric with respect to the first shaft 11B, but may only be inclined with respect to the first shaft 11B. The biasing means 35 already described with reference to FIG. 3 may also be provided in the wear test apparatus 1B.

In this embodiment, the simulated valve sheet 21B is fixed to the first shaft 11B. The ring valve holder 29B is fixed to the second shaft 12B, and one side 15A of the ring valve 15 held by the ring valve holder 29B comes into contact with the simulated valve sheet 21. The ring valve 15 is driven by the rotationally driven simulated valve sheet 21B, and the ring valve 15 performs the above-mentioned relative movement with respect to the simulated valve sheet 21.

According to the above configuration, to change the conditions of the wear test, it is sufficient to change the configuration of either the support mechanism such as the first support base 31 for supporting the simulated valve seat 21B so that it can be rotated, or the support mechanism such as the second support base 32 for supporting the ring valve 15 so that it can be rotated. For example, by changing the position and tilt attitude of the first support base 31, it is possible to adjust both the eccentricity and tilt angle of the second shaft 12B relative to the first shaft 11B. This realizes a wear test device 1B with a high degree of freedom in changing the test conditions.

The wear test device 1B illustrated in FIG. 5 may also include a joint 88 that is connected to the first shaft 11B and the second shaft 12B. The joint 88 is a universal joint or a shaft joint. By providing the joint 88, the first shaft 11B and the second shaft 12B can rotate at the same speed.

According to the above configuration, even if the sliding state of the ring valve 15 against the simulated valve sheet 21B changes due to the ring valve 15 sliding against the raised portion 21P of the simulated valve sheet 21, the rotation speed of the second shaft 12B and the rotation speed of the first shaft 11B can be prevented from shifting from each other. Therefore, the rotation speed of the ring valve 15 about the axis M1 can be prevented from slowing down, and the change in the circumferential direction of the ring valve 15 at the contact portion 15P on one side 15A of the ring valve 15 can be prevented from slowing down. Therefore, the wear resistance of the ring valve 15 can be accurately evaluated in a short time.

<4. Wear test method for ring valve 15>
3, 5, and 6, a method for testing the wear of the ring valve 15 is illustrated. Fig. 6 is a flowchart showing a method for testing the wear of the ring valve 15 according to an embodiment of the present disclosure. In the following description, steps may be abbreviated as "S".

The wear test method for the ring valve 15 using the wear test device 1A is, for example, performed as follows. First, the ring valve 15 is tilted relative to the simulated valve seat 21A and held so that a portion of one side 15A is in contact with the simulated valve seat 21 (S11). The method for attaching the ring valve 15 to the ring valve holding portion 29A is as described above.

Next, lubricating oil is supplied between the ring valve 15 and the simulated valve seat 21 (S13). This allows the lubricating oil to enter between the one side 15A of the ring valve 15 and the raised portion 21P of the simulated valve seat 21. After that, the ring valve 15 is moved relative to the simulated valve seat 21 (S15). Specifically, the drive source 30 of the wear test device 1A is driven to start the relative movement of the ring valve 15, and the contact portion 15P of the one side 15A of the ring valve 15 slides and the contact portion 15P of the one side 15A changes in the circumferential direction of the ring valve 15. After a specified time has elapsed since the drive source 30 started driving, the drive source 30 is stopped. After that, the ring valve 15 is removed from the wear test device 1A and the amount of wear of the one side 15A is measured, and the wear resistance of the ring valve 15 can be evaluated.

When S15 is executed, one side 15A of the ring valve 15 comes into partial contact with the raised portion 21P of the simulated valve seat 21. The above configuration realizes a wear test method that more faithfully reproduces the operating environment of the compressor 10 in which the ring valve 15 and the suction valve seat 61 are in partial contact.

When S15 is performed, the stopper 87 does not have to be provided on the wear test device 1A. In other words, in S15, the ring valve 15 may be allowed to rotate around its axis (which coincides with the axis L2 of the first shaft 11 in FIG. 4). With the above configuration, it is possible to more faithfully reproduce the behavior of the ring valve 15 in a compressor 10 having a configuration in which the ring valve 15 (the suction valve 63 in this example) can rotate in the circumferential direction.

In another embodiment, a stopper 87 may be provided to the wear testing device 1A when S15 is executed. That is, in S15, a braking force may be applied to the ring valve 15 to prevent rotation about the axis of the ring valve 15. With the above configuration, it is possible to more faithfully reproduce the behavior of the ring valve 15 in a compressor 10 having a configuration (e.g., a stopper mechanism) that restricts rotation about the axis of the suction valve 63.

In addition, in this embodiment, a step (S13) of supplying lubricating oil is executed before execution of S15. According to the above configuration, a wear test method for a compressor ring valve that more faithfully reproduces the operating environment of an actual compressor (10) is realized. Note that S13 may be executed during execution of S15. Also, the above-mentioned wear test method for a compressor ring valve may be used in the wear test device 1B.

<5. Summary>
The contents described in the above-mentioned embodiments can be understood, for example, as follows.

1) A method for testing wear of a compressor ring valve according to at least one embodiment of the present disclosure, comprising:
a step (S11) of holding a compressor ring valve (15) inclined relative to a simulated valve seat (21) simulating a valve seat (suction valve seat 61) for a compressor such that a portion of a circumferential direction of one surface (15A) of the ring valve (15) is in partial contact with the simulated valve seat (21);
and a step (S15) of moving the ring valve (15) relative to the simulated valve sheet (21) so that a contact portion (15P) of the one side (15A) that contacts the simulated valve sheet (21) slides against the simulated valve sheet (21) and the contact portion (15P) on the one side (15A) changes in the circumferential direction.

When an actual compressor (10) operates, the ring valve (15) moving toward the valve seat (suction valve seat 61) assumes an inclined position relative to the valve seat (suction valve seat 61). When the ring valve (15) strikes the valve seat (suction valve seat 61) in this position, the ring valve (15) is deflected by bending stress caused by gas pressure or a spring or the like, and a portion of the circumferential direction of one side (15A) of the ring valve (15) comes into partial contact with the valve seat (suction valve seat 61). After that, before the ring valve (15) sits on the valve seat (suction valve seat 61), the partial contact portion (15P) of one side (15A) of the ring valve (15) slides against the valve seat (suction valve seat 61), and this partial contact portion (15P) on one side (15A) of the ring valve (15) changes in the circumferential direction of the ring valve (15). The ring valve (15) repeats the above-mentioned behavior during operation of the compressor (10), so one side (15A) of the ring valve (15) wears. According to the above configuration 1), a step of moving the ring valve (15) relative to the simulated valve seat (21) is executed, so that the behavior of the ring valve (15) when the compressor (10) is operating can be reproduced and one side (15A) of the ring valve (15) can slide against the simulated valve seat (21). Thus, a wear test method for a compressor ring valve that can accurately evaluate the wear resistance of the ring valve (15) is realized.

2) In some embodiments, the method for testing a compressor ring valve according to 1) above includes the steps of:
In the step (S15) of relative movement, the ring valve (15) is biased toward the simulated valve seat (21).

According to the configuration of 2) above, the partial contact portion (15P) of the ring valve (15) presses against the simulated valve seat (21), which accelerates the progression of wear in the ring valve (15). Therefore, the wear resistance of the ring valve (15) can be accurately evaluated in a short time.

3) In some embodiments, there is provided a method for testing abrasion of a compressor ring valve according to either 1) or 2) above, comprising the steps of:
In the holding step (S11), the ring valve (15) is held so as to be eccentric with respect to the simulated valve seat (21).

According to the configuration of 3) above, when the step (S15) of causing relative movement is performed, the ring valve (15) moves relative to the simulated valve seat (21) in the radial direction based on the axis of the simulated valve seat (21). This increases the amount of sliding of the partial contact portion (15P) of the ring valve (15) against the simulated valve seat (21), making it possible to accurately evaluate the wear resistance of the ring valve (15) in a short time.

4) In some embodiments, there is provided a method for testing abrasion of a compressor ring valve according to any one of 1) to 3) above, comprising the steps of:
In the step of causing relative movement (S15), the simulated valve seat (21) is fixed at a specified position.

According to the configuration of 4) above, a drive mechanism for moving the simulated valve seat (21) of the simulated valve seat (21) and the ring valve (15) is not required, so the device for carrying out the wear test method for compressor ring valves can be simplified.

5) In some embodiments, the method for testing a wear of a compressor ring valve according to any one of 1) to 4) above, further comprising the steps of:
In the step of causing relative movement (S15), rotation about the axis of the ring valve (15) is permitted with respect to the ring valve (15).

The configuration of 5) above realizes a wear test method for a compressor ring valve that more faithfully reproduces the behavior of the ring valve (15) in a compressor (10) that has a configuration in which the ring valve (15) can rotate around its axis.

6) In some embodiments, there is provided a method for testing a wear of a compressor ring valve according to any one of 1) to 4) above, comprising the steps of:
In the step (S15) of causing relative movement, a braking force is applied to the ring valve (15) to prevent rotation about the axis of the ring valve (15).

The configuration of 6) above realizes a wear test method for a compressor ring valve that more faithfully reproduces the behavior of the ring valve (15) in a compressor (10) that has a configuration that restricts the rotation of the ring valve (15) around its axis.

7) In some embodiments, there is provided a method for testing abrasion of a compressor ring valve according to any one of 1) to 3) above, comprising the steps of:
In the step of causing relative movement (S15), the ring valve (15), which is driven by the simulation valve seat (21) that is rotationally driven, is caused to move relative to the simulation valve seat (21).

According to the configuration of 7) above, the test conditions can be changed by changing the configuration of either the mechanism for supporting the simulated valve seat (21) so that it can be driven to rotate, or the mechanism for supporting the ring valve (15) so that it can be driven to rotate. This realizes a wear test method for compressor ring valves that allows a high degree of freedom in changing the test conditions.

8) In some embodiments, the method for testing a wear of a compressor ring valve according to any one of 1) to 7) above, further comprising the steps of:
In the step (S15) of performing relative movement, an area (raised portion 21P) of the opposing surface (21F) of the simulated valve sheet (21) that faces the one side (15A) of the ring valve (15) that protrudes toward the ring valve (15) is brought into contact with the one side (15A).

The configuration of 8) above realizes a wear test method for compressor ring valves that more faithfully reproduces the operating environment of the compressor (10) in which the ring valve (15) and the valve seat (suction valve seat 61) are in partial contact.

9) In some embodiments, the method for testing a wear of a compressor ring valve according to any one of 1) to 8) above, further comprising the steps of:
The method further includes an oil supplying step (S13) of supplying lubricating oil between the ring valve (15) and the simulated valve seat (21) during the relative movement step (S15).

The above configuration 9) realizes a wear test method for compressor ring valves that more faithfully reproduces the operating environment of an actual compressor (10).

10) A wear testing device (1) for a compressor ring valve according to at least one embodiment of the present disclosure,
A first shaft (11);
A second shaft (12) configured to rotate in conjunction with the first shaft (11) while being inclined relative to the first shaft (11);
a simulated valve seat (21) provided coaxially with the first shaft (11) and simulating a valve seat (suction valve seat 61) for a compressor;
a ring holder (29) for holding a compressor ring valve (15) so that one side (15A) of the ring valve (15) is in partial contact with the simulated valve seat (21);
and a drive source (30) for rotating the first shaft (11) and the second shaft (12) so that a contact portion (15P) of the one side (15A) that contacts the simulated valve seat (21) slides against the simulated valve seat (21) and the contact portion (15P) on the one side (15A) changes in the circumferential direction of the ring valve (15).

According to the configuration of 10) above, since the second shaft (12) is inclined relative to the first shaft (11), when the drive source (30) is driven, the ring valve (15) inclined relative to the first shaft (11) rotates around the axis (L1, M1) of the first shaft (11). With this rotation, the contact portion (15P) of one side (15A) of the ring valve (15) that contacts the simulated valve seat (21) slides against the simulated valve seat (21), and the ring valve (15) can move relative to the simulated valve seat (21) so that the contact portion (15P) on one side (15A) of the ring valve (15) changes in the circumferential direction. As a result, for the same reason as in 1) above, a wear test device (1) for a compressor ring valve that can accurately evaluate the wear resistance of the ring valve (15) is realized.

11) In some embodiments, the wear testing device (1) for a compressor ring valve described in 10) above,
The valve further includes a biasing means (35) for biasing the ring holder (29) toward the simulated valve seat (21).

The configuration 11) above allows the wear resistance of the ring valve (15) to be evaluated accurately in a short time for the same reason as 2) above.

12) In some embodiments, the wear testing device (1) for a compressor ring valve according to any one of 10) or 11) above,
The second shaft (12) is eccentric with respect to the first shaft (11).

According to the configuration of 12) above, when the drive source (30) is driven, the ring valve (15) moves relative to the simulated valve seat (21) in the radial direction based on the axis of the simulated valve seat (21). This allows the wear resistance of the ring valve (15) to be evaluated accurately in a short time for the same reason as in 3) above.

13) In some embodiments, the wear testing device (1) for a compressor ring valve according to any one of 10) to 12) above,
The simulated valve seat (21) is fixed in a defined position.

The configuration of 13) above allows the compressor ring valve wear test device (1) to be simplified for the same reason as 4) above.

14) In some embodiments, the wear testing device (1) for a compressor ring valve according to any one of 10) to 13) above,
The second shaft (12) is directly connected to the first shaft (11);
The ring holder (29) is connected to the second shaft (12) via a bearing (97).

According to the above configuration 14), by simply adopting a configuration in which the ring holder (29) is connected via a bearing (97) to the second shaft (12) which is directly connected to the first shaft (11), the one-sided contact portion (15P) of the ring valve (15) slides against the simulated valve seat (21) and the one-sided contact portion (15P) on one side (15A) of the ring valve (15) moves in the circumferential direction. This simplifies the wear test device (1) for compressor ring valves.

15) In some embodiments, the wear testing device (1) for a compressor ring valve according to any one of 10) to 12) above,
The first shaft (11) is connected to the driving source (30),
The simulated valve seat (21) is fixed to the first shaft (11);
The ring retainer (29), configured to retain the ring valve (15) for contacting the simulated valve seat (21), is fixed to the second shaft (12).

According to the configuration of 15) above, the ring valve (15) is driven by the simulated valve seat (21) which is rotationally driven by the drive source (30). As a result, the ring valve (15) moves relative to the simulated valve seat (21). Therefore, for the same reason as 7) above, a wear test device (1) for compressor ring valves with a high degree of freedom in changing the test conditions is realized.

16) In some embodiments, the wear testing device (1) for a compressor ring valve described in 15) above,
The device further includes a coupling (88) connected to the first shaft (11) and the second shaft (12).

The configuration of 16) above makes it possible to suppress deviations between the rotational speeds of the second shaft (12) and the first shaft (11) due to changes in the sliding state of the ring valve (15) against the simulated valve seat (21). Therefore, it is possible to suppress slowing of the circumferential change of the contact portion (15P) on one side (15A) of the ring valve (15), so that the wear resistance of the ring valve (15) can be accurately evaluated in a short time.

1: Wear test device 10: Compressor 11: First shaft 12: Second shaft 15: Ring valve 15A: One side 15P: One-sided contact area 21: Simulation valve seat 21F: Opposing surface 21P: Raised portion 30: Driving source 35: Pressing means 40: Cylinder sleeve 63: Suction valve 63A: One side 63P: One-sided contact area 88: Joint 97: Bearing

Claims (16)

a step of holding a compressor ring valve inclined relative to a simulated valve seat simulating a valve seat for a compressor such that a portion of a circumferential direction of one side of the ring valve is in partial contact with the simulated valve seat;
and moving the ring valve relative to the simulated valve seat so that a portion of the one side that comes into partial contact with the simulated valve seat slides against the simulated valve seat and the portion of the one side that comes into partial contact with the simulated valve seat changes in the circumferential direction. 2. The method for wear testing of a compressor ring valve according to claim 1, wherein in said step of moving the ring valve relative to the simulated valve seat, said ring valve is biased toward said simulated valve seat. 3. The wear test method for a compressor ring valve according to claim 1, wherein the ring valve is held eccentrically with respect to the simulated valve seat in the holding step. 4. The method for wear testing of a compressor ring valve according to claim 1, wherein in said step of moving the simulated valve seat relative to the valve seat, the simulated valve seat is fixed at a specified position. 5. The wear test method for a compressor ring valve according to claim 1, wherein in the step of moving the ring valve relative to the ring valve, the ring valve is permitted to rotate about an axis of the ring valve. 5. The wear testing method for a compressor ring valve according to claim 1, wherein in the step of moving the ring valve relative to the compressor, a braking force is applied to the ring valve to prevent the ring valve from rotating about its axis. 4. The wear test method for a compressor ring valve according to claim 1, wherein in the step of moving the ring valve relative to the simulated valve seat, the ring valve is moved relative to the simulated valve seat, the simulated valve seat being driven to rotate. The wear test method for compressor ring valves according to any one of claims 1 to 7, wherein in the step of moving relative to one side of the ring valve, an area of the facing surface of the simulated valve seat that faces the one side of the ring valve and that protrudes toward the ring valve is applied to the one side. 9. The wear testing method for a compressor ring valve according to claim 1, further comprising an oil supplying step of supplying lubricating oil between the ring valve and the simulated valve seat during the relative movement step. A first shaft;
A second shaft configured to rotate in conjunction with the first shaft while being inclined relative to the first shaft;
A simulated valve seat that is provided coaxially with the first shaft and simulates a valve seat for a compressor;
a ring valve holding portion for holding the compressor ring valve such that one side of the ring valve is in partial contact with the simulated valve seat;
a drive source for rotating the first shaft and the second shaft so that a portion of the one side that comes into partial contact with the simulated valve seat slides against the simulated valve seat and the portion of the one side that comes into partial contact with the simulated valve seat changes in the circumferential direction of the ring valve. The compressor ring valve wear testing device according to claim 10, further comprising a biasing means for biasing the ring valve holder toward the simulated valve seat. 12. The wear testing device for a compressor ring valve according to claim 10 or 11, wherein the second shaft is eccentric with respect to the first shaft. 13. The wear testing device for compressor ring valves according to claim 10, wherein the simulated valve seat is fixed at a specified position. the second shaft is directly connected to the first shaft;
14. The wear testing device for a compressor ring valve according to claim 10, wherein the ring valve holder is connected to the second shaft via a bearing. The first shaft is connected to the drive source,
the simulated valve seat is fixed to the first shaft;
13. The compressor ring valve wear testing apparatus of claim 10, wherein the ring valve holder configured to hold the ring valve for contacting the simulated valve seat is fixed to the second shaft. 16. The compressor ring valve wear testing apparatus of claim 15, further comprising a coupling coupled to said first shaft and said second shaft.