Wear amount calculation device

Abstract

To provide a wear amount calculation device capable of accurately calculating a wear amount of a tip seal in a scroll compressor.SOLUTION: A wear amount calculation device that calculates an estimated wear amount of a tip seal in a scroll compressor that includes an orbiting scroll provided with a spiral orbiting wrap, a fixed scroll provided with a spiral fixed wrap that meshes with the orbiting wrap, and a tip seal that is provided on a tooth tip of at least one of the orbiting wrap and the fixed wrap and suppresses leakage of compressed air, and generates compressed air by orbiting the orbiting scroll, the wear amount calculation device comprising: The wear amount calculation device includes a monitoring unit configured to monitor a surface pressure value correlated with a surface pressure of the tip seal received from compressed air and a sliding speed value correlated with a sliding speed of the tip seal, and a calculation unit configured to calculate the estimated wear amount based on the surface pressure value and the sliding speed value.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a wear amount calculation device that calculates an estimated wear amount of a tip seal in a scroll compressor. [Background technology]

[0002] One type of equipment that generates compressed air is known as a scroll compressor, as disclosed in Patent Document 1. The scroll compressor has an orbiting scroll provided with a spiral orbiting wrap and a fixed scroll provided with a spiral fixed wrap that meshes with the orbiting wrap, and is capable of generating compressed air by orbiting the orbiting scroll.

[0003] Scroll compressors are excellent in terms of low vibration and noise, and also have the advantage of relatively little air leakage during the compression process. Furthermore, tip seals are typically provided on the tips of the orbiting and / or fixed wrap teeth to prevent leakage of compressed air. Tip seals can be replaced with new ones, for example, when they reach the end of their life due to wear.

[0004] Conventionally, necessary maintenance has been carried out to ensure the appropriate long-term use of various facilities and equipment, etc. However, simply carrying out after-the-fact maintenance (corrective maintenance) after an abnormality has occurred may result in performance degradation or damage to the equipment, etc., due to the abnormality, or downtime caused by unexpected shutdowns may have a significant impact on the availability rate.

[0005] To minimize such problems, it is effective to carry out before-the-fact maintenance (preventive maintenance) before an abnormality occurs. The two main types of before-the-fact maintenance known are time-based maintenance and condition-based maintenance.

[0006] Time-based maintenance has the advantage that maintenance is performed based on elapsed time or a regularly set time, making it easy to develop a habit of on-site operation. However, the degree of deterioration of equipment varies depending on the frequency of use and the environment in which it is used. Therefore, with time-based maintenance, it is not easy to perform maintenance at the appropriate time, and problems can easily arise such as unnecessary maintenance being performed even when the equipment is not very deteriorated, or, conversely, necessary maintenance not being performed even when the equipment is very deteriorated.

[0007] On the other hand, condition-based maintenance can eliminate such problems as much as possible because maintenance is carried out according to the deterioration state of the equipment, etc. By adopting condition-based maintenance, it is possible to optimize the frequency of maintenance and minimize the downtime of equipment, etc. due to maintenance. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] Japanese Patent Publication No. 2022-143913 Summary of the Invention [Problem to be solved by the invention]

[0009] In the scroll compressor described above, the orbiting scroll orbits while the tip seal rubs against the fixed scroll or the orbiting scroll. As a result, the tip seal gradually wears out with use of the scroll compressor, and maintenance to replace the tip seal is required to continue using the scroll compressor appropriately.

[0010] The aforementioned condition-based maintenance is desirable as a maintenance method from the viewpoint of optimizing the frequency of maintenance. However, because the degree of wear of the tip seal varies greatly depending on the usage conditions of the scroll compressor, it is difficult to accurately determine the amount of wear of the tip seal simply by monitoring the usage time of the scroll compressor. Therefore, it is desirable to be able to accurately calculate the amount of wear.

[0011] Furthermore, because the tip seal is installed inside the scroll compressor, it is generally difficult for a maintenance worker to visually check the wear state of the tip seal unless the scroll compressor is disassembled. Therefore, from the perspective of being able to grasp the wear state without visual inspection, it is desirable to be able to accurately calculate the amount of wear of the tip seal.

[0012] In view of the above-mentioned problems, an object of the present invention is to provide a wear amount calculation device that can accurately calculate the amount of wear of a tip seal in a scroll compressor. [Means for solving the problem]

[0013] The wear amount calculation device of the present invention is a scroll compressor that generates compressed air by orbiting the orbiting scroll, and that has an orbiting scroll provided with a spiral-shaped orbiting wrap, a fixed scroll provided with a spiral-shaped fixed wrap that meshes with the orbiting wrap, and a tip seal that is provided on the tooth tip of at least one of the orbiting wrap and the fixed wrap to prevent leakage of compressed air.The wear amount calculation device calculates an estimated wear amount of the tip seal, and is configured to have a monitoring unit that monitors a surface pressure value that is correlated with the surface pressure of the tip seal received from the compressed air and a sliding speed value that is correlated with the sliding speed of the tip seal, and a calculation unit that calculates the estimated wear amount based on the surface pressure value and the sliding speed value.

[0014] According to this configuration, it is possible to accurately calculate the amount of wear of the tip seal in the scroll compressor.More specifically, as the above configuration, the calculation unit may be configured to calculate the estimated amount of wear by integrating the product of the surface pressure value and each value including the sliding speed value per unit time.

[0015] More specifically, the above configuration may be configured such that the monitoring unit is capable of detecting the discharge pressure of the scroll compressor, and when the discharge pressure is lower than the internal compression pressure of the scroll compressor, a value corresponding to the internal compression pressure is used as the surface pressure value, and when the discharge pressure is higher than the internal compression pressure, a value corresponding to the discharge pressure is used as the surface pressure value.

[0016] More specifically, the monitoring unit may be configured to detect the number of rotations per unit time of the orbiting scroll or the drive motor that orbits the orbiting scroll, and a value corresponding to the number of rotations may be set as the sliding speed value. Also, more specifically, the monitoring unit may be configured to execute an alarm operation to notify a user when the calculated value of the estimated wear amount exceeds a predetermined threshold. [Effects of the Invention]

[0017] According to the wear amount calculation device of the present invention, it is possible to accurately calculate the wear amount of the tip seal in the scroll compressor. [Brief explanation of the drawings]

[0018] [Figure 1] 1 is an explanatory diagram of a wear amount calculation device according to an embodiment of the present invention and its peripheral configuration; [Figure 2] 1 is a perspective view of a scroll compressor according to an embodiment of the present invention. [Figure 3] FIG. 2 is an exploded perspective view of a housing included in the scroll compressor. [Figure 4] FIG. 2 is a vertical cross-sectional view of the scroll compressor. [Figure 5] FIG. 2 is a front view of a fixed scroll included in the scroll compressor. [Figure 6] FIG. 2 is a front view of an orbiting scroll included in the scroll compressor. DETAILED DESCRIPTION OF THE INVENTION

[0019] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the accompanying drawings.

[0020] 1 is a schematic diagram showing a wear amount calculation device 2 according to this embodiment and its peripheral configuration. The scroll compressor 1 shown in the figure has a drive motor 1a for orbiting an orbiting scroll 30, which will be described later. The scroll compressor 1 supplies compressed air generated by driving the drive motor 1a to a load facility 4 (facility requiring compressed air) via a supply pipe 3.

[0021] Furthermore, the scroll compressor 1 has a controller 1b that controls the number of rotations per unit time of the drive motor 1a (hereinafter, sometimes referred to as "number of rotations N"), etc. The scroll compressor 1 also has a pressure sensor 5 that detects the discharge pressure of the scroll compressor 1 (the pressure of compressed air discharged from the scroll compressor 1 to the supply pipe 3, hereinafter, sometimes referred to as "discharge pressure Py").

[0022] The wear amount calculation device 2 is a device that monitors various pieces of information related to the scroll compressor 1 and calculates an estimated amount of wear of the tip seal in the scroll compressor 1 based on the information. The wear amount calculation device 2 of this embodiment is continuously sent information on the current rotation speed N from the controller 1b and information on the current discharge pressure Py from the pressure sensor 5, and is able to calculate the estimated amount of wear by monitoring this information. Details of the wear amount calculation device 2 will be described later.

[0023] Next, the detailed configuration of the scroll compressor 1 will be described below. FIG. 2 is a perspective view of the scroll compressor 1. FIG. 3 is an exploded perspective view of a housing 10 provided in the scroll compressor 1. FIG. 4 is a vertical cross-sectional view of the scroll compressor 1. The scroll compressor 1 is a water-addition type compressor in which lubricating water is added to the air taken in. The scroll compressor 1 includes a housing 10, an orbiting scroll 30, a crankshaft 70, and two fixed scrolls 50, 150.

[0024] The housing 10 is composed of a first housing portion 15 and a second housing portion 20. A fixed scroll 50 is attached to an opening 16 formed in the first housing portion 15. A fixed scroll 150 is attached to an opening 21 formed in the second housing portion 20. The fixed scroll 50 and the fixed scroll 150 have the same configuration except that they are in a line-symmetrical mirror image relationship with a predetermined direction, such as the vertical direction, as the axis of symmetry. Note that the fixed scroll 50 is not shown in FIG. 3.

[0025] The orbiting scroll 30 is housed inside the housing 10 so that its center of rotation is located in the center. In this embodiment, the orbiting scroll 30 is held by the housing 10 so that its axial direction faces sideways (horizontally). A plurality of crankshafts 70 are connected to the orbiting scroll 30.

[0026] The crankshaft 70 includes an eccentric shaft portion 71 and base shaft portions 72 disposed on both sides of the eccentric shaft portion 71. In this embodiment, a weight balancer 75 is provided on the base shaft portion 72 to smooth the orbiting motion of the orbiting scroll 30. The shape and weight of the weight balancer 75 are adjusted appropriately depending on the mounting position of the crankshaft 70. The eccentric shaft portion 71 is journaled on the orbiting scroll 30, and the base shaft portions 72 are journaled on the housing bearing portion 26 of the housing 10.

[0027] A total of three crankshafts 70 are arranged at equal intervals in the circumferential direction. The three crankshafts 70 have the same structure and rotate synchronously with the eccentric shaft portions 71 aligned by a rotation synchronization mechanism consisting of a pulley 76, two timing belts 77, and two tension rollers 78. Of the three crankshafts 70, two crankshafts 70 around which the timing belts 77 are wound are drive shafts that rotate by directly transmitting the rotational driving force of the drive motor 1a, and the other two crankshafts 70 are driven shafts that rotate synchronously by transmitting the rotational force of the drive shafts via the timing belts 77.

[0028] When each crankshaft 70 is rotated by the power of the drive motor 1a, the orbiting scroll 30 orbits relative to the fixed scroll 50. As described above, the rotation speed N (number of rotations per unit time) of the drive motor 1a is controlled by the controller 1b. The value of the rotation speed N is the same as or proportional to the rotation speed per unit time of the orbiting scroll 30. The controller 1b controls the rotation speed N so that an appropriate amount of compressed air is generated according to the compressed air demand of the load equipment 4.

[0029] The fixed scroll 50 is disposed on one axial side of the orbiting scroll 30, and the fixed scroll 150 is disposed on the other axial side of the orbiting scroll 30. In other words, the orbiting scroll 30 is sandwiched between the fixed scroll 50 and the fixed scroll 150.

[0030] Next, a description will be given of the configuration of the fixed scroll 50. Fig. 5 is a front view of the fixed scroll 50 provided in the scroll compressor 1.

[0031] The fixed scroll 50 comprises a disk-shaped fixed side substrate portion 51, one or more fixed wraps 52 provided on a plate surface (one side) of the fixed side substrate portion 51 facing the orbiting side substrate portion 31, and an annular outer wrap 55 surrounding the fixed wrap 52.

[0032] A central opening 60 is formed in the center of the fixed-side substrate portion 51, penetrating it in the thickness direction. The central opening 60 is a through-hole that connects the outside of the scroll compressor 1 with the compression chamber 90. In addition, an outer peripheral opening 61 is provided on the outer peripheral side of the fixed-side substrate portion 51.

[0033] The fixed wraps 52 are formed in a number, shape, and size corresponding to the orbiting wraps 32 of the orbiting scroll 30. The fixed wraps 52 extend vertically (axially) from the plate surface of the fixed-side substrate portion 51, and are configured to be curved in an involute spiral shape from the center of the fixed-side substrate portion 51 toward the outer periphery.

[0034] A tip seal 54 is provided at the tooth tip (the tip facing the orbiting scroll 30) of the fixed wrap 52 to fill the gap with the orbiting-side base plate portion 31 of the orbiting scroll 30. The tip seal 54 is arranged along the spiral of the fixed wrap 52 and comes into contact with the orbiting-side base plate portion 31.

[0035] The tip seal 54 is an insulating resin molded product whose main component is, for example, polytetrafluoroethylene. The tip seal 54 may contain a solid lubricant such as carbon fiber or graphite to improve its wear resistance.

[0036] The outer circumferential wrap 55 is formed in a cylindrical shape surrounding the fixed wrap 52. The space surrounded by the orbiting-side base plate portion 31, the fixed-side base plate portion 51, and the outer circumferential wrap 55 functions as a compression chamber 90 that compresses the hydrated air (fluid).

[0037] An outer circumferential seal 80 is provided at the tip of the outer circumferential wrap 55 to fill the gap with the orbiting-side base plate portion 31 of the orbiting scroll 30. The outer circumferential seal 80 is formed in an annular shape surrounding the compression chamber 90 and prevents water from leaking outside the compression chamber 90.

[0038] A notch 510 is provided on the inner peripheral surface of the outer circumferential wrap 55. The notch 510 is located radially inward of the outer circumferential seal 80 and is formed in an arc shape. A drain port 520 that communicates with the outside of the compression chamber 90 is formed near one end 512 of the notch 510. The drain port 520 opens on the end face of the notch 510 facing the orbiting-side base plate portion 31. The drain port 520 penetrates all the way to the outer surface of the fixed-side base plate portion 51, and serves as a flow path for discharging water that has accumulated inside to the outside of the compression chamber 90.

[0039] Next, a description will be given of the configuration of the orbiting scroll 30. Fig. 6 is a front view of the orbiting scroll 30 provided in the scroll compressor 1. The orbiting scroll 30 includes a disk-shaped orbiting-side substrate portion 31, orbiting wraps 32 provided on both sides of the orbiting-side substrate portion 31, and an orbiting scroll outer peripheral portion 35.

[0040] A central opening 33 is formed in the center of the orbiting-side base plate portion 31, penetrating through it in the thickness direction. The orbiting wrap 32 extends vertically (axially) from the plate surface of the orbiting-side base plate portion 31, and is configured in a plate shape that curves in an involute spiral shape from the center to the outer periphery of the orbiting-side base plate portion 31. The orbiting wraps 32 on both sides have shapes that correspond to each other.

[0041] A tip seal 34 is provided at the tooth tip (the tip portion facing each fixed scroll 50, 150) of each orbiting wrap 32 to fill the gap with the fixed-side base plate portion 51 of each fixed scroll 50, 150. The tip seal 34 is arranged along the spiral of the orbiting wrap 32 and comes into contact with the fixed-side base plate portion 51.

[0042] The tip seal 34 is an insulating resin molded product whose main component is, for example, polytetrafluoroethylene. The tip seal 34 may contain a solid lubricant such as carbon fiber or graphite to improve its wear resistance.

[0043] The orbiting scroll outer peripheral portion 35 is formed in the shape of a roughly triangular frame that surrounds the orbiting-side substrate portion 31, with the orbiting-side substrate portion 31 located inside it. The orbiting scroll outer peripheral portion 35 and the orbiting-side substrate portion 31 are integrally formed. Connecting holes 301 to which the crankshaft 70 is connected are formed at positions corresponding to the vertices (corners) of the roughly triangle of the orbiting scroll outer peripheral portion 35.

[0044] The scroll compressor 1 has the above-described configuration, and air (fluid) to which lubricating water has been added is introduced from the outside through piping (not shown) as the orbiting scroll 30 orbits. The air introduced into the compression chamber 90 of the scroll compressor 1 is compressed between the orbiting scroll 30 and each of the fixed scrolls 50, 150, moves from the outer end to the inner end of the spiral, and is discharged from the central opening 60. The compressed air thus discharged is supplied to the load equipment 4 via the supply piping 3.

[0045] As described above, the scroll compressor 1 has an orbiting scroll 30 provided with a spiral-shaped orbiting wrap 32, fixed scrolls 50, 150 provided with spiral-shaped fixed wraps 52 that mesh with the orbiting wrap 32, and chip seals 34, 54 provided at the tooth tips of the orbiting wrap 32 and the fixed wrap 52 to prevent leakage of compressed air, and generates compressed air by orbiting the orbiting scroll 30.

[0046] In the following description, the tip seal 34 provided on the tooth tip of the orbiting wrap 32 and the tip seal 54 provided on the tooth tip of the fixed wrap 52 may be collectively referred to as the tip seal CS. In the scroll compressor 1 described above, the tip seal CS is provided on the tooth tip of both the orbiting wrap 32 and the fixed wrap 52, but it may be provided on the tooth tip of only one of them.

[0047] The scroll compressor 1 orbits the orbiting scroll 30 to generate compressed air at a predetermined internal compression pressure Px (e.g., 0.5 MPa) in the compression chamber 90, but can discharge compressed air at any set pressure up to a predetermined maximum discharge pressure Pz (e.g., 0.8 MPa) that exceeds this internal compression pressure Px. This set pressure can be set to an appropriate pressure according to the requirements of the load equipment 4, for example.

[0048] More specifically, when compressed air having a pressure higher than the internal compression pressure Px is discharged (when the discharge pressure Py is higher than the internal compression pressure Px), the scroll compressor 1 operates to forcefully push the compressed air in the compression chamber 90 (air having the internal compression pressure Px) into the supply pipe 3 by the force of the motor. This increases the pressure of the compressed air by the amount that it is pushed in, making it possible to discharge compressed air having a pressure higher than the internal compression pressure Px.

[0049] At this time, at least a portion of the compressed air that has been strongly pushed into the supply pipe 3 passes through the gap between the supply pipe 3 and the compression chamber 90 and leaks back into the compression chamber 90. Therefore, the surface pressure that the tip seal CP receives from the compressed air becomes approximately equal to the discharge pressure Py of the scroll compressor 1.

[0050] On the other hand, when discharging compressed air at a pressure lower than the internal compression pressure Px (when the discharge pressure Py is lower than the internal compression pressure Px), the scroll compressor 1 operates to expand the compressed air in the compression chamber 90 (air at the internal compression pressure Px) in the supply pipe 3. This reduces the pressure of the compressed air by the amount of expansion, making it possible to discharge compressed air at a pressure lower than the internal compression pressure Px.

[0051] Even when compressed air having a pressure lower than the internal compression pressure Px is discharged in this way, the pressure of the compressed air in the compression chamber 90 remains almost unchanged at the internal compression pressure Px. Therefore, the surface pressure that the tip seal CP receives from the compressed air is approximately equal to the internal compression pressure Px.

[0052] Here, the internal compression pressure Px is a design pressure based on the geometric theory of the scroll body. For example, the main parameters of a scroll compressor can be obtained from the geometric properties of the involute of a circle, and the change in compression chamber volume and built-in volume ratio relative to the rotation angle can be calculated. The theoretical built-in compression ratio can be determined by applying a polytropic exponent to the built-in volume ratio, and the internal compression pressure Px is obtained by multiplying the suction pressure by the theoretical built-in compression ratio.

[0053] The tip seal CS is provided so as to contact the orbiting-side substrate portion 31 or the fixed-side substrate portion 51 to prevent leakage of compressed air. Therefore, when the scroll compressor 1 is driven, the orbiting scroll 30 orbits while the tip seal CS rubs against the orbiting-side substrate portion 31 or the fixed-side substrate portion 51. Therefore, the tip seal CS gradually wears as the scroll compressor 1 is used. The estimated wear amount of the tip seal CS can be calculated by the wear amount calculation device 2.

[0054] Next, a more detailed description will be given of the wear amount calculation device 2. As shown in Fig. 1, the wear amount calculation device 2 has a monitoring unit 2a and a calculation unit 2b.

[0055] The monitoring unit 2a monitors a surface pressure value V1, which correlates with the surface pressure of the tip seal CS received from compressed air, and a sliding speed value V2, which correlates with the sliding speed of the tip seal CS (the speed at which the tip seal CS rubs against the orbiting-side base plate portion 31 or the fixed-side base plate portion 51). Even if the scroll compressor 1 is used for the same amount of time, the greater the surface pressure, the more likely the tip seal CS will wear, and the greater the sliding speed, the more likely the tip seal CS will wear. Therefore, the surface pressure value V1 and the sliding speed value V2 are closely correlated (basically proportional) with the degree of wear of the tip seal CS.

[0056] As described above, when the discharge pressure Py of the scroll compressor 1 is higher than the internal compression pressure Px, the surface pressure of the tip seal CS from the compressed air is approximately equal to the discharge pressure Py. On the other hand, when the discharge pressure Py is lower than the internal compression pressure Px, the surface pressure is approximately equal to the internal compression pressure Px.

[0057] Therefore, the monitoring unit 2a is capable of detecting the discharge pressure Py, and when the detected discharge pressure Py is lower than the internal compression pressure Px, a value corresponding to the internal compression pressure Px (the value of the internal compression pressure Px itself or a value correlated with that value) is set as the surface pressure value V1. Note that in this embodiment, the monitoring unit 2a is capable of continuously detecting (monitoring) the discharge pressure Py based on information received from the pressure sensor 5 described above.

[0058] Furthermore, when the detected discharge pressure Py is higher than the internal compression pressure Px, the monitoring unit 2a sets a value corresponding to the discharge pressure (the value of the detected discharge pressure Py itself or a value correlated with that value) as the surface pressure value V1. In this way, the monitoring unit 2a can monitor the surface pressure value V1 with high accuracy.

[0059] Furthermore, the sliding speed of the tip seal CS is closely correlated with the rotation speed N (number of rotations per unit time) of the drive motor 1a that drives the orbiting scroll 30. The monitoring unit 2a is capable of detecting this rotation speed N, and sets a value corresponding to the detected rotation speed N (the value of the rotation speed N itself, or a value correlated to that value) as the sliding speed value V2. In this embodiment, the monitoring unit 2a is capable of continuously detecting (monitoring) the rotation speed N based on information received from the controller 1b described above.

[0060] If the controller 1b is configured to inverter-control the drive motor 1a, information on the frequency of the control may be continuously sent from the controller 1b to the monitoring unit 2a, and the monitoring unit 2a may detect the rotation speed N based on this information. Alternatively, the monitoring unit 2a may directly detect the rotation speed per unit time of the orbiting scroll 30, and use the value of this rotation speed as the sliding speed value V2.

[0061] The calculation unit 2b calculates the estimated wear amount Ws of the tip seal CS based on the surface pressure value V1 and the sliding speed value V2. More specifically, the calculation unit 2b calculates the estimated wear amount Ws by integrating the calculated value W1 calculated by the following first formula for each unit time (for example, every second). W1=K×V1×V2...Equation 1 In the first formula, "K" represents a predetermined specific wear amount K, "V1" represents the surface pressure value V1 at that time, and "V2" represents the sliding speed value V2 at that time.

[0062] The calculated value W1 is obtained by multiplying each value, including the surface pressure value V1 and the sliding speed value V2, and corresponds to the estimated amount of wear of the tip seal CS within that unit time. Therefore, by sequentially accumulating the calculated value W1 for each unit time, it is possible to calculate the latest estimated amount of wear Ws of the tip seal CS (an estimate of the total amount of wear accumulated up to that point).

[0063] The specific value of the specific wear rate K may be determined, for example, by calculation taking various conditions into consideration, or may be determined based on the results of a simulation experiment using an experimental machine equivalent to the scroll compressor 1. Furthermore, the wear pattern of the tip seal CS may change depending on the contact pressure. Therefore, information on the specific wear rate K for each contact pressure value V1 may be obtained in advance by calculation or experiment and stored in the calculation unit 2b, and the calculation unit 2b may then use this information to calculate the calculated value W1. This allows the calculation unit 2b to use the specific wear rate K corresponding to the current contact pressure value V1 when calculating the calculated value W1, thereby enabling the calculation unit 2b to calculate the calculated value W1 with greater accuracy.

[0064] Furthermore, when the calculated value of the estimated wear amount Ws described above exceeds a predetermined threshold Wa, the wear amount calculation device 2 performs a notification operation to notify the facility manager or a service person of a maintenance company (a company that provides maintenance services for the facility) of this fact. This threshold Wa is set appropriately in advance as a value corresponding to the wear amount at which replacement of the tip seal CS is deemed desirable. The specific form of the notification operation is not particularly limited, and may be, for example, the output of visual information (such as a predetermined display or the illumination of a warning lamp) or the output of auditory information (such as the output of a warning sound). The notification operation may also be in the form of transmitting predetermined information (maintenance recommendation information notifying that the estimated wear amount Ws has exceeded the threshold Wa) to an information terminal of the facility manager or a service center via an internet line or a mobile phone line. By performing the notification operation, the facility worker or manager can know that it is time to replace the tip seal CS and can perform maintenance to replace the tip seal CS at the appropriate time.

[0065] As described above, the wear amount calculation device 2 is a device that calculates the estimated wear amount Ws of the tip seal CP for the scroll compressor 1, and includes a monitoring unit 2a that monitors the surface pressure value V1, which is correlated with the surface pressure of the tip seal CS received from compressed air, and the sliding speed value V2, which is correlated with the sliding speed of the tip seal CS, and a calculation unit 2b that calculates the estimated wear amount Ws based on the surface pressure value V1 and the sliding speed value V2. Therefore, the wear amount calculation device 2 can accurately calculate the wear amount of the tip seal CS by taking into account the surface pressure value V1 and the sliding speed value V2, which affect the degree of wear of the tip seal CS.

[0066] It should be noted that the above-described embodiments are illustrative in all respects and should not be considered limiting. The technical scope of the present invention is defined by the claims, not by the description of the above-described embodiments, and should be understood to include all modifications that fall within the meaning and scope of the claims. [Industrial Applicability]

[0067] The present invention can be used in a device for calculating an estimated amount of wear of a tip seal.

[0068] <Contribution to the United Nations-led Sustainable Development Goals (SDGs)> The wear calculation device disclosed herein calculates the estimated wear of the tip seal of a scroll compressor and provides condition-based maintenance at the appropriate time. This not only maintains the specific energy of the scroll compressor at a high level, but also reduces carbon dioxide emissions associated with unnecessary on-site dispatches of service personnel. This can contribute to achieving Goal 13 of the Sustainable Development Goals (SDGs), "Take urgent action to combat climate change." [Explanation of symbols]

[0069] 1 Scroll compressor 1a Drive motor 1b Controller 2. Wear calculation device 2a Monitoring section 2b Calculation part 3 Supply piping 4 Load equipment 5 Pressure Sensor 10. Housing 15 First housing section 16 Opening 20 Second housing section 21 Opening 26 Housing bearing part 30 Swivel Scroll 301 Connection hole 31 Swivel side base plate 32 Turning Lap 33 Central opening 34 Chip seal installed on the rotating wrap 35 Rotating scroll outer periphery 50,150 fixed scroll 51 Fixed side board part 510 Notch 52 Fixed Wrap 520 Drain port 54 Chip seal on fixed wrap 55 Outer wrap 55 60 central opening 61 Outer periphery opening 70 crankshaft 71 Eccentric shaft part 72 Base section 75 Weight Balancer 76 Pulley 77 Timing belt 78 Tension roller 80 Periphery seal 90 compression chamber CS Tip Seal

Claims

1. A wear amount calculation device for a scroll compressor that generates compressed air by orbiting the orbiting scroll, the scroll compressor comprising: an orbiting scroll having a spiral orbiting wrap; a fixed scroll having a spiral orbiting wrap that meshes with the orbiting wrap; and a tip seal that is provided on a tooth tip of at least one of the orbiting wrap and the fixed wrap to suppress leakage of compressed air, the wear amount calculation device calculating an estimated wear amount of the tip seal, a monitoring unit that monitors a surface pressure value that is correlated with the surface pressure of the tip seal received from compressed air and a sliding speed value that is correlated with the sliding speed of the tip seal; a calculation unit that calculates the estimated wear amount based on the surface pressure value and the sliding speed value.

2. The calculation unit 2. The wear amount calculation device according to claim 1, wherein the estimated wear amount is calculated by integrating the product of the surface pressure value and each value including the sliding speed value per unit time.

3. the monitoring unit is capable of detecting a discharge pressure of the scroll compressor, When the discharge pressure is lower than the internal compression pressure of the scroll compressor, a value corresponding to the internal compression pressure is set as the surface pressure value, 3. The wear amount calculation device according to claim 1, wherein when the discharge pressure is higher than the internal compression pressure, a value corresponding to the discharge pressure is set as the surface pressure value.

4. the monitoring unit is capable of detecting the number of rotations per unit time of the orbiting scroll or a drive motor that orbits the orbiting scroll, The wear amount calculation device according to claim 1 or 2, wherein a value corresponding to the number of revolutions is set as the sliding speed value.

5. 3. The wear amount calculation device according to claim 1, wherein when the calculated value of the estimated wear amount exceeds a predetermined threshold, a notification operation is executed to notify the user of the fact.

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