Compressor control device and vibration isolation device

Abstract

To provide a vibration control device which warms up quickly, and to provide a vibration-proof device.SOLUTION: A heat pump device 1 includes a compressor 30 as an excitation source. A module 20 including the compressor 30 is elastically supported by a vehicle frame 40 via a vibration-proof member 50 (rubber bushes 51, 52). The module 20 vibrates because of the rotation of the compressor 30. When the rotational frequency of the compressor 30 is resonance frequency, the module 20 vibrates at the resonance frequency. In the resonance frequency, the vibration-proof member 50 resonates by its own elasticity, and deforms greatly. The great deformation of the vibration-proof member 50 promotes warm-up by internal heat generation of the vibration-proof member 50. When a predetermined operation condition is established, a control device operates at the resonance frequency of the compressor 30.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The disclosure in this specification relates to a compressor control device and a vibration isolation device.

Background Art

[0002] Patent Document 1 discloses a vibration isolation device for a compressor as a vibration source. In Patent Document 1, a support base for supporting the compressor is configured by combining rubber members made of rubber materials having different temperature characteristics of loss factors.

[0003] Patent Document 2 proposes a structure in which some of a plurality of elements constituting a refrigeration cycle, particularly a heat pump cycle, are assembled together as a module.

[0004] The description of the prior art documents is incorporated herein by reference as an explanation of the technical elements in this specification.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0006] In the configuration of the prior art documents, it may be difficult to obtain good vibration isolation performance from immediately after the start of the device over a wide range of rubber temperatures or over a wide range of outside air temperatures. For example, the device may be planned so that the vibration isolation device exhibits good vibration isolation performance at a predetermined temperature. In this case, when the temperature of the vibration isolation device is higher or lower than the planned temperature, the expected vibration isolation performance may not be obtained. For example, sufficient vibration isolation performance may not be exhibited at startup in winter when the outside air temperature is low.

[0007] Furthermore, vibration isolation devices supporting devices like those described in Patent Document 2 are required to exhibit the desired vibration isolation performance under loads significantly heavier than those anticipated for this type of device. In particular, in heat pump cycles where high heat output is expected at low temperatures, such as in winter, vibrations caused by the rotation of the compressor become a problem. Vibrations themselves, or the noise they produce, can be unpleasant for users.

[0008] In the respects described above, or in other respects not mentioned, further improvements are needed in the compressor control system and vibration isolation system.

[0009] One of the disclosed objectives is to provide a compressor control device and a vibration isolation device that enable faster warm-up. [Means for solving the problem]

[0010] The compressor control device disclosed herein is elastically supported by an elastic vibration-damping member (50) and controls the rotational speed of an electric compressor (30) that causes the displacement of the vibration-damping member to resonate at the resonant frequency. The compressor control device has a resonant operation mode that adjusts the rotational speed of the electric compressor to the resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency. Furthermore, the resonant operation mode is performed in the low-temperature range within the operating temperature range of the vibration-damping material. The compressor control device disclosed herein is elastically supported by an elastic vibration-damping member (50) and controls the rotational speed of an electric compressor (30) that causes the displacement of the vibration-damping member to resonate at a resonant frequency. The compressor control device has a resonant operation mode that adjusts the rotational speed of the electric compressor to a resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency, and the resonant operation mode is performed to set the resonant rotational speed of the electric compressor according to the temperature (Tb) of the vibration-damping member. The compressor control device disclosed herein is elastically supported by an elastic vibration-damping member (50) and controls the rotational speed of an electric compressor (30) that causes the displacement of the vibration-damping member to resonate at the resonant frequency. The compressor control device has a resonant operation mode that adjusts the rotational speed of the electric compressor to the resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency. Furthermore, in the low-temperature range of the operating temperature range of the vibration-damping member, it has a high-capacity operation mode that increases the rotational speed of the electric compressor above the resonant rotational speed in order to increase the heat output of the heat pump device. The system executes the resonance operation mode when the room temperature (Tr) controlled by the thermal output is below the first temperature (Th1) and the temperature of the vibration-damping member (Tb) is between the second temperature (Th2) and the third temperature (Th3), which is higher than the second temperature. The system executes the high-capacity operation mode when the room temperature (Tr) controlled by the thermal output is below the first temperature (Th1) and the temperature of the vibration-damping member (Tb) is below the second temperature (Th2). The system executes the high-capacity operation mode when the room temperature (Tr) controlled by the thermal output is below the first temperature (Th1) and the temperature of the vibration-damping member (Tb) is above the third temperature (Th3). ru.

[0011] The compressor control device disclosed herein is , electricThe rotational speed of the electric compressor is controlled. The electric compressor is elastically supported by an elastic vibration-damping member. Therefore, due to the elasticity of the vibration-damping member, the displacement of the vibration-damping member resonates at the resonant frequency. When the electric compressor rotates, it becomes an excitation source. The compressor control device has a resonant operation mode. In the resonant operation mode, the rotational speed of the electric compressor is adjusted to the resonant rotational speed. At the resonant rotational speed, the frequency of vibration caused by the rotation of the electric compressor becomes the resonant frequency. As a result, by adjusting the rotational speed of the electric compressor, the vibration-damping member can be made to resonate, and the internal friction during resonance can heat up the vibration-damping member, thus accelerating the warm-up process.

[0012] The vibration isolation device disclosed herein is a vibration isolation device in which an electric compressor (30) or equipment (20) including an electric compressor is elastically supported by an elastic vibration isolation member (50), wherein in a part of the adjustable range of the rotational speed of the electric compressor, the frequency of vibration caused by the rotation of the electric compressor substantially coincides with the resonant frequency at which the displacement of the vibration isolation member resonates. Furthermore, the frequency range of vibrations caused by the rotation of the electric compressor and the resonance frequency range in the low-temperature range of the operating temperature range of the vibration-damping material overlap. Yes, they are.

[0013] According to the vibration isolation device disclosed herein, the electric compressor is elastically supported by an elastic vibration isolation member. Therefore, due to the elasticity of the vibration isolation member, the displacement of the vibration isolation member resonates at the resonant frequency. When the electric compressor rotates, it becomes an excitation source. The compressor control device has a resonant operation mode. In the resonant operation mode, the rotational speed of the electric compressor is adjustable within a predetermined adjustable range. On the other hand, the displacement of the vibration isolation member resonates at the resonant frequency. Within a portion of the adjustable range, the frequency of vibrations caused by the rotation of the electric compressor almost coincides with the resonant frequency. As a result, at the resonant frequency, the vibration isolation member resonates, and internal friction causes the vibration isolation member to heat up, accelerating the warm-up process.

[0014] In the present specification, the plurality of forms disclosed employ different technical means to achieve their respective purposes. The claims and the reference numerals in parentheses described in this section exemplify the correspondence with the parts of the embodiments described later, and are not intended to limit the technical scope. The purposes, features, and effects disclosed in this specification will become clearer by referring to the subsequent detailed description and the accompanying drawings.

Brief Description of the Drawings

[0015] [Figure 1] It is a block diagram of a heat pump device according to the first embodiment. [Figure 2] It is a schematic side view showing a module. [Figure 3] It is a graph showing the relationship between the temperature of the vibration isolation member and the outside air temperature. [Figure 4] It is a graph showing the relationship between the temperature of the vibration isolation member and the material properties. [Figure 5] It is a graph showing the relationship between the loss (loss tangent tanδ) of the vibration isolation member and the amount of deformation. [Figure 6] It is a graph showing the relationship between the temperature of the vibration isolation member and the resonance frequency. [Figure 7] It is a table showing arithmetic expressions. [Figure 8] It is a flowchart showing the operation of the control device. [Figure 9] It is a graph showing the relationship between the control mode, the temperature of the vibration isolation material, and the in-vehicle noise.

Modes for Carrying Out the Invention

[0016] A plurality of embodiments will be described while referring to the drawings. In the plurality of embodiments, functionally and / or structurally, corresponding parts and / or associated parts may be assigned the same reference numerals or reference numerals that differ in the hundreds place or more. For corresponding parts and / or associated parts, the description of other embodiments can be referred to.

[0017] First Embodiment In FIG. 1, the heat pump device 1 provides a temperature control device for a vehicle. The heat pump device 1 provides a vibration control device and a vibration isolation device in this disclosure. The heat pump device 1 circulates a refrigerant and transports heat by utilizing the phase change of the refrigerant. The heat pump device 1 may sometimes be called a refrigeration cycle device. The heat pump device 1 is a vapor compression refrigeration cycle. The temperature control device adjusts the temperature of the temperature control object by supplying cold heat and / or warm heat to the temperature control object. When the temperature control device provides only cold heat, the heat pump device 1 may sometimes be called a refrigeration cycle device. The temperature control object may be air or a liquid such as water. The temperature control object may be an electric circuit or a device such as a battery. For example, the temperature control device is an air conditioner. For example, the temperature control device is a cooling device for a device. The temperature control device may be a heating device for a device.

[0018] In this embodiment, the heat pump device 1 is applied to a vehicle. Instead of this, the heat pump device 1 may be applied to an unmanned moving body that a human does not ride on. Furthermore, the moving body may be a vehicle, a ship, and an aircraft. The heat pump device 1 may be applied to a building fixed to the ground.

[0019] In FIG. 1, the heat pump device 1 provides an air conditioner 2 and a temperature control device 3. The air conditioner 2 conditions the interior of a vehicle as an example of a vehicle. The air conditioner 2 heats or cools the temperature inside the room. The air conditioner 2 adjusts the temperature inside the room to a set temperature. Furthermore, the air conditioner 2 adjusts the humidity inside the room. The temperature control device 3 adjusts the temperature of the battery 16. The battery 16 is a high-voltage secondary battery that supplies power to a motor for driving the vehicle. The temperature control device 3 adjusts the temperature of the battery 16 to a temperature range in which the battery 16 can exhibit its intended function. The temperature control device 3 adjusts the temperature of the battery 16 to a temperature zone suitable for charging and discharging.

[0020] In Figure 1, the heat pump device 1 includes a control device 4. The control device 4 is an electronic control unit (ECU). The control device 4 controls the heat pump device 1 by controlling its components as controlled objects. The control device 4 executes a control method for controlling the heat pump device 1 based on predetermined control characteristics. The control device, or control system, is provided by (a) an algorithm as a set of logics called if-then-else forms, or (b) a trained model tuned by machine learning, such as an algorithm as a neural network.

[0021] The control device is provided by a control system that includes at least one computer. The control system may include multiple computers linked by a data communication device. The computer includes at least one hardware processor (hardware processor). The hardware processor can be provided by (i), (ii), or (iii) below.

[0022] (i) A hardware processor may be at least one processor core that executes a program stored in at least one memory. In this case, a computer is provided by at least one memory and at least one processor core. A processor core is also called a CPU: Central Processing Unit, GPU: Graphics Processing Unit, RISC-CPU, etc. Memory is also called a storage medium. Memory is a non-transitional and tangible storage medium that non-temporarily stores "programs and / or data" that can be read by a processor. Storage mediums are provided by semiconductor memory, magnetic disks, or optical disks, etc. A program may be distributed on its own or as a storage medium on which a program is stored.

[0023] (ii) A hardware processor may be a hardware logic circuit. In this case, the computer is provided by a digital circuit that includes a large number of programmed logic units (gate circuits). Digital circuits are also called logic circuit arrays, e.g., ASIC: Application-Specific Integrated Circuit, FPGA: Field Programmable Gate Array, SoC: System on a Chip, PGA: Programmable Gate Array, CPLD: Complex Programmable Logic Device, etc. Digital circuits may have memory that stores programs and / or data. A computer may be provided by analog circuits. A computer may be provided by a combination of digital and analog circuits.

[0024] (iii) A hardware processor may be a combination of (i) and (ii) above. (i) and (ii) may be located on different chips or on a common chip. In these cases, the (ii) portion is also called an accelerator.

[0025] Control devices, signal sources, and controlled objects provide a variety of elements. At least some of these elements can be called blocks, modules, or sections. Furthermore, elements included in a control system are called functional means only when intentionally used.

[0026] In Figure 1, the heat pump device 1 includes a plurality of sensors and a plurality of actuators for providing a control system. The plurality of sensors may include a switch for inputting a command to start air conditioning operation. The plurality of sensors may include a temperature sensor for detecting at least the indoor air temperature. The plurality of sensors may include a temperature sensor for detecting at least the temperature of a vibration-isolating member. The plurality of actuators may include a motor 31 for rotating a compressor as an excitation source. The plurality of actuators may include a control device 4, which includes an inverter circuit or the like for controlling the rotational speed of the motor 31 that rotates the compressor.

[0027] In Figure 1, the heat pump device 1 provides at least one cooling output. Furthermore, it is desirable that the heat pump device 1 provides one cooling output (cold) and one heating output (heat). In addition, in this embodiment, the heat pump device 1 provides one cooling output for air conditioning, one heating output for air conditioning, and one temperature control output (cold or heat) for temperature control of equipment. The temperature control output can be either a cooling output or a heating output.

[0028] In Figure 1, the heat pump device 1 includes an outdoor heat exchanger 5 as an unused heat exchanger. The outdoor heat exchanger 5 is also called a condenser or heat radiator. The outdoor heat exchanger 5 provides heat exchange between the outdoor air and the refrigerant.

[0029] In Figure 1, the heat pump device 1 includes a first indoor heat exchanger 6 as one of several user-side heat exchangers. The first indoor heat exchanger 6 is also called an evaporator or cooler. The first indoor heat exchanger 6 is housed in the air conditioning case 7 of the air conditioning device 2. The air conditioning case 7 includes a blower fan and forms a duct through which air for air conditioning flows. The first indoor heat exchanger 6 provides heat exchange between the air for air conditioning and the refrigerant. The air is air that is blown into the room. The first indoor heat exchanger 6 cools and dehumidifies the air supplied to the room. The first indoor heat exchanger 6 provides the cooling output for air conditioning from among the multiple heat outputs provided by the heat pump device 1.

[0030] In this embodiment, the first indoor heat exchanger 6 directly exchanges heat between the air to be temperature controlled and the refrigerant. Alternatively, the first indoor heat exchanger 6 may be configured to provide indirect heat exchange, as in the heating medium system described later. In this case, the first indoor heat exchanger 6 is configured to exchange heat with a heat medium that exchanges heat with the air.

[0031] In Figure 1, the heat pump device 1 includes a first medium heat exchanger 8 as one of several user-side heat exchangers. The first medium heat exchanger 8 is also called a condenser or heater. The first medium heat exchanger 8 provides heat exchange between the heat medium circulating in the heating medium system 9 and the refrigerant. The heating medium system 9 is a circulation system that circulates a heat medium such as water. The heating medium system 9 includes a pump 10 that circulates the heat medium. The heating medium system 9 includes a second indoor heat exchanger 11. The second indoor heat exchanger 11 is also called a heater. The second indoor heat exchanger 11 is housed in the air conditioning case 7 of the air conditioning device 2. The second indoor heat exchanger 11 provides heat exchange between the air for air conditioning and the heat medium. The second indoor heat exchanger 11 heats the air supplied to the room. As a result, the heat pump device 1 indirectly heats the air supplied to the room by the heating medium system 9. The heating medium system 9 provides a heating output for air conditioning from among the multiple heat outputs provided by the heat pump device 1.

[0032] In Figure 1, the first indoor heat exchanger 6 is located upstream of the second indoor heat exchanger 11. The second indoor heat exchanger 11 is located downstream of the first indoor heat exchanger 6. At least a portion of the air that has passed through the first indoor heat exchanger 6 passes through the second indoor heat exchanger 11. The temperature of the air blown into the room can be adjusted by the flow rate of the heat transfer medium in the heating medium system 9. Alternatively, the temperature of the air blown into the room may be adjusted by an air mix door located inside the air conditioning case 7. The air mix door adjusts the amount of air that passes through the second indoor heat exchanger 11 and the amount of air that bypasses the second indoor heat exchanger 11.

[0033] In Figure 1, the heat pump device 1 includes a second medium heat exchanger 12 as one of several user-side heat exchangers. The second medium heat exchanger 12 is also called a chiller, evaporator, or cooler. The second medium heat exchanger 12 provides heat exchange between the heat medium circulating in the cooling medium system 13 and the refrigerant. The cooling medium system 13 is a circulation system that circulates a heat medium such as water. The cooling medium system 13 includes a pump 14 that circulates the heat medium. The cooling medium system 13 includes an equipment heat exchanger 15. The equipment heat exchanger 15 is also called a cooler. The equipment heat exchanger 15 is positioned to be thermally coupled with the battery 16, which is the object to be temperature controlled. The equipment heat exchanger 15 provides heat exchange between the battery 16 and the heat medium, either directly or indirectly. The equipment heat exchanger 15 cools the battery 16. As a result, the heat pump device 1 indirectly cools the battery 16 through the cooling medium system 13. The cooling medium system 13 provides a cooling output for the equipment from among the multiple heat outputs provided by the heat pump device 1.

[0034] The second medium heat exchanger 12 may also function as a condenser or heater of the heat pump device 1. In this case, the cooling medium system 13 cools or heats the battery 16 and is therefore also called the temperature control medium system 13. As a result, the heat pump device 1 indirectly regulates the temperature of the battery 16 through the temperature control medium system 13. The temperature control medium system 13 provides cooling output and heating output for the equipment from among the multiple heat outputs provided by the heat pump device 1.

[0035] In Figure 1, the heat pump device 1 comprises a module 20 including cyclic equipment for constituting the heat pump. The module 20 includes at least conduits 22 for connecting the cyclic equipment and is also called a conduit module. For example, the module 20 has an aluminum die-cast component that provides the conduits 22. The cyclic equipment includes a plurality of components for constituting the heat pump device 1. The cyclic equipment may include, for example, at least one of a compressor, a valve device, an accumulator, an internal heat exchanger, and a medium heat exchanger.

[0036] In module 20, the conduit 22 and the cyclic equipment may be connected by non-disassemblable connecting members such as welds or brazes. Furthermore, in module 20, the conduit 22 and the cyclic equipment may be connected by disassemblable connecting members such as bolts, pipe fittings, or snap-fits. In either case, module 20 is configured to be handled by an operator as a single unit.

[0037] In Figure 1, in this embodiment, module 20 includes at least a compressor 30. The compressor 30 is a device that compresses and circulates the refrigerant. The compressor 30 includes a motor 31 that rotates the compressor 30. The compressor 30 and motor 31 are sometimes referred to as an electric compressor. Furthermore, module 20 may include a valve device. The valve device may include an expansion valve for evaporating the refrigerant. Furthermore, the valve device may include on-off valves, three-way switching valves, opening control valves, etc., for controlling the flow of refrigerant in the cycle. Furthermore, module 20 may include an accumulator that provides a reservoir of refrigerant in the cycle. Furthermore, module 20 may include a first medium heat exchanger 8. Furthermore, module 20 may include a second medium heat exchanger 12.

[0038] For information regarding the form of module 20 and the cyclic equipment included in module 20, please refer to Japanese Patent Application Publication No. 2022-190675 (Patent Document 2). The contents of Japanese Patent Application Publication No. 2022-190675 are incorporated by reference as explanations of the technical elements in this specification.

[0039] Figure 2 is a schematic side view of module 20. In the following description, the term module 20 refers to an integrated unit containing multiple cyclic components. Module 20 has multiple conduits 22 formed within a module body 21. The module body 21 is provided by a die-cast aluminum component or a resin component with embedded piping. The multiple conduits 22 provide refrigerant passages for the heat pump cycle. The multiple conduits 22 fluidly connect the multiple components located in module 20.

[0040] In Figure 2, module 20 includes a compressor 30. Module 20 includes brackets 23 for supporting the compressor 30. Module 20 includes multiple brackets 23. On the other hand, the compressor 30 also includes support brackets 32. The compressor 30 includes multiple brackets 32. The brackets 32 extend radially from the rotation axis AX of the compressor 30. The brackets 32 extend so as to protrude radially from the cylindrical body of the compressor 30. As a result, vibrations associated with the rotation of the compressor 30 may be amplified and transmitted to module 20. The compressor 30 is supported by module 20 by the mechanical connection between brackets 32 and brackets 23.

[0041] In Figure 2, a rubber bushing 51, acting as a vibration damping member 50, is positioned between bracket 23 and bracket 32. The bushing 51 is an elastic member that suppresses the transmission of vibrations between module 20 and compressor 30. The bushing 51 is primarily provided to suppress the transmission of vibrations to module 20 associated with the rotation of compressor 30. Therefore, compressor 30 is elastically supported by module 20.

[0042] In Figure 2, module 20 includes piping 24 that fluidly connects module 20 to compressor 30. The passages in piping 24 are fluidly connected to conduit 22 within module 20. Module 20 includes a refrigerant container 25 for storing refrigerant. The refrigerant container 25 is also called an accumulator. Module 20 includes piping 26 that fluidly connects module 20 to refrigerant container 25. The passages in piping 26 are fluidly connected to conduit 22 within module 20. Module 20 includes a valve device 27. Module 20 includes a plurality of valve devices 27. The valve device 27 may be, for example, an expansion valve for expanding the refrigerant. Furthermore, module 20 includes a second medium heat exchanger 12.

[0043] In Figure 2, the cyclic equipment, including the compressor 30, is connected to the module body 21 by connecting members such as bolts. As a result, a cyclic module that can be handled as a single unit is provided.

[0044] In Figure 2, module 20 includes a bracket 28. The bracket 28 is provided as part of module body 21 and is made of a material continuous with module body 21. The bracket 28 provides a fixing portion for fixing module 20 to vehicle frame 40, which is the object to be fixed. Vehicle frame 40 also includes a bracket 41. Module 20 is supported by vehicle frame 40 by the mechanical connection of bracket 28 and bracket 41.

[0045] In Figure 2, a rubber bush 52, acting as a vibration damping member 50, is positioned between bracket 28 and bracket 41. The bush 52 is an elastic member that suppresses the transmission of vibrations between module 20 and vehicle frame 40. The bush 52 is primarily provided to suppress the transmission of vibrations to vehicle frame 40 associated with the rotation of compressor 30. Therefore, compressor 30 is elastically supported by vehicle frame 40 via bush 51 and bush 52. Module 20 is also elastically supported by vehicle frame 40 via bush 52.

[0046] In this embodiment, the vibration-damping member 50 is made of rubber. Alternatively, the vibration-damping member 50 may be made of elastomer, a metal spring, or the like. The bushings 51 and 52 can be provided in a variety of shapes, such as plate-shaped, cylindrical, or cylindrical.

[0047] In the following explanation, the vibration-damping member 50 primarily refers to the bush 52. When discussing the vibration of the compressor 30 relative to the module body 21, the vibration-damping member 50 primarily refers to the bush 51. The vibration-damping member 50 is an elastic body that resonates due to its own elastic properties and can deform relatively large in the resonant state. In contrast, the compressor 30 and the vehicle frame 40 are rigid bodies that are significantly less prone to deformation, and their deformation can be considered zero (0).

[0048] In Figure 2, the compressor 30 is elastically supported by an elastic vibration-damping member 50. The compressor 30 causes the displacement of the vibration-damping member 50 to resonate at the resonant frequency fr. The displacement of the vibration-damping member 50 caused by the vibration of the compressor 30 is maximized by resonance. In this embodiment, the support structure by the vibration-damping member 50 provides a vibration isolation device. In the vibration isolation device, the compressor 30, or the module 20 as equipment including the compressor 30, is elastically supported by the elastic vibration-damping member 50.

[0049] In Figure 1, the heat pump device 1, when operated, provides multiple operating modes. These operating modes include, for example, a cooling mode for cooling the interior of the vehicle. Other operating modes include, for example, a cooling mode for cooling the interior of the vehicle while simultaneously cooling the battery 16. Other operating modes include, for example, a heating mode for heating the interior of the vehicle. Other operating modes include, for example, a heating mode for heating the interior of the vehicle while simultaneously cooling the battery 16. Other operating modes include, for example, a cooling mode for cooling only the battery 16. Furthermore, the operating modes may include modes that provide cooling dehumidification or heating dehumidification instead of cooling or heating.

[0050] In each of these multiple operating modes, the compressor 30 is operated. In the operating mode in which the compressor 30 is operated, the motor 31 shown in Figure 1 rotates, and the refrigerant compression mechanism of the compressor 30 rotates. This rotation of the motor 31 and the rotation of the refrigerant compression mechanism are called the rotation of the compressor 30. Due to the rotation of the compressor 30, the compressor 30 vibrates. The compressor 30 is the source of vibration.

[0051] In Figure 2, the compressor 30 is elastically supported in the module 20 on the module body 21 via a bush 51. Vibrations from the compressor 30 are transmitted from the compressor 30 to the module 20 via the bush 51. The compressor 30 and the module body 21 are elastically connected by the bush 51. Therefore, the compressor 30 vibrates relative to the module body 21. Furthermore, the compressor 30 may vibrate resonantly with respect to the module body 21 due to the elasticity of the bush 51.

[0052] In Figure 2, the module 20, including the compressor 30, is elastically supported on the vehicle frame 40 via bushings 52. Vibrations from the module 20, including the compressor 30, are transmitted to the vehicle frame 40 via the bushings 52. The module 20, including the compressor 30, and the vehicle frame 40 are elastically connected by the bushings 52. Therefore, the module 20, including the compressor 30, vibrates relative to the vehicle frame 40. Furthermore, the module 20, including the compressor 30, may vibrate resonantly with respect to the vehicle frame 40 due to the elasticity of the bushings 52.

[0053] In Figure 2, the vibration of the compressor 30, either its own vibration or the noise it produces, may cause discomfort to vehicle users. Furthermore, the vibration of the module 20 caused by the vibration of the compressor 30, either its own vibration or the noise it produces, may cause discomfort to vehicle users. Additionally, the vibration of the vehicle frame 40 caused by the vibration of the compressor 30, either its own vibration or the noise it produces, may cause discomfort to vehicle users. Moreover, resonance in various parts caused by the vibration of the compressor 30 may also cause discomfort to vehicle users.

[0054] In Figure 2, the vibration-damping member 50, including bushings 51 and 52, suppresses vibration transmission by elastically deforming. The properties of the vibration-damping member 50 are sometimes referred to as elastic or viscoelastic. In this embodiment, viscoelasticity is included and referred to as elastic. The ease with which the vibration-damping member 50 deforms in response to vibration and its flexibility in response to vibration have temperature characteristics. Generally, the vibration-damping member 50 is less deformable at low temperatures and more deformable at high temperatures.

[0055] Figure 3 shows the relationship between the temperature Tb of the vibration-damping member and the ambient temperature Tam. The temperature Tb of the vibration-damping member 50 at the start of the heat pump device 1 is thought to depend on the ambient temperature Tam. Therefore, in areas where the ambient temperature Tam is low, or during low temperatures such as winter, the vibration-damping member 50 may not exhibit the expected vibration-damping effect immediately after the heat pump device 1 is started. Furthermore, immediately after the heat pump device 1 is started, a relatively large heat output may be required. For example, an operating mode that provides maximum heating capacity, such as a heat boost operation mode, may be executed. In the operating mode that provides maximum heating capacity, the compressor 30 is operated at a relatively high rotational speed. In one example, the compressor 30 is operated at its maximum rotational speed Nm. In this case, the vibration of the compressor 30 is transmitted without being attenuated by the bushings 51 and 52, and the vibration or noise is easily perceived by the user.

[0056] Figure 4 shows the relationship between the temperature Tb of the vibration-damping member and the material property K. The solid line shows the properties of the high-loss material H. The dashed line shows the properties of the low-loss material L. The material property is stiffness. Stiffness is sometimes evaluated as the static spring constant. Loss is the loss tangent tanδ, which is an index for evaluating viscoelasticity. The high-loss material H is a material with higher loss than the low-loss material L. The vibration-damping member 50 exhibits higher stiffness K as the temperature Tb decreases. Stiffness K as a material property has the characteristic of increasing at lower temperatures. At the same temperature Tb, the high-loss material H exhibits higher stiffness K than the low-loss material L. From this, it can be seen that in the region where stiffness K is high, the vibration-damping member 50 cannot sufficiently exhibit vibration damping effect.

[0057] When the ambient temperature Tam is low and the temperature Tb of the vibration-damping member 50 tends to be low, it is necessary to raise the temperature Tb of the vibration-damping member 50. In this embodiment, the vibration-damping member 50 is deformed relatively significantly by resonant vibrations caused by vibrations associated with the rotation of the compressor 30. As a result, the temperature of the vibration-damping member 50 rises due to frictional heat inside the vibration-damping member 50, and its vibration damping capacity is enhanced. Resonant vibrations may manifest as behavior of the compressor 30. In addition, resonant vibrations may manifest as behavior of the module 20 including the compressor 30.

[0058] Figure 5 shows the relationship between the loss (loss tangent tanδ) and deformation W of the vibration-damping member 50. The higher the loss of the vibration-damping member 50, the smaller the deformation W. That is, a material with loss L1 has a deformation of W2. In contrast, a material with lower loss L2 has a deformation of W1. Therefore, by using a material with low loss, a large deformation can be obtained in conjunction with resonance, and a large temperature rise can be obtained due to internal friction. Moreover, as explained in Figure 4, the stiffness K of a material with high loss (high-loss material H) increases rapidly as the temperature decreases. Therefore, a material with low loss can obtain a large deformation even at low temperatures. Thus, it is desirable to use a material with relatively low loss. Specifically, a material with a loss tangent tanδ = 0.1 or less is desirable.

[0059] Figure 6 shows the relationship between the temperature Tb of the vibration-isolating member and the resonant frequency fr. The solid line shows the characteristics of the high-loss material H. The dashed line shows the characteristics of the low-loss material L. The vibration-isolating member 50 exhibits a higher resonant frequency fr as the temperature Tb decreases. For example, consider the case where the temperature Tb of the vibration-isolating member 50 changes between Tb1 and Tb2. In this case, the fluctuation range fH of the resonant frequency fr of the high-loss material H is significantly larger than the fluctuation range fL of the resonant frequency fr of the low-loss material L. The fluctuation range of the resonant frequency fr of the high-loss material H with respect to temperature changes is greater than the fluctuation range of the resonant frequency fr of the high-loss material H with respect to temperature changes. Therefore, the range over which the resonant frequency fr can be changed becomes excessively wide. The adjustable range of the rotational speed Nc of the compressor 30 as an excitation source is limited. Therefore, it is desirable for the fluctuation range of the resonant frequency fr to be small. From this viewpoint, the use of the low-loss material L is desirable.

[0060] Here, the vibration-damping member 50 is selected with the assumption that it will be used within a predetermined operating temperature range. The operating temperature range is, for example, from -50°C as an extremely low temperature to +60°C as a high temperature. Note that the operating temperature range can be set arbitrarily. By causing the vibration-damping member 50 to resonate in the low-temperature range of this operating temperature range, the warm-up of the vibration-damping member 50 is accelerated. The frequency of vibrations caused by the rotation of the compressor 30 can be adjusted within a predetermined range depending on the rotational speed of the compressor 30. Therefore, the range of vibration frequencies caused by the rotation of the compressor 30 and the range of the resonance frequency fr in the low-temperature range of the operating temperature range of the vibration-damping member 50 overlap. By having this overlapping range, the vibration-damping member 50 can utilize the vibration of the compressor 30 to resonantly accelerate its warm-up.

[0061] Equation 1 in Figure 7 is the formula for calculating the resonant frequency fr. Equation 1 can also be written as fr = 1 / (2π)√(K / M). Equation 1 can also be written as fr = 1 / (2π)(K / M)^1 / 2. The variable K is the static spring constant (N / m) (stiffness) of the vibration isolation member 50. The variable M is the weight of the object (Kg). When considering the bush 51, the weight of the compressor 30 is used as the weight of the object (Kg). When considering the bush 52, the weight of the module 20 including the compressor 30 is used as the weight of the object (Kg). In this embodiment, weight M is the total weight of multiple cycle equipment included in module 20. The weight of module 20 can be in the range of 10 kg to 50 kg, or in the range of 20 kg to 40 kg. The multiple cycle equipment includes the compressor 30. Considering that typical electric compressors weigh less than 10 kg, in this embodiment, the significantly heavier module 20 is elastically supported by the vibration-damping member 50. This is because, in this embodiment, the vibration-damping device and the compressor control device are designed to cause the bush 52 to deform significantly due to resonance, thereby promoting a temperature rise in the bush 52. The setting of the resonant frequency fr may be performed using only some of the cyclic equipment included in the module 20. For example, only the module body 21 and some of the cyclic equipment may be the dominant elements of the resonance of the module 20 that can vibrate on the vibration isolation member 50 (bush 52).

[0062] Equation 2 in Figure 7 shows the nth-order component frequency fn at the rotational speed Nc of the compressor 30. The order n is a natural number greater than or equal to 1. Equation 2 can also be written as fn = Nc / 60 × n. By matching the main nth-order component frequency fn of the vibration components of the compressor 30 to the resonance frequency fr, the vibration isolation member 50 can be made to vibrate relatively large using the nth-order component frequency fn. For example, the order n can be set to 1. Alternatively, the order n may be set to 2, 3, 4, etc., targeting resonance in harmonics. As a result, the temperature Tb of the vibration isolation member 50 can be rapidly increased by internal friction due to the relatively large vibration of the vibration isolation member 50.

[0063] Equation 3 in Figure 7 is a calculation formula for evaluating the amount of deformation, i.e., the amplitude x, in the vibration-damping member 50. Equation 3 can also be written as x = a / (2πf)^2, where a is the acceleration (m / s^2), and a is a constant value determined experimentally. F is the vibration frequency (Hz).

[0064] By operating the compressor 30 at a predetermined target rotational speed Ntg, the nth-order component frequency fn of the compressor 30's vibration can be made to nearly match the resonant frequency fr. This allows the amplitude of the vibration-damping member 50 to be nearly maximized.

[0065] Returning to Figure 6, if the temperature Tb of the vibration-damping member 50 gradually increases, the resonant frequency fr gradually decreases. Therefore, in order to maintain the resonant state over a long period of time, it is necessary to change the target rotational speed ft of the compressor 30 in accordance with the change (increase) in the temperature Tb of the vibration-damping member 50.

[0066] The rotational speed Nc of the compressor 30 is adjustable within an adjustable range from a minimum rotational speed Nmin to a maximum rotational speed Nmax. The minimum rotational speed Nmin and the maximum rotational speed Nmax are set as rotational speeds that enable the heat pump device 1 to function. In this embodiment, within a portion of the adjustable range, the frequency of vibration caused by the rotation of the compressor 30 approximately coincides with the resonant frequency fr at which the displacement of the vibration-damping member 50 resonates. This "approximate coincidence" allows for an error range in which the vibration caused by the rotation of the compressor 30 resonates the vibration-damping member 50.

[0067] Figure 8 is a flowchart illustrating the operation of the control device 4. The control device 4 provides the compressor control device in this disclosure. The control device 4 controls the rotational speed of the compressor 30. The flowchart is executed repeatedly from the start of operation of the heat pump device 1. In step 100, when the operation of the heat pump device 1 starts, the control device 4 starts executing the program.

[0068] In step 101, the control device 4 acquires an input signal indicating the operating state of the heat pump device 1 from a plurality of sensors. The input signal includes a signal indicating the indoor temperature Tr. The input signal includes a signal indicating the temperature Tb of the vibration isolation member 50. Note that the temperature Tb may be directly detected or indirectly estimated. For example, a temperature sensor can be directly provided on the vibration isolation member 50. Instead of this, for example, the temperature Tb of the vibration isolation member 50 may be estimated to gradually increase from the outside air temperature Tam to a predetermined stable temperature. Further, the input signal includes a signal indicating the rotational speed of the compressor 30. Note that the rotational speed may be directly detected or indirectly estimated. For example, a rotational speed sensor can be directly provided on the compressor 30. Instead of this, for example, the rotational speed may be estimated from the drive signal of the inverter circuit that drives the motor 31.

[0069] In step 102, the control device 4 compares the vehicle interior temperature Tr with the first temperature Th1. Here, it is determined whether the vehicle interior temperature Tr is higher than the first temperature Th1. The first temperature Th1 is a temperature for determining whether rapid heating is required. Rapid heating is provided, for example, by the maximum heating capacity called the heat boost operation mode. When the vehicle interior temperature Tr is higher than the first temperature Th1 (Th1 < Tr), the process proceeds to step 103. When the vehicle interior temperature Tr is less than or equal to the first temperature Th1 (Th1 ≥ Tr), the process proceeds to step 105.

[0070] In step 103, the control device 4 calculates the required heat output and sets the rotational speed of the compressor 30 for obtaining the required heat output. The rotational speed of the compressor 30 for obtaining the required heat output is called the heat output rotational speed. The heat output rotational speed includes not only the rotational speed required to obtain the heat output for air conditioning but also the heat output required to appropriately maintain the temperature of the battery 16. Further, the heat output includes both the supply of cold heat and the supply of warm heat.

[0071] In step 104, the control device 4 normally operates the heat pump device 1. Here, the compressor 30 is operated at the heat output rotation speed set in step 103. Thereby, the heat pump device 1 executes air conditioning control to approach and maintain a comfortable indoor space, and temperature control of the battery 16.

[0072] When branching from step 102 to step 105, the control device 4 compares the temperature Tb of the vibration isolator 50 with the second temperature Th2 and the third temperature Th3 in step 105. Here, it is determined whether the temperature Tb is between the second temperature Th2 and the third temperature Th3. The third temperature Th3 is higher than the second temperature Th2 (Th2 < Th3). When the temperature Tb is between the second temperature Th2 and the third temperature Th3 (Th2 < Tb < Th3), the process proceeds to step 106. When the temperature Tb is not between the second temperature Th2 and the third temperature Th3 (Th2 ≥ Tb or Tb ≥ Th3), the process proceeds to step 108.

[0073] In step 106, the control device 4 sets the resonance frequency fr based on the temperature Tb of the vibration isolator 50 and Equations 1 in FIGS. 6 and 7. Equations 1 in FIGS. 6 and 7 can be stored in the control device 4 as a map. In this case, the map is a temperature-resonance frequency map having the temperature Tb of the vibration isolator 50 as an input variable and the resonance frequency fr as an output variable. In step 106, by referring to the temperature-resonance frequency map, the resonance frequency fr corresponding to the temperature Tb is set. In this case, the rotation speed Nc of the compressor 30 in the resonance operation mode is set by a map having the temperature Tb as an input variable and the resonance rotation speed Nr as an output variable.

[0074] Step 106 may store the temperature dependency of the vibration isolator 50 shown in FIG. 6 in the control device 4 as a temperature-characteristic map. In this case, the control device 4 sets the static spring constant K (N / m) of the vibration isolator 50 from the temperature-characteristic map. Further, the control device 4 sets the resonance frequency fr by executing the calculation of Equation 1.

[0075] Furthermore, in step 106, the control device 4 sets the resonant rotational speed Nr of the compressor 30 such that the resonant frequency fr approximately matches the frequency fn of the main nth-order component among the vibration components of the compressor 30. It is desirable that the resonant frequency fr and the nth-order component frequency fn perfectly match, but there may be an error within a range in which the effect of heating the vibration-damping member 50 is recognized. The order n is selected taking into consideration the effect of heating the vibration-damping member 50.

[0076] The control device 4 may superimpose a beat component corresponding to the resonant frequency fr onto the rotational speed Nc of the compressor 30. For example, by modulating the rotational speed Nc of the compressor 30 with a low frequency of about 10 Hz to 100 Hz, vibrations at the resonant frequency fr can be generated in the module 20. If the rotational speed Nc of the compressor 30 is set too low, the thermal output will be impaired. In contrast, by superimposing a beat component to generate behavior at the resonant frequency fr, the thermal output can be maintained while promoting the warm-up of the vibration-damping member 50.

[0077] In step 107, the control device 4 operates the compressor 30 in resonant operation mode. At this time, the compressor 30 is operated at a resonant rotational speed Nr that is lower than the maximum rotational speed Nm available for use as a heat pump device 1 (Nm > Nr). The control device 4, as a compressor control device, has a resonant operation mode. In resonant operation mode, the control device 4 adjusts the rotational speed Nc of the compressor 30 to the resonant rotational speed Nr so that the vibration caused by the rotation of the compressor 30 becomes the resonant frequency fr. The resonant operation mode is performed in the low-temperature range of the operating temperature range of the vibration-damping member 50. Moreover, the resonant mode is performed only in the initial startup phase when the vibration-damping member 50 has not yet warmed up. In this embodiment, the low-temperature range of the operating temperature range of the vibration-damping member 50 may be a range where the temperature Tb of the vibration-damping member 50 is less than the first temperature Th1 and higher than the lowest temperature of the operating temperature range (e.g., -50°C). Furthermore, the low-temperature range may be a range where the temperature Tb of the vibration-damping member 50 is 0°C or lower.

[0078] The resonant operation mode is performed during the period when the temperature Tb is between the second temperature Th2 and the third temperature Th3. For example, the resonant operation mode is performed during the period when the temperature Tb gradually rises from the second temperature Th2 to the third temperature Th3. During this period of resonant operation mode, the resonant rotational speed Nr is continuously updated as the temperature Tb rises. The resonant operation mode is performed to set the resonant rotational speed Nr of the compressor 30 according to the temperature Tb of the vibration-damping member 50. As a result, the vibration-damping member 50 vibrates relatively strongly and is continuously heated by internal heat generation throughout the period during which the resonant operation mode is performed. Therefore, the temperature Tb of the vibration-damping member 50 can be rapidly increased in the range from the second temperature Th2 to the third temperature Th3.

[0079] In this embodiment, even if the temperature Tb of the vibration-damping member 50 changes during the period when the temperature Tb is between the second temperature Th2 and the third temperature Th3, a resonant rotational speed corresponding to the temperature Tb is set. The characteristics of the vibration-damping member 50, particularly its rigidity, shift in accordance with the change in temperature Tb. In this embodiment, the resonant rotational speed corresponding to the temperature Tb is repeatedly set. Therefore, the vibration-damping member 50 (bush 52) continues to tolerate resonant vibrations for a predetermined period of time. The vibration-damping member 50 (bush 52) generates heat due to the relatively large deformation caused by resonance, promoting a temperature rise in the vibration-damping member 50. Moreover, the vibration-damping member 50 continuously maintains a resonant state. As a result, the vibration-damping member 50 is quickly warmed up to a temperature range of the third temperature Th3 or higher, where it can exhibit a high vibration-damping effect.

[0080] If the temperature Tb of the vibration-damping member 50 is below the second temperature Th2, the control device 4 executes the high-capacity operation mode in step 108. In the high-capacity operation mode, the target rotational speed Ntg of the compressor 30 is set to the highest rotational speed Nmax available at that time. The high-capacity operation mode provides, for example, rapid heating that rapidly increases the temperature inside the vehicle. The high-capacity operation mode is also called, for example, the heat boost operation mode. Therefore, if the temperature Tr inside the vehicle is lower than the first temperature Th1 and the temperature Tb of the vibration-damping member 50 is below the second temperature Th2, the control device 4 executes the high-capacity operation mode without executing the resonance operation mode.

[0081] If the temperature Tb of the vibration-damping member 50 is 3rd temperature Th3 or higher, the control device 4 executes the high-capacity operation mode in step 108. Therefore, if the cabin temperature Tr is lower than the 1st temperature Th1 and the temperature Tb of the vibration-damping member 50 is 3rd temperature Th3 or higher, the control device 4 executes the high-capacity operation mode without executing the resonant operation mode. Thus, the control device 4 as a compressor control device has a high-capacity operation mode. In the high-capacity operation mode, in the low-temperature range of the operating temperature range of the vibration-damping member 50, the rotational speed Nc of the compressor 30 is increased above the resonant rotational speed Nr in order to increase the heat output of the heat pump device 1.

[0082] The control device 4 executes the resonance operation mode when the indoor temperature Tr, which is regulated by the heat output, is below the first temperature Th1 (step 102), and the temperature Tb of the vibration-damping member 50 is between the second temperature Th2 and the third temperature Th3, which is higher than the second temperature. The control device 4 executes the high-capacity operation mode when the indoor temperature Tr, which is regulated by the heat output, is below the first temperature Th1, and the temperature Tb of the vibration-damping member 50 is below the second temperature Th2. The control device 4 executes the high-capacity operation mode when the indoor temperature Tr, which is regulated by the heat output, is below the first temperature Th1, and the temperature Tb of the vibration-damping member 50 is above the third temperature Th3, which is higher than the second temperature Th2. By executing the resonance operation mode in the high-capacity operation mode, it is possible to achieve both the effect of heat output in the high-capacity operation mode and the effect of noise reduction due to accelerated warm-up in the resonance operation mode.

[0083] Step 102 provides a function of the control device 4 to determine that the indoor air to be air-conditioned is in a low-temperature environment. Step 102 also provides a function of the control device 4 to determine that it is the initial stage of air conditioning, particularly heating operation. Step 105 provides a function of the control device 4 to determine whether the temperature Tb of the vibration-damping member 50 is in a low-temperature state below a predetermined temperature (third temperature Th3). Furthermore, step 105 provides a function of the control device 4 to determine whether the temperature Tb of the vibration-damping member 50 is in an extremely low-temperature state below a predetermined temperature (second temperature Th2). The outside air temperature Tam affects both the in-vehicle temperature Tr and the temperature Tb of the vibration-damping member 50. At the start of heating, the in-vehicle temperature Tr may be equal to the outside air temperature Tam, and the temperature Tb of the vibration-damping member 50 may also be equal to the outside air temperature Tam. Therefore, in a low-temperature environment where the in-vehicle temperature Tr is below the first temperature Th1, it is assumed that the temperature Tb of the vibration-damping member 50 is also in a low-temperature state below the third temperature Th3. In this case, when the temperature Tb of the vibration-damping member 50 is below the second temperature Th2 (an extremely low temperature state), the outside air temperature Tam is also considered to be extremely low, so step 108 is performed to promote heating, even if vibration or noise is tolerated. On the other hand, when the temperature Tb of the vibration-damping member 50 is above the second temperature Th2 and below the third temperature Th3 (a low temperature state), the outside air temperature Tam is also considered to be low, or the vibration-damping member 50 is considered to be in the warm-up process, so step 107 is performed to suppress vibration or noise, even if a decrease in heating capacity is tolerated. The first temperature Th1 is also a threshold for determining whether high-capacity operation is necessary. In this case, by setting the second temperature Th2 to be below the first temperature Th1, high-capacity operation can be performed, followed by resonance operation, and then high-capacity operation can be performed again. Alternatively, both the second temperature Th2 and the third temperature Th3 may be set to be below the first temperature Th1 (Th2 <Th3≦Th1)。

[0084] Furthermore, the in-vehicle temperature Tr and the temperature Tb of the vibration-damping member 50 may have a correlation when they change from a state where they are in equilibrium with respect to the outside air temperature Tam (for example, Tam=Tr=Tb). For example, consider the case where the outside air temperature Tam is low enough to require heating. When the outside air temperature Tam is low enough to require heating, it may be considered to be in the low-temperature range of the operating temperature range of the vibration-damping member 50. In this case, the in-vehicle temperature Tr gradually rises after heating is started and stabilizes at a set temperature set by the user near ambient temperature. On the other hand, the temperature Tb gradually rises due to the heat generated by the vibration-damping member 50 itself and heat received from surrounding equipment, and stabilizes at an equilibrium temperature determined according to the outside air temperature Tam. Therefore, it can be said that the changes in in-vehicle temperature Tr and temperature Tb have a correlation with the tendency to gradually rise from low temperatures. Such a correlation can be grasped by experimentally measuring it in advance. In this embodiment, the first temperature Th1, the second temperature Th3, and the third temperature Th3 are set so that when the in-vehicle temperature Tr and temperature Tb are correlated, the warming of the vibration-damping member 50 is promoted to suppress vibration transmission and noise.

[0085] Thus, the resonant operation mode is provided only when the temperature Tb of the vibration-damping member 50 is within a specific range. If the temperature Tb of the vibration-damping member 50 is not within the specific range, the high-capacity operation mode is provided without the resonant operation mode. Therefore, in the range where the heating effect of the vibration-damping member 50 due to the use of the resonance phenomenon is not provided, the high-capacity operation mode can be used to prioritize heating the interior of the vehicle. From another perspective, the vibration-damping member 50 can be efficiently heated by utilizing the resonance phenomenon only in the range where the heating effect of the vibration-damping member 50 can be obtained.

[0086] The control device 4 appropriately controls the operation of the heat pump device 1 by repeating the process in steps 101-108.

[0087] Figure 9 shows the control mode, vibration isolation material temperature, and changes in in-vehicle noise. The graph, from top to bottom, shows the in-vehicle noise S, which is the audible sound transmitted into the vehicle and reached the user's ears, the temperature Tb of the vibration isolation member 50, and the control mode MODE. The sequence of control mode MODE corresponds to steps 104, 107, and 108 in Figure 8. The solid line shows the behavior according to this embodiment. The dashed line shows the behavior of a comparative example that does not include steps 105, 106, and 107. That is, the comparative example continues only in high-capacity operation mode until the indoor temperature Tr reaches the first temperature Th1.

[0088] The diagram shows the case where the operation of the heat pump device 1 is started at time t0. The heat pump device 1 is started in a low-temperature environment where the in-vehicle temperature Tr is lower than the first temperature Th1 and also lower than the third temperature Th3. When the control device 4 starts control at time t0, the control process proceeds to step 108. In step 108, the high-capacity operation mode is executed. For example, the compressor 30 is operated at the maximum available rotational speed Nm. The maximum rotational speed Nm is, for example, 10,000 rpm. The rotational speed of the compressor 30 gradually increases toward the maximum rotational speed Nm.

[0089] When the compressor 30 is operated at its maximum rotational speed Nm, the vibrations of the compressor 30 cause the bushes 51 and 52 to vibrate, and the temperature of the bushes 51 and 52, i.e., the temperature of the vibration-damping member 50, gradually rises. In the comparative example, the temperature of the vibration-damping member 50 rises slowly and gradually. Meanwhile, the in-vehicle noise S also rises, eventually exceeding the target sound pressure Stg of the in-vehicle noise S. The target sound pressure Stg is set, for example, to a sound pressure level that does not cause discomfort to the user.

[0090] In this embodiment, at time t1, the temperature of the vibration-damping member 50 exceeds the third temperature Th3. As a result, the control process proceeds to steps 106 and 107. In step 107, the resonant operation mode is started. When the resonant operation mode is started, the rotational speed of the compressor 30 is suppressed to the resonant rotational speed Nr, which is lower than the maximum rotational speed Nm. Moreover, the vibration of the vibration-damping member 50 at the resonant rotational speed Nr provides a larger amplitude than the vibration of the vibration-damping member 50 at the maximum rotational speed Nm. Therefore, the rate of increase in the temperature Tb of the vibration-damping member 50 at the resonant rotational speed Nr is greater than the rate of increase in the temperature Tb of the vibration-damping member 50 at the maximum rotational speed Nm. As a result, the temperature Tb of the vibration-damping member 50 rises rapidly, and the vibration-damping member 50 quickly acquires the ability to dampen vibration transmission.

[0091] The temperature Tb of the vibration-damping member 50 rises rapidly from time t1, with a steeper upward slope than in the comparative example. Eventually, the temperature of the vibration-damping member 50 reaches its saturation temperature. The in-vehicle noise S fluctuates in accordance with the change in the vibration damping capacity of the vibration-damping member 50 due to this change in temperature Tb. In the illustrated example, the in-vehicle noise S has periods of both increase and decrease.

[0092] At time t2, the temperature Tb of the vibration-damping member 50 exceeds the second temperature Th2. As a result, the control process proceeds to step 108 again. In step 108, the high-capacity operation mode is executed again. However, at this time, the temperature Tb of the vibration-damping member 50 has risen sufficiently and reached the saturation temperature. As a result, the in-vehicle noise S is suppressed to slightly exceed the target sound pressure Stg or to be below the target sound pressure Stg. Furthermore, even if the in-vehicle noise S rises, the period of increase is limited to a short period.

[0093] Eventually, at time t3, the in-vehicle temperature Tr exceeds the first temperature Th1. As a result, the control process proceeds to step 104. In step 104, the normal operation mode is executed. In the normal operation mode, the compressor 30 is operated at a thermal output rotational speed set to achieve thermal output corresponding to the thermal load. At this time, the in-vehicle temperature Tr exceeds the first temperature Th1, and the heat pump device 1 can meet the thermal load with its normal design capacity even without performing at its maximum capacity. For example, the thermal capacity of the heat pump device 1 in the normal operation mode is lower than that in the high-capacity operation mode, and is sometimes called the design rated capacity. Therefore, the thermal output rotational speed is lower than the maximum rotational speed Nm.

[0094] According to the embodiment described above, the heat pump device 1 includes a compressor 30 as an excitation source. The module 20, including the compressor 30, is elastically supported by the vehicle frame 40 via vibration-damping members 50 (rubber bushings 51, 52). The module 20 vibrates due to the rotation of the compressor 30. The rotational speed of the compressor 30 is variable within a predetermined range from the maximum rotational speed to the minimum rotational speed. This variable range includes at least one resonant frequency. When the rotational speed of the compressor 30 is the resonant rotational speed, the module 20 vibrates at the resonant frequency. At the resonant frequency, the vibration-damping members 50 resonate due to their own elasticity and deform significantly. The large deformation of the vibration-damping members 50 promotes warm-up due to internal heat generation of the vibration-damping members 50. When predetermined operating conditions are met, the control device 4 operates the compressor 30 at the resonant rotational speed. As a result, when predetermined conditions are met, the vibration-damping control device provided by the control device 4 causes the vibration-damping members 50 to generate internal heat, promoting warm-up of the vibration-damping members 50.

[0095] According to the embodiment described above, the resonant frequency fr is set according to the temperature Tb of the vibration-damping member 50. Therefore, even if the temperature Tb changes, the resonant frequency fr corresponding to the changed temperature Tb can be set.

[0096] Other Embodiments The disclosures in this specification and drawings are not limited to the exemplary embodiments. The disclosures include the exemplary embodiments and variations thereof by those skilled in the art. For example, the disclosures are not limited to combinations of parts and / or elements shown in the embodiments. The disclosures are implementable in a variety of combinations. The disclosures may have additional parts that can be added to the embodiments. The disclosures include those in which parts and / or elements of an embodiment have been omitted. The disclosures include substitutions or combinations of parts and / or elements between one embodiment and another. The scope of the disclosed technical areas is not limited to the descriptions of the embodiments. Some of the scope of the disclosed technical areas are indicated by the claims and should be understood to include all modifications within the meaning and scope equivalent to the claims.

[0097] The disclosures in the specification and drawings are not limited by the claims. The disclosures in the specification and drawings encompass the technical ideas described in the claims and extend to a wider and more diverse range of technical ideas than those described in the claims. Therefore, a variety of technical ideas can be extracted from the disclosures in the specification and drawings without being bound by the claims.

[0098] In the above embodiment, the heat pump device 1 provides the vibration isolation control device and the vibration isolation device. Alternatively, the vibration isolation control device and vibration isolation device according to this disclosure may be provided by a refrigeration cycle device that only supplies cold air.

[0099] In the above embodiment, the heat pump device 1 provides a system for a vehicle. Alternatively, the heat pump device 1 may provide an air conditioning system for an office or residence. In this case, the vehicle frame 40 is a structural member such as the foundation or walls of the office or residence. The heat pump device 1 may also provide a device for regulating the temperature of food or drinking water.

[0100] In the above embodiment, the control device 4 performed the resonant operation mode when the temperature state of the heat pump device 1 met predetermined conditions. Alternatively, the resonant operation mode may be performed when the conditions for the startup time of the heat pump device 1 are met. For example, the resonant operation mode may be performed only for a short time during the initial startup of the heat pump device 1. [Explanation of symbols]

[0101] 1. Heat pump system, 2. Air conditioning system, 3. Temperature control system, 4 Control device, 5 Outdoor heat exchanger, 6 First indoor heat exchanger, 7. Air-conditioned case, 8 first medium heat exchanger, 9 heating medium system, 10 pumps, 11 second indoor heat exchangers, 12 second medium heat exchanger, 13 cooling medium system, 14 Pumps, 15 Equipment heat exchangers, 16 batteries, 20 modules, 21 module bodies, 22 conduits, 23 Bracket, 24 Piping, 25 Refrigerant container, 26 Piping, 27 Valve device, 28 Bracket, 30 Compressor, 31 Motor, 32 Bracket, 40 Vehicle frame, 41 Bracket, 50 Vibration damping component, 51 Bushing, 52 Bushing.

Claims

1. In a compressor control device that controls the rotational speed of an electric compressor (30) which is elastically supported by an elastic vibration-damping member (50) and causes the displacement of the vibration-damping member to resonate at the resonant frequency, The system has a resonant operation mode that adjusts the rotational speed of the electric compressor to the resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency. The aforementioned resonance operation mode is a compressor control device that is executed in the low-temperature range of the operating temperature range of the vibration-damping member.

2. The compressor control device according to claim 1, wherein the resonance operation mode is performed to set the resonance rotation speed of the electric compressor according to the temperature (Tb) of the vibration-damping member.

3. A compressor control device that controls the rotational speed of an electric compressor (30) which is elastically supported by an elastic vibration-damping member (50) and causes the displacement of the vibration-damping member to resonate at a resonant frequency, The system has a resonant operation mode that adjusts the rotational speed of the electric compressor to the resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency. The aforementioned resonant operation mode is a compressor control device that is executed to set the resonant rotational speed of the electric compressor according to the temperature (Tb) of the vibration-damping member.

4. The compressor control device according to claim 2 or 3, wherein the rotational speed of the electric compressor in the resonant operation mode is set by a map in which the temperature is the input variable and the resonant rotational speed is the output variable.

5. The compressor control device according to any one of claims 1 to 3, wherein the vibration-damping member supports the electric compressor or a module including the electric compressor on the vehicle.

6. The compressor control device according to any one of claims 1 to 3, wherein the vibration-damping member is a low-loss material with a loss tangent (tanδ) of 0.1 or less.

7. Furthermore, the compressor control device according to any one of claims 1 to 3, which has a high-capacity operating mode in which the rotational speed of the electric compressor is increased above the resonant rotational speed in order to increase the heat output of the heat pump device in the low-temperature range of the operating temperature range of the vibration-damping member.

8. The resonance operation mode is executed when the room temperature (Tr) controlled by the heat output is below the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is between the second temperature (Th2) and a third temperature (Th3) that is higher than the second temperature. When the room temperature (Tr) controlled by the heat output is less than or equal to the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is less than or equal to the second temperature (Th2), the high-capacity operation mode is executed. The compressor control device according to claim 7, wherein the high-capacity operation mode is executed when the room temperature (Tr) controlled by the heat output is less than or equal to the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is greater than or equal to the third temperature (Th3).

9. A compressor control device that controls the rotational speed of an electric compressor (30) which is elastically supported by an elastic vibration-damping member (50) and causes the displacement of the vibration-damping member to resonate at a resonant frequency, The system has a resonant operation mode that adjusts the rotational speed of the electric compressor to the resonant rotational speed so that the vibration caused by the rotation of the electric compressor becomes the resonant frequency. Furthermore, within the operating temperature range of the vibration-damping member, in the low-temperature range, there is a high-capacity operating mode in which the rotational speed of the electric compressor is increased above the resonant rotational speed in order to increase the heat output of the heat pump device. The resonance operation mode is executed when the room temperature (Tr) controlled by the heat output is below the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is between the second temperature (Th2) and a third temperature (Th3) that is higher than the second temperature. When the room temperature (Tr) controlled by the heat output is less than or equal to the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is less than or equal to the second temperature (Th2), the high-capacity operation mode is executed. A compressor control device that executes the high-capacity operation mode when the room temperature (Tr) controlled by the heat output is less than or equal to the first temperature (Th1), and the temperature (Tb) of the vibration-damping member is greater than or equal to the third temperature (Th3).

10. A vibration isolation device in which an electric compressor (30) or equipment (20) including the electric compressor is elastically supported by an elastic vibration isolation member (50), Within a portion of the adjustable range of the rotational speed of the electric compressor, the frequency of vibration caused by the rotation of the electric compressor substantially coincides with the resonant frequency at which the displacement of the vibration-damping member resonates. The frequency range of vibrations caused by the rotation of the electric compressor, A vibration isolation device in which the range of the resonance frequency in the low-temperature range of the operating temperature range of the vibration isolation member overlaps with the range of the resonance frequency in the low-temperature range of the operating temperature range of the vibration isolation member.

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