Features of modal analysis
What is modal analysis?
Tekla Structural Designer's modal analysis is an analysis of undamped and simpleharmonic vibrations.
To formulate a solution we begin by considering the discrete dynamic equation used in finite element analysis:
[M]{ü} + [C]{u̇} + [K]{u} = {F}
Where [M] is the mass matrix, [C] is the damping matrix and [K] the stiffness matrix. All three matrices are constant in linear dynamics. {ü}, {u̇} and {u} are respectively the acceleration vector, velocity vector and the displacement vector. All three vectors vary as a function of time, as does {F} which is the loadvector (sometimes referred to as the forcing function).
Thinking about this equation in physical terms; [M]{ü} is the inertial force (from Newton's 2nd law), [C]{u̇} the damping force and [K]{u} the internal elastic force (i.e. strain energy).
By making some simplifications  such as that damping is zero  this can be reduced to:
[M]{ü} + [K]{u} = 0
A physical explanation of this equation is that, for a valid vibration mode at any instant of time, the inertial forces ([M]{ü}) and internal elastic forces ([K]{u}) are equal and opposite, while no external force is applied to the system. This is known as free vibration. Free vibration isn't related to static loading (other than where this defines mass) and will identify frequencies at which the structure can naturally resonate, based on its mass distribution and stiffness alone.
Solutions for the above equation have the following form:
{u}(t) = {U}e^{iωt} and {ü}(t) = ω^{2}{U}e^{iωt}
Substituting and dividing by e^{iωt} (which represents the timeresponse and is simply a sine wave since the behaviour is simple harmonic) we obtain the eigenvalue equation:
([K]  ω^{2}[M]){U} = {0}
In which ω^{2} is the eigenvalue and {U} the eigenvector.
Dividing by {U} and rearranging gives the following equation, which you may recognize as being of the same form as the fundamental equation for frequency (valid only for a single degree of freedom (SDOF) system) f ∝ √ (k/m) :
ω = √ ( [K]/[M] )
Note the eigenvalue equation contains no terms for force or acceleration.
Tekla Structural Designer’s modal analysis is a solution of this eigenvalue equation for the specific model. The method of solution is highly complex  if you are interested, details can be found in any good reference on vibration theory (we can recommend Vibration: Fundamentals and Practice Clarence W. de Silva, Boca Raton: CRC Press LLC, 2000). There are many (numerical) methods of solution, no fewer than three of which are implemented in TSD; Jacobi, Subspace and FEAST (the selection of the method used being automated).
The solution to the eigenvalue equation is the vector {U}  which is the mode shape  with a corresponding frequency which is the square root of the eigenvalue; ω = √ ω^{2}. The mode shape is just that; a shape. It can have any amplitude  modal analysis does not give this, just the shape. So it does not produce ‘real’ deflections or forces.
Note that ω is the angular (or ‘circular’) frequency in terms of radians and so must be converted (by dividing by 2π ) to be in Hz.
There is not a single solution to the eigenvalue equation (other than for a single degree of freedom (SDOF) system)  a structure which has many DOFs will have multiple mode shapes*. Each mode shape occurs at a very specific frequency called the natural frequency of the mode in question.

We can easily calculate the number of mode shapes for any numerical model  it is the number of free nodes (i.e. those not at a support) multiplied by the number of DOF’s (i.e. mass directions) at each node. In 3D space and using the consistent mass matrix (the default), there are 6 DOFs (3 translational and 3 rotational). Hence a model with 100 nodes will have 100*6 = 600 modes.

From this you will appreciate that even a relatively small model will have a large number of modes, while a large model will have 1000’s. However we are generally only interested in the lower modes  i.e. those with lower frequencies  which a) will involve the majority of the structure and b) are most likely to be excited (by whatever forcing function is in play  e.g. an earthquake or human movement) and thus problematic.
So in summary; modal analysis in Tekla Structural Designer is an idealized solution which finds the natural frequencies of a structure that does not consider damping or dynamic loading 'input' to your structure, which may occur in the real world. The results it produces are a list of modes  in order of ascending frequency  together with their: frequency; period; mass participation % and modal mass.
Active mass and mass participation
In a 1st order modal analysis mass is assigned to nodes of the analysis model. In simple terms (neglecting rotation terms for the consistent mass matrix) half of each element mass is assigned to each node it is attached to.
Mass that is assigned to a translational support cannot go anywhere  i.e. it is not "active".
Reported in the Dynamic Masses table, this is the actual total active mass for each direction, but expressed in terms of force units rather than mass.
Summed total translational mass
Reported in the Dynamic Masses table (see above), this is the total system mass for each direction, again expressed in terms of force units rather than mass.
Reported in the Summed Mass table, this is the proportion of mass that is active for each direction. For a building this will usually be close to but not quite 100% as some mass always goes to the supports.
Translation % = (Summed Active Mass / Summed Total Translational Mass) x 100
Participation translation %
Reported in the Summed Mass table (see above), this is the sum of Mass Participation % (reported in the Modal Frequencies table, as shown below) for all modes for each direction.
Mass participation is used in seismic analysis  in simple (not literal) terms it is a measure of the momentum of a mode and so a predictor of the base shear it produces.
Design codes stipulate that the sum for all the modes should be ≥ 90% for seismic analysis usually for two orthogonal lateral directions.
Modal mass
After running a 1st order modal analysis, modal masses for each mode are available in the Modal Frequencies table.
In Tekla Structural Designer the modal mass, M_{i} is given by the following matrix equation:
M_{i} = { Ψ}_{i}^{T} [M] { Ψ}_{i}
Where {Ψ}_{i} is the unityscaled mode shape (often termed mode vector) of the i^{th} mode (i.e. any single mode) and [M] is the mass matrix. The meaning of the unityscaled mode shape is that the (numerically) largest modal displacement is set to unity and all other displacements are scaled accordingly. The term {Ψ}_{i} is used to differentiate this mode shape from the massnormalized shape {Φ}_{i} which is the mode shape actually reported by Tekla Structural Designer.
This equation comes from modal analysis theory. It may also be termed "generalized mass".
Another way to state this equation, which is found in some design guides, is a summation equation for point masses and their associated modal displacements for a system of discretized mass distribution:
We have from CCIP016:
where i is each on N points on the structure, having mass m_{i} at which the mode shape μ_{j,i} is the j^{th} mode is known.
According to this reference  "Conceptually, the modal mass can be thought of as the mass of an equivalent single degree of freedom system... which represents the j^{th} mode."
It can be seen how this is equivalent to the matrix equation given above. Actually Tekla Structural Designer makes use of a shortcut calculation since it already has mode shapes which are normalized to mass.
The massnormalized mode shape { Φ}_{i} and the unitynormalized mode shape {Ψ}_{i} are related as follows:
From this we can state the following, where Φ_{2} is the largest modal displacement from the massnormalized mode shape (which we already have from the Tekla Structural Designer modal analysis):
Hence: